Improvements in Rotary Pumps and Engines.
Year: 1891

page_text: COMPLETE STEIFICATION.
Improvements in Rotary Pumps and Engines.
I, ELLICK HENRY GOLLINGS of 958 Millard Avenue in the City of Chicago
and State of Illinois United States of America, Engineer, do hereby declare the
nature of this invention and in what manner the same is to be performed, to be
particularly described and ascertained in and by the following statement :-
This invention relates to rotary pumps and engines of that class in which a
cylindric shell contains an eccentrically mounted wheel having a motion within
the shell produced by the relative revolution of the eccentric on which the wheel
is mounted. The shell may in fact rotate while the eccentric is stationary or
cice versa, construction for both these relative movements being herein illustrated.
It is a feature of the invention herein set forth that neither the shell nor the
contained wheel has a rotary motion with respect to the other, but that the wheel
simply gyrates within the shell, and to this end the wheel is engaged with the
shell. Provision is also made for the diametrical division of the space between
the shell and the wheel, substantially in the plane of the eccentric, its plane of
division revolving when the eccentric revolves or remaining stationary with the
eccentric when the shell revolves. In order that this plane of diametrical division
may be practically permanent in the plane of the eccentric the wheel is provided
with numerous wings or radial partitions which have extensions in one form or
another by which they are continued in contact with the periphery of the shell.
To give practically uniform speed of the shell and its contained wheel when both
revolve, or to hold the wheel steadily against revolution when the eccentric
revolves, the devices for engaging the shell with the wheel, which ordinarily are of
a kind to act successively, are numerous, and to render them more effective to the
end sought they operate within a short arc about midway of the half circle at the
side of the plane of the eccentric. Provision is made for the admission and
discharge of a fluid to and from the spaces between the shell and wheel, at
opposite sides of the diametrical division, by suitable ports and passages, so that
the rotation of the shell while the shaft is stationary, or the rotation of the shaft
while the shell is stationary, will result in the induction and expulsion of the fluid
to be pumped. On the other hand, the introduction of steam or other expansive
fluid will cause the operation of the machine, (when properly designed for this
purpose) as an engine. The apparatus is illustrated with especial reference to its
adaptation as a steam engine in Figures 38 to 41 inclusive of the accompanying
drawings.
Describing the invention in each of the several forms in which it is illustrated
by the accompanying drawings, I first describe the construction shown in Figures 1,
2, 3 and 4, in which Figure 1 is an interior view of the shell and a side view of
the eccentric wheel therein; Figure 2 is a section in the indirect line 2-2 of
Figure 1, and Figure 4 is one in side view of the shell, showing the slots for
engagement with pins on the wheel seen in section. These figures show the shaft
and its eccentric as non-rotative, and the shell and the interior wheel rotative. In
these figures also the shaft is made hollow at both ends and admits fluid at one
end while discharging it at the other.
A represents a stationary frame having clamp bearings a at its ends for the
support of the non-rotating shaft B. This shaft is shown as formed of an integral
piece provided with axial passages band in its opposite ends respectively for
the inlet and outlet of the fluid to be pumped. Between the passages
shaft B is solid or closed and is provided with an eccentric portion ³.
passages open laterally on opposite sides of the shaft and at opposite ends o
the
The

page_text: the eccentric 12, forming ports 63 b for the inlet and outlet of the fluid to be
pumped. CC are two parts or end plates together forming the shell, being
provided with marginal flanges c through which bolts pass to secure them together
and each half, having a bearing, as c¹, upon the concentric portion of the shaft B
outside the ports 63 so that the latter may deliver into and discharge from said
shell. Collars & secured to the shaft retain the shell laterally in place. The
central part of the shell as a whole is cylindric, as indicated in Figures 2 and 3,
said cylindric portion having end walls which are parallel with each other from the
periphery inward part way to the axis. At the inner margins of these parallel
portions of the end walls the latter project outwardly as shown in the same figures,
and the interior of each of these projecting portions is divided into a series of
chambers or passages d d' by equi-distant radial partitions D D'. The edges of
these partitions adjacent to the cylindric chamber are in the planes of the parallel
inner faces of the shell and the remaining edges of said partitions are parallel
with the axis of the shaft. The ports 3 and 4 of the shaft are located abreast of
the passages d d¹. Assuming the shell to be rotated from left to right the
passage will be the inlet and the outlet, and the feed port will discharge
directly into the passage d, while the delivery port 4 will receive directly from the
passage d'. At each side of each port the shaft is provided with a longitudinal
rib H of suitable width to extend from one partition D D¹ to the next, so that one
such partition is always in contact at its inner edge with said rib. These ribs are
on diametrically opposite sides of the shaft and are all in the plane of the eccentric.
While passing these ribs the partitions of the shell form practically water-tight
joints with them.
The interior wheel is composed of a hub e from which radiate wings E corre-
sponding in number with the partitions D D and separated by equal spaces. This
wheel is mounted loosely on the eccentric and laterally fills the cylindric
space within the shell. The hub is shown provided with a two-part bushing e¹
which admits of its application to the eccentric when made smaller than the shaft,
as shown. To the outer end of each wing E of the eccentric wheel, is hinged an
extension F. The hinge connection, consists of a transverse cylindric socket fin
the end of the wing into which a parti-cylindric edge of the extension is inserted.
