Note : Les descriptions sont présentées dans la langue officielle dans laquelle elles ont été soumises.
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This invention relates to progressing-cavity-type
positive displacement helical pumps for handling liquid comminut-
ed material, such as the progressing cavity helical pump of my
Canadian Patents Nos. 913,989 and 1,029,602. More particularly,
the invention relates to an improved flexible coupling shaft of
the type that extends through a helical pump rotor of tubular
form and flexes therein for coupling the pump rotor to a rotary
drive shaft to accommodate orbital movement of the rotor during
rotation thereof.
Progressing-cavity-type positive displacement rotary
devices of the general class that includes the devices disclosed
in my Canadian Patents Nos. 913,989 and 1,209,602 (hereinafter
referred to as "Allen" devices or pumps) have a rotor with an
exterior helical surface that engages the surrounding interior
helical surface of the stator, the rotor surface having one more
thread than the stator surface and a lead twice that of the
stator surface. Thus, the stator surface and the rotor surface
define therebetween sealed pumping cavities that are axially
advanced as the rotor rotates and at the same time orbits in the
same direction at two or more times the rate of its rotation.
For a more complete description of Allen pumps of this type,
reference is made to my aforesaid Patent No. 913,989.
This class of rotary helical devices differs from the
well-known Moineau-type devices as disclosed, for example, in
U.S. Patent No. 1,892,217. In the Moineau-type device, the
helical rotor orbits in the reverse direction relative to its
rotation and the helical stator surface has one more thread
than the helical rotor. A universal coupling must be provided
bet~een the Moineau rotor and drive shaft to accommodate the
orbital motion of the rotor, the orbital speed being equal to
the speed of rotation. Various types of universal connections
or couplings have been utilized, including conventional universal
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joints, long flexible shafts, etc.
Typical examples of such couplings utilizing flexible
shafts, or the like, are described in U.S. Patents Nos. 2,028,407;
2,456,227, and 3,612,734 and in British Patent No. 1,379,907.
The devices shown use flexible metal shafts or metal cables.
The flexing produces substantial stresses in the metal shafts
or cables and the devices are prone to failure due to fatigue.
Among the many applications for Allen pumps are uses
where small units are used to pump slurries, such as sludge
from dust separators, and thick, viscuous industrial chemical
products. It is desirable that these pump units be of compact,
easily maintained construction and that replacement of parts,
such as a worn rotor or stator, be easily accomplished.
One advantageous form of flexible coupling is dis-
closed in my Canadian Patent No. 1,029,602 wherein the pump is
designed primarily for use in the pumping of sewage. The same
drive shaft that drives the pump rotor is used to drive a
grinding unit that operates simultaneously with the pump. In
that application, the shaft extends through a hollow rotor and
the coupling between the rotor and the shaft is accomplished by
a flexible sleeve positioned within the rotor and surrounding
the drive shaft. The flexible sleeve is connected at one end
to the shaft and at the opposite end to the rotor. That con-
struction is especially adapted to applications where the drive
shaft extends completely through the rotor, whereas, the present
invention deals with applications wherein there is no need for
the drive shaft to extend through the rotor.
More specifically, the present invention is concerned
with the flexible coupling between a rotary drive shaft and a
generally hollow orbital rotor of the type shown in my Canadian
Patent No. 1,029,602, the required flexibility being provided
by a flexible coupling shaft with at least a portion of its
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length being adapted to flex in the space within the hollow
rotor. The connection of the flexible shaft to the rotor can be
accomplished in several conventional ways, although these usual-
ly require relatively large components, such as hubs, flanges,
etc., which require considerable space relative to the rotor
and shaft. While sufficient space may be available in larger
pumps, there is frequently insufficient space in the case of
smaller, lower capacity pumps. Also, the smaller the pump, the
more difficult and time-consuming the assembly of the connection
between the hollow rotor and flexible shaft becomes.
Another related problem in the field of liquid pumps
generally, as well as progressing-cavity-type pumps of the type
described above, is that of preventing leakage of the material
being pumped along the drive shaft to the shaft bearings. Gen-
erally, this is done by providing a packing gland between an
outer portion of the shaft and a surrounding bore in the hous-
ing. This packing must not only be adequately retained in its
desired position, but must be periodically replaced. In the
past, the removal and replacement has required substantial dis-
assembly of the pump and has been a burdensome, time-consuming
procedure.