The outer ends of the extension Fare held in close contact with the inner periphery
of the shell by pins f¹ which project laterally, from the extensions F into slots f
in the adjacent face or faces of the shell. These extensions F are located between
the parallel portions of the end plates of the shell. The slots f' are located in
a circle drawn from the axis of the shell and are of suitable length to allow the
gyrating movement of the wheel produced by the action of the eccentric thereon
in the rotation of the shell and wheel. Said slots are also so located that the end of
one of them situated about midway of the half circle cut off by the plane of the
eccentric, will bear against a pin on an extension F and will thus form a means
acting temporarily to rotate the eccentric wheel with the shell. As this plane
revolves or .constantly shifts its position the pins and slots will successively act as
described, each through a short are situated in the same relation to said plane and
with the effect of giving a substantially uniform rotation to the eccentric wheel
corresponding with the rotation of the shell and resulting in the production of a
mere gyrating movement of the wheel within the shell. In locating the slots f
care is taken that opposite wings of the eccentric wheel in the plane of the eccentric
will coincide with opposite partitions D D¹ at the ends of the shell, so that there
shall be, by such coincidence of partitions and wings, a longitudinal division of the
entire space within the shell into two general parts, one of which communicates
with the inlet port of the shaft and the other with the outlet port thereof. The
slots and pins thus form what I term a driving connection between the shell and
the eccentric wheel.
By reason of the uniform speed of the shell and wheel obtained by the multi-
plicity of successively acting driving connections, as described, not only is a steady
and pulseless flow of water produced but the friction between the surfaces of the

page_text: rotating parts in contact is reduced to a minimum, being limited to that which
results from the eccentricity of the inner wheel.
The shell may be driven by any external means, as for example, by a sprocket
wheel m, seen in Figures 2 and 3.
In the construction above described the two parts of the interior of the shell
divided in the plane of the eccentric and communicating one with the inlet port,
and the other with the outlet port of the shaft B, the minor chambers or spaces
within the shell are severally expanded during their movement through the half
circle on that side on which they communicate with the inlet port and corre-
spondingly contracted successively on the opposite side. As a consequence, in the
rotation of the shell, water will be admitted to one part of the shell while it is
being expelled from the other.
Figures 5, 6, 7 and 8 are views of a modified construction, corresponding (as
views) respectively with Figures 1, 2, 3, and 4. In this modification, the radial
passages of the shell are omitted, the eccentric wheel is closed at the sides (except
that ports are formed near the hub) and the shaft is provided with parti-annular
flanges, one at either side of the wheel and on opposite sides of the shaft, each of
which flanges closes one-half of such ports of the eccentric wheel. The shaft is
here shown made in parts, the end portions B being separate from the middle
portion and the latter being also made in parts one of which, B2, is the axis of
the eccentric, another, B³, the portion in which is formed the inlet port b³, and
still another, B', the part in which is formed the outlet port . The shell has
central enlargements M and N embracing spaces which surround the ports 63 and 6.
The eccentric wheel in this construction is formed with two side walls g¹ g'
(Figures 6 and 7) laterally enclosing the radial spaces g and it has a rim uniting
the two sides g' which is provided with water passages 92. The radial spaces also
communicate at M and N through passages or ports i near the hub of the wheel.
Half the ports on each side of the wheel are closed by the opposite segmental
flanges J, said flanges being extended, however, to overlap a diameter so that
no one space in the eccentric wheel can at the same time communicate with the
spaces M N. The eccentric wheel in Figures 5 to 8 inclusive has hinged
extensions F essentially like those of the preceding figures, except that they are
not relied upon as driving connections between the shell and wheel, and the free
ends of said extensions are held in contact with the inner periphery of the shell
by projections thercon which extend into continuous grooves p in the side walls of
the shell adjacent to its periphery. The driving connections, as shown in Figures 5
to 8 inclusive, consist of pins s projecting from the side of the eccentric into
circular holes s¹ and located in the side walls of the shell. The gyrating move-
ment of the wheel requires that these holes or recesses shall be at least double the
radius of the eccentric plus the diameter of the pin s.
In the construction shown in Figures 9 to 12 inclusive:
Figure 9 is a longitudinal section in the indirect line 1-1 of Figure 11.
Figure 10 is a horizontal section in the line 2-2 of Figure 11.
Figure 11 is a transverse section in the line 3-3 of Figure 9, and
Figure 12 is a transverse section in the line 4-4 of Figure 9.
In the construction here shown the shell and its contained eccentric wheel
rotate and the shaft is non-rotative and, as in the preceding figures, the fluid to
be pumped is admitted at one end of the machine and discharged at the other.
Instead of employing hinged extensions to effect diametrical division of the
general space between the shell and wheel the wings of the eccentric wheel are
provided at their outer ends with lateral flanges which work in undercut recesses
formed in the shell to give the contacts necessary for diametrical division of the
shell interior and also the contacts necessary for driving the wheel with the shell,
or vice versa.
Giving a detailed description of these Figures 9 to 12 inclusive, A is a base
having uprights A' A' within which are secured the non-rotating axial or shaft
pipes B.B, and the prolongations B2 B² thereof. The pipe or portion B. of the

page_text: shaft is provided with a lateral opening and the pipe B¹ has a similar opposite
opening . In the proximate ends of the pipes B B¹ are secured the ends of a
shaft B³ composed of concentric portions 6 and a central eccentric portion 65. C is
the rotating shell consisting of the two similar heads or end plates C¹ and the
interposed peripheral ring C. The shell is mounted on the concentric portion b₁
of the shaft B³ through the medium of anti-friction rollers E, and upon the
eccentric is rotatably mounted the wheel D provided with evenly spaced wings d
affording intermediate spaces or chambers d¹.
Each of the heads C of the shell has a boss C³ within which are formed a series
of passages c c separated by radial partitions c¹ corresponding in number with the
wings dd on the wheel D, said passages c having cominunication with the
openings. The inner edges of the partitions c' are connected by the annular
rings which furnish inner bearing surfaces for the anti-friction rollers E, the
latter being journalled at their ends in suitable spacing rings e e. Each of the
rings C is provided with an inwardly directed, annular flange extending nearly
C³
to the shaft B between the closed end of the adjacent pipe B or B¹ and the outer
ring e of the contiguous roller bearing. The wheel D is also mounted on the
eccentric by anti-friction rollers F journalled in spacing rings f. The eccentric
is in a plane at right angles to the plane of the openings 661 of the pipes B and B¹
and at each side of its openings or each of said pipes is provided with longi-
tudinal ribs b', as shown in Figures 10 and 12. Said ribs closely proximate or
bear against the edges of the partitions c and each is of such width that when
one partition passes a rib the next one following will have reached it.
result only those chambers or passages which are on the same side as the
opening or b₁ are in communication with the interior of the corresponding
pipe B or B. These ribs be are in the plane of the eccentric.
b
As a
Adjustable rings G bear against the ends of the shell hubs, annular packing
rings d serving to make the joint water tight.
The periphery C of the shell C is formed with a series of undercut recesses c³
corresponding in number with the wings of the eccentric wheel D, said recesses
being separated by transverse overhanging flanges c¹. The extreme end faces of
these flanges are fitted to bear (when in proper position to do so) against the radial
faces of said wings d. The wings d have end flanges or lateral offsets & which
enter the recesses c³ and are directed towards the concavities of said recesses which
are overhung by the flanges c. The inner or under, surface of said flanges d' are
fitted to bear against the outer surfaces of the flanges et near their extremities, as
shown at the left in Figure 11, and the outer surfaces of said flanges d are also
fitted to bear against the bottoms of the recesses, as indicated at the right in
Figure 11.
The simultaneous rotation of the shell and eccentric wheel is produced by
contact of that one of the shell flanges, c, which is for the time being most remote
from the plane of the eccentric (or as said plane is shown in the drawing to be
horizontal, by contact of the lowermost of the flanges c) with the corresponding
wing d of the wheel. This contact is of course continued only through a short arc
and is constantly shifting from one wing and flange to the next in such simultaneous
rotation of the shell and wheel.
The contacts shown at the left and right in Figure 11 are manifestly produced
by the eccentric B. The wings & having such contact are in the same plane with
the ribs, and are also coincident with the partitions e' in the hubs C³, from which it
follows that the chambers in the lower half of the shell and wheel (being rotated
in the direction of the arrow, Figure 11) are severally enlarged as they pass from
right to left and are correspondingly contracted in the upper half of the wheel
and shell as they move from left to right. The chambers or spaces in the lower
half of the shell and wheel therefore take water from the opening 6 of the pipe B
and those in the upper half force the water into the opening 6 of the pipe B1.
The construction illustrated in Figures 13, 14, 15 and 16 also has a stationary
or non-rotating shaft and a rotating shell and wheel. It presents the feature of

page_text: having both the inlet and outlet at one end of the machine and a modification of
the construction of the wings upon the eccentric wheel and the projections from
the inner periphery of the shell set forth in the last four preceding figures.
Figure 13 is a longitudinal vertical section of the machine arranged with the
plane of the eccentric horizontal, said section being in the indirect line 1-1 of
Figure 15.
Figure 14 is a horizontal section in the plane of the eccentric or in the line 2-2
of Figure 15, the shaft and anti-friction rollers being shown in full view instead
of in section.
Figure 15 is a vertical, transverse section through the rotating shell and its
contained eccentric wheel, in the line 3-3 of Figure 13, and
Figure 16 is a vertical transverse section in the line 4-4 of Figure 13.
The arrows applied to the several section lines indicate the directions of view.
A. A are the side portions of a main frame having cross beams A¹ at its ends
and supporting an annular part A² at one end and having arms A³ at the opposite
end which sustain a socket piece A for the reception of a concentric portion of
the non-rotating shaft. B B is such non-rotating shaft having at its opposite ends
the concentric portions B B and an intermediate eccentric portion B¹. C is a
non-rotating hollow casting provided with a diaphragm C¹ and sustained by bolted
connection with the ring A of the frame. E is an extension of the non-rotating
part C having a diaphragm separating it into passages el e² which are continuous
with the corresponding passages of the part Č. This part E is desirably
supported from the floor by a base portioned and it is adapted in any suitable way
for connection with pipes in prolongation of the passages therein.
The casting C is strictly a tube having a cylindric portion at its inner end
which forms a bearing for one end of the rotating shell D. It also has its
diaphragm C prolonged beyond the inner end of the tube and tapered in such
prolongation toward its extremity, as seen in Figures 14 and 16. The diaphragm C¹
is arched within the tube to make the inlet passage c* larger than the outlet c, but
the extremity of its prolongation c¹ is in the plane of the horizontal diameter of the
tube C, as shown in Figure 16, to coincide with the horizontal line of diametrical
division of the interior of the shell adopted in the drawing.
One end of the shaft B B₁ is inserted in a socket c formed in the projecting
end of the diaphragm C¹ and is held from rotation in said socket by a pin b
passing through the walls of the socket, and through a slot in the end of the
shaft. The opposite end of said shaft is secured in the socket piece A* of the
frame.
an
The shell D is composed of three parts, to wit, the end plates d and D', and a
intermediate peripheral portion D2. The end plate d is chambered to receive
anti-friction rollers bearing on the adjacent concentric portion B of the shaft and
beyond the roller bearing it is contracted about the shaft where it is provided
with a packing d'. The opposite end plate D' also has a roller bearing on the
adjacent concentric portion B of the shaft and has besides a bearing upon the
cylindric periphery of the tube C packed at d. Said end plate D₁ is provided
with a number of passages p separated by equi distant radial webs or partitions d³
arranged to communicate with the passages of the tube C. The ends of the
webs d adjacent to said tubes run in contact with the tapered sides of the
prolongations c' of the diaphragm C₁, as indicated in Figure 14, and these tapered
sides of the diaphragm are made wide enough to continue in contact with one of
the webs until another has reached it, as illustrated in Figure 16.