The device of the present invention satisfies the
requirements and difficulties indicated above and affords other
features and advantages heretofore not obtainable.
It is among the objects of the present invention to
provide a positive displacement, helical pumping mechanism
(e.g., Allen pump) with an improved means for coupling a hollow
orbital rotor to a rotary drive shaft.
Another object of the invention is to provide a coup-
ling between a rotary drive shaft and a hollow orbital rotorfor a pump of the type described wherein a flexible connection
is made entirely within the hollow orbital rotor.
10~ 50
These and other objects are accomplished by the novel
pump construction of the invention which comprises a progressing
cavity, positive displacement rotary pump, including a housing,
a rotary drive shaft journaled in the housing, drive means for
the shaft and a generally tubular stator coaxial with the rotary
shaft and having a helically formed interior surface. Located
within the stator is a tubular hollow orbital rotor having a
helically formed exterior surface engaging the interior surface
of the stator to define therewith sealed pumping cavities that
progress axially when the rotor is simultaneously rotated and
orbited within the stator. m e rotor has at its outer, down-
stream end, a coupling socket, including an axially extending
seat portion of polygonal transverse cross-section that tapers
inwardly toward the outer end.
The flexible coupling shaft extends through the rotor
and is connected at its outer end to the outer end of the rotor
and at its inner end to the rotary drive shaft. The coupling
shaft has an enlarged head at its outer end of non-circular
transverse cross-section that tapers inwardly toward the outer
end to mate with the tapered seat in the rotor. A suitable
fastening means secures the head in the seat to couple the flex-
ible shaft to the rotor so that the shaft flexes to accommodate
orbital movement of the rotor during operation of the pump.
The flexible coupling shaft is preferably formed of
an engineering grade plastic, such as an acetal homopolymer or
an acetal copolymer. "DELRIN" and "CELCON" are commerical
trademarks for these materials, respectively.
According to another aspect of the pump construction,
the rotary drive shaft for the unit is provided with a shaft
seal retainer that extends through opposite sides of the housing
and bears against the end of a packing-gland-type seal assembly
at three bearing points to urge the seal assembly tightly into
V
its operating position. The bearing points are located on a
crescent-shaped portion of the retainer that fits around the
drive shaft, but is easily laterally removed therefrom. The
retainer is tightly clamped to the housing with pressure adjust-
ing screws readily accessible from outside the housing. Accord-
ingly, the retainer is easily removed to facilitate removal and
replacement of the seal components.
The invention consists in the provision, in a progress-
ing cavity, positive displacement rotary pump, including a hous-
ing, a rotary drive shaft journaled in said housing, drive meansfor said shaft, a generally tubular stator coaxial with said
rotary shaft, and having a helically formed interior surface,
and a hollow, orbital rotor received in said stator and having
a helically formed exterior surface engaging said interior sur-
face of said stator to define therewith, pumping cavities that
progress axially when said rotor is simultaneously rotated and
orbited within said stator, the improvement which comprises:
means defining a coupling socket at the opposite end of said
hollow rotor from said drive shaft, said means including an
axially extending internal seat portion of polygonal transverse
cross-section that tapers inwardly toward said opposite end, a
flexible coupling shaft extending through said rotor and con-
nected at its outer end to said opposite end of said rotor and
at its inner end to said rotary drive shaft, said coupling shaft
having a coupling head at its outer end of polygonal, trans-
verse cross-section that tapers inwardly toward said outward end
to mate with said tapered seat in said rotor, means defining an
axial bore extending through said opposite end of said rotor to
said socket, means defining an axial threaded bore in said head,
and a threaded fastener extending inwardly through said axial
bore in said rotor and into said threaded axial bore in said
head to tightly anchor said head in said socket, whereby said
1(~91~5(J
drive shaft turns said rotor through said coupling shaft and
said coupling shaft flexes to accommodate orbital movement of
said rotor during rotation thereof.