The peripheral ring D² of the shell D is provided with a number of transverse
slots having cylindric enlargements at their bottoms, as shown in Figure 15.
F F are wings hinged in these slots having for that purpose parti-cylindric
enlargements at their outer edges. One wall of each of the slots ³ is parallel
to a radius of the shell and the opposite wall is inclined so that the wings F when
occupying the slots may have a limited range of vibratory movement. These

page_text: hinged wings F have at their inner edges flanges on that side towards the
straight side of the slot d.
G is the wheel mounted on the eccentric B' and provided in its periphery with
a series of recesses g opening outwardly and separated by rigid wings q' corre-
sponding in number with the hinged wings F. The wings g' are generally radial
to the wheel but at their outer ends have flanges g' which project in the same
direction as the flanges F¹ on the wings F. The wings g' are of such length as
to reach into contact with the inner periphery of the shell on that side thereof
towards which the eccentric projects and the wings F are of sufficient length and
are arranged in position to bear at the edges of their flanges F' upon the straight
sides of the wings gl at that side of the wheel most remote from the shell. This
contact of a rigid wing of the eccentric wheel with the shell at one side and contact
of the opposite wing with a hinged wing F at the opposite side of the wheel
gives a division of the general space between the shell and wheel into two parts,
the line of division being in the plane of the eccentric. The webs or partitions d³
in the end plate D₁ of the shell correspond in number with the wings of the shell
or of the wheel, and are so arranged that two opposite partitions will be in a
horizontal plane when two opposite wings of the wheel are also in that plane. The
division of the pump therefore extends to the chambered head and the common
inlet and outlet tube C.
The wings of the shell and wheel having their flanges directed as shown, the
shell will be rotated in the direction indicated by the arrow applied to Figure 15
and the wing F of the shell which is at the time lowermost (as here arranged)
will be the medium through which motion is transmitted from the shell to the
wheel. In this action it has contact with the straight side of the slot d³ in which
it is hinged, being thereby supported from tipping farther in that direction.
Such driving contact is short as between two engaging wings, and one pair of
wings follows another in affording such driving connection, with the effect of giving
practically uniform rotation of the shell and wheel.
The end plates d D' of the shell are parallel inwardly from the periphery as
far as the wings F extend, and radially inside the circle of the inner ends of
the wings F the passages p of the head D¹ connect with the cylindric chamber of
the shell.
In the arrangement here shown, c is the suction or inlet passage of the pump,
and its outlet.
By making the side faces of the prolongation c¹ of the diaphragm C' inclined or
tapering, as shown, and making the webs d³ correspondingly inclined at their ends,
a substantially tight joint between the stationary and revolving parts may be main-
tained by movement of the revolving parts toward the casting C. An adjusting
device for this purpose is shown in Figure 13, consisting of a ring H interposed
between the end of the head d and the support A, backed by adjusting screws hh.
A set screw 1 threaded through the closed end of the socket piece A and
bearing against the end of the shaft permits the latter to be adjusted with the
shell.
I
The construction shown in Figures 17, 18, 19 and 20 differs from that shown in
Figures 13 to 16 inclusive only with respect to the form of the wings on the
eccentric wheel and the extensions for prolonging the wings to the remote side of
the shell and affording the driving engagement.
Figure 17 is a vertical section in the indirect line 1-1 of Figure 18.
Figure 18 is a transverse section in the line 2-2 of Figure 17.
Figure 19 is a transverse section in the line 3-3 of Figure 17, and
Figure 20 is a fragmentary section in the line 2-2 of Figure 17, showing a
modification of Figure 18.
The wings g on the eccentrically mounted wheel G are straight and radial to
said wheel, and to provide for their prolongation as partitions of the shell interior
a series of extensions F, here shown as cylinders, are provided having gudgeons f

page_text: and at a distance from the inner periphery of the rim D' suitably to allow contact
of the cylinders with said periphery. The wings g' of the wheel bear against the
cylinders F and by the engagement of the gudgeons on said cylinders with the
slots in the shell the wheel is rotated by rotation of the shell. The slots are
of such length that in this simultaneous rotation of the shell and eccentric wheel,
the cylinders not concerned in driving the wheel may adjust themselves to a position
between the wings on both sides of them severally without binding or undue
pressure against the extremities of the slots.
The extensions F are manifestly not necessarily cylindric, but may be, for
example, rectangular in cross section. When cylindric, however, they are desirably
of a diameter equal to or greater than twice the length of the greatest space
between the shelf and one of the wings g¹.
In Figure 20 the rim D2 of the shell is shown as having transverse depressions d³,
the deepest parts of which will be occupied by the cylinders F when their
gudgeons are in contact with the rear ends of the slots. This is the position
of the cylinder when concerned in imparting motion to the wheel from the shell
and substantially its position most remote from the shell. By this modification
centrifugal action upon the cylinders tends to bring them into these working
positions after being moved out of such positions by the wings during other portions
of their revolution.
In the succeeding figures of the drawing, the shaft rotates while the shell and
its contained wheel are non-rotative. This involves the revolution of the plane of
diametrical division within the shell and consequently a revolution of the devices
containing the ports for the delivery and discharge of the fluid. Figures 21 to 24
inclusive illustrate also still another form of devices for giving extension to the
wings and thereby producing the diametrical division of the shell interior.
Figure 21 is a longitudinal vertical section in the indirect line 1-1 of
Figure 23.
Figure 22 is a horizontal section in the indirect line 2-2 of Figure 23.
Figure 23 is a transverse section in the line 3-3 of Figure 22.
Figure 24 is a transverse section in the line 4-4 of Figure 22.
Figure 25 is a perspective of one of the gates or extension members employed
in the shell for engagement and co-operation with the wings of the eccentric
wheel.
A represents a frame having the uprights A' A2 at its opposite ends. B is a
non-rotating shell secured to the said uprights and composed, as here illustrated,
of castings B and B together forming a cylindric chamber which contains the
eccentric winged wheel D. The casting B' of the shell is constructed to afford an
induction chamber and passages, separated by radial partitions and giving
communication between the chambers band. The induction chamber com-
municates with a source of supply of liquid to be pumped, as indicated in
Figure 21 at 13. Through the induction chamber passes the rotating port
casting B. A is an outlet or delivery pipe arranged in continuation of the
opening a which coincides with the delivery opening of said port casting, the
pipe A being bolted to the upright A. C is the rotating shaft having an
eccentric portion C₁ separated by collars cc from the concentric portions of the
shaft, and D is a winged wheel loosely mounted on the eccentric C. The shaft C
rests in bearings formed in the shell, which bearings, as here illustrated,
contain anti-friction rollers c'. Similar rollers are inserted within the hub of
the wheel D and around the eccentric C¹.
The wheel D as here illustrated has radial wings d d, at the outer ends of which
are lateral flanges. For the purpose of closing the spaces between the inner
peripheral wall of the shell and the several wings of the eccentric wheel a series of
vibrating extensions or gates are illustrated at E E, said gates being pivoted in the
lateral and parallel walls of the shell B. One of said gates is shown detached in
perspective in Figure 25, from which figure it will be seen that it has gudgeons e e

page_text: at its opposite ends which, as indicated by dotted lines in Figure 21, enter sockets
in the shell walls. The sectional form of each of the gates is indicated by full and
dotted lines in Figure 23 wherein it will be seen that the inner margin of each gate
has a surface e¹ which is inclined to the general surface of the gate so as to bear
squarely and closely against the inner surface of the flange d' of the adjacent wing d
of the wheel D when said wing is in its most retracted position with respect to the
surrounding shell. Each of said gates is also shown provided with an arm e' which
is illustrated in the form of a web and located at one end of the gate. This arm
projects into the space between the two adjacent wings d of the wheel, and is of
suitable width to come into successive contact with both of said wings at the
proper time to secure the vibration of the gate into and out of contact with the
shell.
The ultimate contact of the edge of the gate with the shell is, however, effected
by the bearing of the hook-formed flange d' of a wing most remote from the shell
against the surface e¹ of the adjacent gate E, as seen at the left in Figure 23. This
gate E is in the plane of the eccentric and diametrically opposite the wing d which
is borne by said eccentric into direct contact with the shell. This produces the
desired diametrical division of the shell interior into two chambers or compartments
and the line of such division sweeps about the axis of the shaft C and is always
substantially in the plane of the eccentric. One of these chambers is the suction,
and the other the expulsion chamber of the pump, and with both of said chambers,
certain of the passages * are in constant communication. The partitions ³
separating these passages are arranged to coincide with those opposite wings d of
the wheel D which are in the plane of the eccentric, so that the division of the
space between the shell and wheel D is extended to the passages 2, said division
varying its position in the latter as in the former upon the rotation of the shaft C.
To provide inlet and outlet ports which shall follow the revolving suction and
expulsion chambers of the pump the port casting B is constructed and adapted to
rotate within the induction chamber b' and between the outer edges of the non-revolving
partition and the non-rotating head A². The said casting B is rotated by connection
with the shaft C, having for this purpose a socket in which the end of said shaft is
inserted, and being made fast to the shaft by a through pin 6'. The casting B has a
wall extending diametrically across its inner open end, and arranged at its inner
edge or face in the plane of the division of the space within the shell, as shown in
Figures 23 and 24. This inner face of the wall is of such width as to have
contact with one of the partitions before it leaves contact with another. At the
inlet or suction side of the wall 68 the casting B is open both to the induction
chamber and the passages 63 b². The passage on the opposite side of said wall be
leads from the eduction or expulsion side of the shell to the opening a and the
pipe A³.
The casting B is shown in double conical form with its larger end towards the
pump chamber, and as having bearing at its extreme inner end against an
annular seat 6 formed upon the non-rotating portion of the shell B', and at its
opposite end against the adjacent upright A about the opening a.
Fis a ring
fitted to the outer conical surface of the casting B and screwed into the shell for
the purpose of centering and holding the port casting B in place at its inner end.
F is a similar ring fitted to the outer conical end of the said casting and screwed to
the upright A2 for the proper bearing support of its outer end. The joints between
the rings F and F' and the surface of the casting B upon which they bear should
be substantially water-tight and as these rings bear upon conical surfaces of said
casting they may be adjusted to any degree of closeness thereon by their screw-
threaded connection with the shell and head or upright. Set-screws ff
(Figure 22) may be employed to secure the rings after their adjustment.
In the construction shown in Figures 21 to 25 inclusive, wherein the shell does
not rotate and the shaft is horizontal, provision needs to be made for the discharge
of air from the chamber b, especially in starting the pump and also desirably to
prevent the accumulation of air within said chamber at any time. For this purpose

page_text: an automatic air valve is shown at G consisting of a hollow bulb g communicating
with the top of the chamber 6 by a passage g¹ and containing a loose ball g². This
bulb is provided with a nozzle which is closed or opened at pleasure by a plug
cock g. When the cock is open air within the expulsion side of the chamber b,
finding its way to the top of said chamber past the gates E E, will raise the ball
and have escape through the nozzle. After the air has been exhausted in starting
the pump the cock g₁ will be closed to be opened again when making another start
or when the stream thrown by the pump indicates accumulation of air within the
latter. It is one object of providing the gates E with arms e by which they are
opened by the flanges d' of the wheel, to give free passage for air from the lower to
the upper part of the shell. If it were not desirable to give such passage for the
air said gates might remain in constant bearing against the periphery of the
chamber b.