In the drawings:
Figure 1 is a plan view of an Allen-type pump assem-
bly embodying the invention;
Figure 2 is a side elevation with parts broken away
and shown in section for the purpose of illustration;
Figure 3 is a cross-sectional view taken on line 3-3
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,,
,,.
., .
lO~
of Figure 2:
Figure 4 is a cross-sectional view taken on the line
4-4 of Figure 2;
Figure 5 is a cross-sectional view taken on the line
5-5 of Figure 2;
Figure 6 is a cross-sectional view taken on the line
6-6 of Figure 2;
Figure 7 is a fragmentary perspective view of a flex-
ible coupling shaft embodying the invention;
Figure 8 is a fragmentary longitudinal sectional view
on an enlarged scale taken on the line 8-8 of Figure 2 and with
parts broken away for the purpose of illustration;
Figure 9 is a sectional view on an enlarged scale
taken on the line 9-9 of Figure 8; and
Figure lO is a sectional view taken on the line lO-lO
of Figure 8.
For the purpose of illustration, the invention is
described herein in connection with its use in a progressing
cavity Allen type pump designed for pumping liquid and liquid
slurries. me pump is adapted to receive the liquid to be
pumped from an inlet pipe (not shown) with a suitable flange
fitting and to be exhausted through an outlet pipe (not shown)
connected to the front end of the pump. m e pump comprises a
housing lO in the form of a steel casting that serves as a bear-
ing mount for a rotary drive shaft ll. The shaft ll is journal-
ed in a conventional manner in a pair of bearing assemblies 12
and 13 supported in the rearward end of the housing lO as indi-
cated in Figure 2. The outer, or rearward, end of the shaft ll
has a ~ey slot 14 that serves to connect the shaft to a power
source, such as an electric motor (not shown) for driving the
pump.
The housing lO also defines an inlet cavity 15 into
lO~lO:~U
which the forward end of the rotary drive shaft 11 extends, and
an inlet throat 16 communicating with the inlet cavity 15. The
inlet throat 16 is defined, in part, by an inlet flange 17 with
four bolt holes, as indicated in Figure 1, used to secure an
inlet pipe to the housing 10. At the bottom of the inlet cavity
15 is a pipe plug 19 that may be used for draining and cleaning
the pump.
A drive flange 20 is keyed to the inner end of the
drive shaft 11, as shown in Figure 6. The flange 20 is in the
form of a split ring with a ~ey slot 22 that cooperates with a
Woodruff key 23 to key the flange 20 to the end of the shaft 11.
A threaded tangential bore is formed in the drive flange 20 per-
pendicular to the radial split and a socket head cap screw 21 is
threaded into the drive flange 20 to tighten the drive flange
20 down on the shaft 11 once it has been positioned at the
desired location.
Intermediate the ends of the drive shaft 11 is a seal
chamber 25 defined by the housing 10 and adapted to receive a
conventional shaft seal, as will be described in detail below.
Pipe plugs 27 and 28 are threaded into the housing at the top
and bottom of the seal chamber 25 to permit flushing and lubri-
cation of the seal.
A stator assembly 30 with a rotor assembly 40 therein
is located at the forward end of the housing 10. The stator
assembly 30 includes a cylindrical casing 31 threaded into an
opening in the housing 10 communicating with the inlet cavity
15. Threaded onto the opposite end of the cylindrical casing
31 is an outlet reducer 33 adapted to be connected to an outlet
pipe at its outer end.
A generally tubular stator 32, preferably formed of
rubber or other resilient material, is bonded to or press-fitted
into the cylindrical casing 31. The stator 32 may be a molded
10~ O
unitary element or may be formed of two molded halves. The
interior surface of the stator 32 defines helical threads that
cooperate with the rotor in a manner described below
A rotor 41 preferably formed of stainless steel by
investment casting is located within the stator. The rotor 41
has an exterior helical surface with a generally eliptical form,
as shown in transverse cross-section (Figure 4). The helical
rotor surface has one more thread (i.e., two threads in this
instance) than the helical stator surface (the stator surface
having one thread in this instance), which it engages to define
sealed pumping cavities 42. Also, the threads have a lead that
is equal to the number of threads in the rotor 41 times the lead
of the helical surface of the stator 32. As the rotor 41
rotates, its axis translates in an orbit circle about the axis
of the pump shaft 11 and the pumping cavities 42 are axially
advanced. This function is described in my aforesaid Patent
No. 913,989.