The wheel is held from rotation by successive engagement of the wheel wings
with the gates in a plane transverse to the divisional plane of the pump, as indicated
by the several contacts shown in Figure 23.
The reversal of the direction of the flow of water or other liquid through the
pump, or, in other words, the transposition of induction and discharge may be
effected by merely turning the port casting B₁, upside down.
The construction shown in Figures 26 to 29 is in many respects similar to that
shown in the last preceding group of figures, but differs in the manner of producing
engagement between the shell and wheel.
Figure 26 is a longitudinal vertical section in the indirect line 1-1 of Figure 27.
Figure 27 is a transverse section in the line 2-2 of Figure 26.
Figure 28 is a fragmentary, transverse section in the line 3-3 of Figure 26, and
Figure 29 is a plan view of one of the sliding gates and a section of the wheel
wing engaged therewith.
A represents the frame having the uprights A¹ A'; and B the shell as a whole,
bolted to these uprights and containing the chamber b, an induction chamber ¹ and
intermediate chambers or passages 2, separated by radial webs 63. The periphery
of the chamber b while included in the appended claims under the term cylindric, is
in fact polygonal, as shown. The rotating shaft C has an eccentric portion C¹, on
which latter is loosely mounted the winged wheel D occupying and gyrating within
the chamber b.
The wheel D is provided with a series of straight radial wings d corresponding
in number to the webs b³. These wings d project into recesses 610 in the inner
polygonal periphery of the chamber, said recesses being of such depth that the
ends of the wings d will bear against their bottom surfaces when thrown outward
to their extreme of movement by the eccentric C' on which the wheel D is mounted.
Said recesses 610 are also of such width in the direction of the circumference of the
shell that they severally accommodate the relative lateral movement of the wings
therein in the gyrating motion of the wheel D produced by the rotation of the
shaft C, and they are desirably of such width that opposite wings of the wheel in
the plane at right angles to the plane of the eccentric will both bear against the
sides of the recesses into which they project. By such bearing of one of the wings
the wheel is held from rotation with the shaft and by that of the other wing the
wheel is held more steadily in its place.
E E are gates each fitted to slide at its end in grooves in the opposite parallel
walls of the chamber B in close proximity to one of the flat surfaces of the
polygonal periphery of said chamber 6, and each gate is provided with an opening e
through which passes one of the wings d of the wheel D. Said wings of the wheel
coincide with the webs in the plane of the eccentric and the gate E applied to
the most retracted wing d (which is the one opposite that which bears at its end
against the bottom of the recess and is in the line of the throw of the eccentric)
closes the mouth of the recess 60 over which it is placed, so that by means of said
gate and the adjacent wing d acting in conjunction with the opposite wing d bearing
B

page_text: against the bottom of its recesses 610, the space within the shell is diametrically
divided into two parts, one of which is the pressure or expulsion side of the chamber
and the other the suction side.
When the apparatus is arranged with the shaft horizontal, as here shown,
provision for the escape of air from the pump chamber is made by forming
passages from several of the uppermost recesses 610 to give communication between
said recesses and, from the uppermost one of them, to an air valve G. Such
communicating passages are shown in full lines in Figure 28 and in dotted lines in
Figure 27, wherein those recesses which are in position to form pockets adapted to
retain air are provided with circumferentially directed outlet slots 1, 2, 3, and 4.
The slot 1 has its bottom inclined upwardly from the recess 610, from which it leads,
in such manner as to allow the air to escape into the general interior of the pump
chamber. The slots 2, 3, and 4 respectively connect adjacent recesses.
This
arrangement of slots is with a view to the rotation of the shaft C in the direction
indicated by the arrow in Figure 28. If the rotation were in the opposite direction,
then the slot 1 should connect with the recess next above it and the slot 4 might
have the form of the slot 1. The construction shown gives full communication
between the upper recess 10 and both of the recesses on that side of it in the
direction in which the shaft rotates, and to close these recesses on the pressure or
expulsion side of the pump when the diametrical division takes place through
either one of them, the gate E applied to each of said three recesses has a wing e
to close the slot.
The gate E may be of the rectangular form shown in full lines in Figure 29
or they may be cut away on one side, as indicated by dotted lines in said
figure.
It will be understood that the devices for producing diametrical division and
driving engagement may be for the most part interchanged in the otherwise
different forms of the machine shown and that other changes may be made
without departure from my invention, the essential principles thereof being
preserved.
In the following Figures 30 to 41 inclusive a construction is shown having special
adaptation to use as a steam engine, one object of the special features shown in
these figures being to reduce the steam space to a minimum for the sake of
economy.
Figure 30 is a longitudinal, axial section of a duplex steam engine.
Figure 31 is a vertical, transverse section in the line 2-2 of Figure 30.
Figure 32 is a vertical, transverse section in the line 3-3 of Figure 30.
Figure 33 is a vertical section in the line 4-4 of Figure 30.
Figure 34 is an elevation of the outer end of the revolving sleeve which
contains the steam and exhaust ports, as seen by a section in the line 5-5 of
Figure 30.
Figure 35 is a section of said port-sleeve and the shaft on which it is mounted, on
the line 6-6 of Figure 30.
Figure 36 is a perspective view of one of the parts or blocks which form
extensions of the several wings of the eccentric wheel, detached.
Figure 37 is an end view of one of said extension blocks.
Figures 38, 39, 40 and 41 are views of modifications, Figure 38 being an axial
section of a single engine; Figure 39 a transverse vertical section in the line 10-10
of Figure 38; Figure 40 a view of the inner or delivery end of the revolving
port-sleeve mounted on the concentric portion of the shaft which is shown in
section, and Figure 41 an axial section of said port-sleeve in the line 12-12 of
Figure 40.
First describing Figures 30 to 37 inclusive, A is a shaft revolving in a suitable
bearing or bearings B. C is a cylindric shell concentric with the shaft A and
having parallel heads C'C'. Within the shell C the shaft A has an eccentric.
portion A¹ and on this eccentric part of the shaft is mounted a wheel or hub D

page_text: having equal-spaced radial wings D¹ D¹. E E are blocks extending from one head
to the other of the shell and adapted to form extensions of the several wings D¹ of
the wheel D. These extension blocks E are retained in contact with the inner
periphery of the shell by means of curved tongues e' on their opposite ends which
run in corresponding annular grooves c c formed in the heads CC of the shell.
Being thus retained in contact with the circumferential wall of the shell while the
winged wheel D moves towards and from each point of the said shell wall
successively, a movement between the wheel and the extension blocks is provided
for by making said blocks with slots e which admit the ends of the wings D¹. But
as the eccentric wings D' are not exactly radial to the shell except in the plane of
the throw of the eccentric, and as it is desirable to have a close fit of the wings D'
in the slots e, the latter are provided with parti-cylindric recesses e³, one at each
side of the slot e, and into these recesses are fitted correspondingly shaped
segments of cylinders, the flat faces of which bear on opposite sides of the wing D₁
and therefore allow a relatively rocking motion of the wing with respect to its
extension block in the gyration of the eccentric wheel. For the purpose of reducing
the clearance of the engine as much as possible, the blocks E are made of such
dimensions as to fill the radial space between the hub and shell and to laterally
touch each other on the side of the throw of the eccentric, as shown in
Figure 31.
The eccentrically mounted hub or wheel D is prevented from rotating and is
caused to merely gyrate by the rotation of the shaft A and its eccentric portion A'
by suitable engagement thereof with the non-rotating head of the shell. Such
engagement is herein shown to consist of revoluble pins d fitted to rotate in holes d¹
in the end of the hub. The revolution of the pins d is provided for by mounting
them on circular plates & fitted to turn in similarly shaped recesses d in the shell
head C. The pins d are virtually cranks having of course the same throw as the
eccentric A. and they necessarily prevent the revolution of the eccentric wheel with
the eccentric on which it is mounted while permitting it to gyrate within the shell
under the revolving action of said eccentric.
Each of the extension blocks E is provided at one end with a segmental, inwardly
directed projection et the sides of which converge at a smaller angle than the sides
of said extension blocks so as to leave spaces between said projections even when
the bodies of the extension blocks themselves are brought together. This is
illustrated in Figure 32. The spaces between the segmental projections are the
passages through which the steam is fed and discharged to and from the spaces
between the hub and shell.
For the purpose of supplying and exhausting steam the concentric portion A of
the shaft is provided with a double port-sleeve F secured to said shaft and rotating
therewith. This sleeve has a steam passage f which opens at its delivery end
opposite the ends of the segmental projections e' of the wing extension blocks E
and said opening is shown in Figure 32 to embrace about three of the between
spaces
Baid projections et adjacent to the eccentric. The exhaust port fis arranged
opposite the inlet port and is of greater width than the latter, having communica-
tion with a greater number of said spaces between the projections e¹. The inlet
port at its receiving end is in constant communication with an annular space G
formed in a stationary part of the machine and supplied by steam through a pipe
or passage g. The exhaust port f' communicates through the side of the port-
sleeve with an annular steam chamber G¹ formed in a stationary casting of the
machine and connected with an exhaust passage or pipe g¹. These ports can be
reversed in their position, and the dimensions of either may be varied according to
the judgment of the constructor.
0
The general space between the wheel or hub D and the surrounding shell may be
considered as being diametrically divided by two opposite wings of said wheel in
the plane of the eccentric and such division therefore constantly revolves with said
eccentric. In one of these two halves of the general space, namely, in that half

page_text: .from which the eccentric portion A³ of the shaft is receding, the subordinate spaces
are constantly enlarging while the spaces in the opposite half are being constantly
contracted. The admission of steam into the enlarging half therefore produces the
expansion of said space and the movement of the eccentric, with the result of
rotating the shaft, the exhaust meantime taking place from the opposite half. The
port-sleeve F is constructed and arranged to give the necessary communications
with the two halves or spaces mentioned to produce these results. The arrow
applied to the port-sleeve in Figures 32 and 35 indicates the direction in which the
shaft is intended to rotate in the illustration given, and from Figure 32 it will be
seen that the block projections e extend into contact with said sleeve. The
division between the ports f and f¹ should cover at least one gap or space
between the parts e and the wall of said division bounding the inlet port f
should be located as nearly as possible in the plane of the eccentric, but never in
advance of it. The advanced wall of the outlet port should also be located as
nearly as practicable in said plane but not in advance of it. The width of the
division between the inlet and outlet ports determines the extent to which steam
will act expansively, serving as a cut off for all of the minor spaces which it covers
and closes.
As a detail of construction I prefer to make the port-sleeve F in two parts,
one part being the shaft forged or otherwise formed with projections constituting
the lateral walls of the parts, and the other part being an outer shell fixed to these
projections and having the lateral openings shown for the inlet and outlet of steam.