The rotor 41 is of hollow construction with a wall of
generally uniform thickness along most of its axial length. The
forward end portion 43 of the rotor 41, however, is considerably
thicker and of a more solid construction than the remainder of
the rotor. The end 43 defines a tapered, pyramid-shaped seat 44
of a generally polygonal transverse cross-section, that tapers
inwardly toward the outer end. An axial bore 45 extends axially
from the outer face of the rotor into the seat.
In accordance with the invention, the rotor 41 is
coupled to the rotary drive shaft 11 by a flexible coupling
shaft 50 molded of a strong engineering grade plastic, such as
an acetal homopolymer or copolymer. The shaft 50 is adapted to
flex as necessary in order to accommodate the orbital movement
of the the rotor 41 in an orbit circle about the axis of the
shaft 11. As indicated, the shaft 50 is located generally within
105~0~-~0
the hollow rotor 41.
Referring to Figure 2, the shaft 50 has an enlarged
forward head 51 with four flat, tapered surfaces (i.e., pyramid-
shaped) formed to mate with the seat 44 in the forward end of
the rotor 40. The foremost portion of the head 51 is of cylin-
drical cross-section and fits the bore 45 in the rotor 41. ~n
annular groove 52 surrounding the cylindrical portion is adapted
to receive an "0" ring seal 53.
In order to secure the coupling shaft 50 to the rotor,
a socket-head machine screw 54 that bears against a washer 55
is threaded into a threaded bore in the end of the head 51.
The opposite end of the shaft 50 is provided with a
coupling flange 56 that i8 initially formed separately and pro-
vided with a frusto-conical tapered opening 57 adapted to mate
with a corresponding taper 58 formed on the end of the shaft 50.
m e flange 56 is secured to the shaft 50 by spin welding accord-
ing to spin welding practices for engineering plastics well-
known to those skilled in the art. m e flange has three axially
extending holes adapted to mate with corresponding holes in the
drive flange 20 which is secured to drive shaft 11. Thus, the
shaft 50 can be secured to the drive flange 20 with socket-head
cap screws 61, and thus connected to the drive shaft 11. Prefer-
ably, the shaft 50 is formed from a length of cylindrical stock
of a diameter approximately equal to the diameter of the head
portion 51. The stock is turned down to the desired diameter
along the major portion of the coupling shaft length to provide
the desired thickness and flexibility. The end portions of the
shaft 50 adjacent the head portion 51 and the tapered portion
58 are flared outward to provide increased strength at the loca-
tions that are subjected to the greatest stress due to the flex-
ing of the shaft 50 during pump operation.
Entry of liquid to the interior of the rotor is pre-
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vented by a Neoprene boot seal 62 that is tightly gripped be-
tween the flange 56 and the inner end of the rotor 41. The
seal is provided with an annular slot 63 in its outer end that
receives the circular end edge of the rotor 41.
The rotor and stator geometry and the mathematical
relationships involved in their operation are described in
detail in my Patent No. 913,989.
The stator 32 may be molded, for example, of "BUNA-~"
rubber in a multiple cavity mold and clamped in place at assem-
bly, or it may be more practical to bond the stator directly to
the interior surface of the sleeve 31 at the time of molding of
the stator. The rubber material, of which the stator 32 is
formed, provides a semipositive characteristic for the unit, so
that it is capable of being "dead-ended" (i.e., blocked at the
outlet end) without risk of bursting a line or destroying the
pump. This is an automatic safety feature in case of a severely
blocked discharge. More importantly, the elastomeric stator
permits a tight sealing fit to the rotor for maximum volumetric
efficiency and flexes to permit solid particles to pass through
the seal lines which separate one cavity from another.
In accordance with another aspect of the invention,
the inlet cavity 15 of the housing 10 is sealed from the bearing
units 12 and 13 for the shaft 11 by a shaft seal assembly 70
located in the seal chamber 25, (Figures 2, 8, 9 and 10). The
shaft seal assembly 70 includes a wear sleeve 71, surrounding
the shaft 11 and secured thereto, by a button head socket screw
72 (Figure 10). Surrounding the wear sleeve 71 are a plurality
of conventional split packing elements positioned against one
another to form a packing seal with an annular liquid cavity in
the central portion. A conventional split gland sleeve 74 locat-
ed at the rearward end of the seal holds the elements 73 in
--11--
10'310.-0
position. Liquid is supplied to the packing gland through an
upper tapped opening closed by the pipe plug 28, and drained off
through a lower tapped opening closed by the pipe plug 27. The
gland sleeve 74 and packing elements 73 are all positioned and
held in place by a packing gland 75 (Figures 8 and 9) that is
easily removed for disassembly and that is positioned and re-
moved through side openings 76 and 77 in the housing 10 located
between an upper connecting span 78 and a lower connecting span
79 extending between the two openings 76 and 77. The packing
gland 75 has a shape that permits it to fit around portions of
the shaft 11, and yet be removed laterally without interference
with the shaft 11.
As best seen in Figure 9, the central portion of the
packing gland 75 has a curved, crescent shape and supports three
symmetrically spaced gland sleeve compression buttons 81, 82 -
and 83, which bear against the gland sleeve 74. Also, retainer
75 has two oppositely extending axms 85 and 86, which extend
through the openings 76 and 77, and which are engaged by adjust-
ing rods 87 and 88. The rods 87 and 88 have threaded stud
portions that are engaged by adjusting nuts 91 and 92. The
inner ends of the rods 87 and 88 are flattened and provided
with a central opening for use in anchoring them with hexhead
machine screws 89 and 90 to tapped holes in bosses formed on
the sides of the housing 10.
With this construction, the shaft seal assem~ly 70
may be disassembled merely by removing the nuts 91 and 92 from
the adjusting rods 87 and 88 and removing the packing gland 75
rearwardly off the ends of the stud portions of the rods 87 and
88, so that the packing gland may be moved laterally out of the
housing 10. The split elements of the seal assembly may then be
easily removed laterally from the shaft 11 through the openings
76 and 77 in the housing 10. The replacement of the packing
10.~
seal elements and the repositioning of the packing gland 75 is
accomplished merely by reversing the procedure just described.
The pump assembly is anchored to a suitable base by
means of support saddles 65 and 66, located as shown in Figures
1 and 2, and straps 67 and 68 that are secured by nuts to
threaded studs 69 on the support saddles 65 and 66.
With the construction shown, the pump is easily dis-
assembled periodically for cleaning and replacement of parts.
In order to remove the rotor assembly 40 from the stator 32,
the outlet reducer 33 is unscrewed from the casing 31, the
machine screw 54 is unscrewed from the flexible shaft 50, and
the rotor assembly 40 is twisted forwardly out of the stator 32.
Then the bootseal 62 is removed and the cap screws 61 connect-
ing the flange 56 to the drive flange 20 are unscrewed to permit
removal of the flexible shaft 50. These parts may be cleaned
and reinserted, or else replaced, as desired. Alternately, the
rotor 40, boot seal 62, flexible shaft 50, and drive flange 20
can be removed as an assembly by loosening the socket head cap
screw 21 and sliding the assembly off the drive shaft 11.
Typical dimensions for the helical positive displace-
ment pump illustrated herein are given in TABLE I below.
TABLE I
Pump
Dimension (Inches)
Eccentricity .1
Cavity length 4.00
Rotor major dia 1.56
Rotor minor dia. 1.16
Rotor form length 5.25
Stator major inside dia. 1.75
Stator minor inside dia. 1.35
Stator outside dia. 2.25
Stator length 5.00
Stator/cavity length ratio 1.25
A pump designed to these dimensions will have a dis-
placement of 17-1/2 gallons per minute at a shaft speed of
1725 rpm.
10~
While the invention has been shown and described with
respect to a specific embodiment thereof, this is intended for
the purpose of illustration rather than limitation and other
modifications and variations of the specific embodiment herein
shown and described wil]. be apparent to those skilled in the
art, all within the intended spirit and scope of the invention.
Accordingly, the patent is not to be limited in scope and
effect to the specific embodiment herein shown and described,
nor in any other way that is inconsistent with the extent to
which the progress in the art has been advanced by the inven-
tion.
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