One advantage of this construction is, that it permits the shell or sleeve proper, if
made conical in form, as shown in Figure 30, to be adjusted lengthwise to com-
pensate wear. The ends of the adjustable sleeve which abut against a ring a on
the shaft or in the bore of the hub D should be made relatively thin so as to wear
as rapidly as do the conical surfaces.
Sectional, conical wedge bearings are shown for the support of the hubs or
wheels D from the eccentric A¹, but these are not material.
Figure 30 illustrates a duplex or double engine consisting, in fact, of two engines,
with its eccentrics on opposite sides of the shaft axis. The object of this con-
struction is to give balance to the engine so that it may be run at high speed. The
cylindric junction piece A uniting the proximate ends of the eccentrics
vided with a peripheral groove a¹ into which oil may be fed through a suitable
passage in the head C₁ and from which it may be distributed to the bearings of
the eccentric by any suitable ducts.
pro-
In the construction illustrated in Figures 38 and 39 the radial slots e in which
the wings D' slide are formed in the hub instead of in the extension blocks E and
said wings have only a hinge connection with said extension blocks, as clearly
indicated in Figure 39, whereby they may rock slightly to accommodate their
variations from an actual radial direction with respect to the shell and eccentric
blocks. In these figures also a series of passages are provided in the stationary or
non-rotating head of the shell adjacent to the revolving port-sleeve, the said
passages corresponding in number with the number of wings on the eccentrically
mounted wheel, or, in other words, with the number of spaces between such wings.
In Figure 38 these passages are indicated at c' by dotted lines on the section of
the end plate C' of the cylinder, and they are also indicated by dotted lines in
Figure 39 where their openings into the shell are shown in full lines. They are
radial in direction and their outer ends are arranged to discharge into the shell
exterior to the hub or body of the wheel D while their inner ends terminate in a
recess c² in the outer face of the head C', forming an enlargement of the passage
through which the shaft A extends and accommodating the inner end of the port-
sleeve F. The passages or ports c¹ have branch openings which admit steam
to the slots e to balance the pressure on the wings D₁ and permit their easy
movement.
The port-sleeve viewed at its inner and delivery end in Figure 40 and in axial

page_text: section in Figure 41 is slightly different in construction, though not in its essential
character, from that shown in preceding figures. It is in these Figures 40
and 41 shown as formed of a single piece and secured to the shaft by means of
a key.
Having now particularly described and ascertained the nature of my said inven-
tion and in what manner the same is to be performed, I declare that what I
claim is :-
1: The combination of a shell having a cylindric chamber, a shaft concentric
with the cylindric chamber and having an eccentric portion within said chamber, a
series of passages being provided around the shaft for the admission and discharge
of fluid to and from the cylindric chamber; a wheel loosely mounted on the
eccentric; a series of parts forming extensible partitions arranged and adapted to
successively divide the space between the wheel hub and the shell substantially in
the plane of the eccentric; driving connections engaging the wheel with the shell
and acting outside said plane of division, whereby the wheel is rotated or held from
rotation by the shell and is caused to merely gyrate within the shell by the rotation
of the shaft or shell, and means for delivering a fluid to the passages on one
side of the divisional plane and receiving it from those on the opposite side of
said plane.
2: In a rotary pump or engine, substantially as described, the combination of
the shell, the eccentric, the gyrating, winged wheel, and parts separate from the
wings of the wheel and forming extensions of said wings and giving division of the
space within the shell substantially in the plane of the eccentric.
3: In a rotary pump or engine, substantially as described, the combination of
the shell containing a series of passages surrounding its axis for the admission and
discharge of a fluid; the eccentrically mounted, gyrating wheel within the shell;
a series of parts successively dividing the space between the wheel and shell in
the plane of the eccentric, and a part constructed to afford two passages each in
constant communication with the same division or half of the shell interior, as set
forth.
4:-The combination of a stationary shell having a cylindric chamber; a
rotating shaft concentric with said chamber and provided with an eccentric portion
within the chamber; a wheel mounted loosely on the eccentric and engaged with
the shell to prevent its rotation while being gyrated by the revolution of the
eccentric; a series of parts forming extensible partitions arranged and adapted to
successively divide the shell interior in the plane of the eccentric; passages for
the inlet and discharge of a fluid to and from the shell interior; a rotating part
constructed to afford two passages each in constant communication with the same
division or half of the shell interior, and two stationary parts or pipes having
passages which communicate severally with the passages of said rotating part.
5: The combination of a cylindric shell, a revoluble shaft having an eccentric
within the shell, a gyrating wheel or hub mounted loosely on the eccentric portion
of the shaft, a series of blocks held in contact with the inner circumference of the
shell and arranged to slide in the curved direction of said circumference, a corre-
sponding series of wings permanently connecting the several blocks with the hub,
said wings having a telescoping connection with one of these parts and having also
pivotal connection with said blocks, and a part having two ports which communicate
with the shell interior, one on one side and the other on the other side of the plane
of the eccentric.
6: The combination of a cylindric shell, a revoluble shaft having an eccentric
portion within said shell, a gyrating wheel or hub mounted loosely on the eccentric
portion of the shaft, a series of segmental blocks arranged to slide in contact with
the curved inner surface of the shell, said blocks being of suitable size to practi-
cally touch each other and the hub on that side of said hub at which the hub most
nearly approaches the shell, a series of wings connecting the several sliding blocks

page_text: with the hub and having pivotal connection with said blocks, and a part having two
ports which communicate with the interior of the shell on opposite sides of the
plane of the eccentric.
Signed at Chicago, Illinois, this 25th day of October A.D. 1890.
ELLICK HENRY GOLLINGS.
Haseltine, Lake & Co.,
45, Southampton Buildings, London, Agents for the Applicant.