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Jill?‘ 7, 1947-
'Filed July 9, 1945 ‘
4 Sheeté-Sheet, 1
2;; 7:219 ai‘i‘af'neys
Jan. 7, 1947. '
Jan- 7, 1947-
Filed July 9, 1943
4 Sheets-Shéet 3
Jan. 7, 1947.
2,414,003 ‘
Filed July 9, 1945
4 Sheets-Sheet 4
6y kzls‘ azivrneys
Patented Jan. 7, 1947
Tom H. Thompson, Larchmont, N. Y., assignor to
Builder-Thompson Engineering and Research
Corporation, New York, N. Y., a corporation
of Michigan
Application July 9, 1943, SerialvNo. 494,071
8 Claims. (Cl. 74-—571)
This invention relates to mechanismand meth
od adapted to convert rotary motion to or from
reciprocatory motion by means of a straight-line
motion, i. e., the motion of a connecting rod of
theoretically unlimited length. The mechanism
movement contributed by that assembly. It is
this latter type of movement which is the primary
is of a type in which two circular eccentrics, one
inside the other, are employed to cause the con
mechanisms where a mechanical movement such
version. The object of the invention is to obtain
adjustment of the length of the reciprocatory
movement‘in a simple manner. It is character 10
istic of the invention that each of the two circu
lar eccentrics above mentioned is itself divided
into two eccentrics of equal lift and that the
opposite rotation ‘of the eccentrics in a pair gives
the change in length of the reciprocatory motion 15
while simultaneously the relatively opposed rota
’tion of the inner and outer pairs of eccentrics
causes-translation of the reciprocatory motion
into rotary motion. ' It is also characteristic of
object of the present invention.
In modern engines, pumps, compressors, brakes,
torque converters, metering devices or other
as above describedv is used, it is frequently desir
able that the length of the ireciprocatory move;
ment be variable. In some mechanisms itis even
desirablethat the direction of ‘an oscillationvbe
reversed, as far as concerns its'timed relation to
the rotary movement. _If, for example, a mech
anism of this type were employed in a pump, the
time of projection of the pistons could sometimes
be changed to advantage so as to cause the pump
to push the water or other liquids in the reverse
direction without stopping the drive of the-pump‘.
Again, if the mechanical movement were em-j
ployed in a device such as an airplane engine, it
the preferred form of the invention that when 20 would be possible to change the direction of rd
tation of the propeller without stopping the en
gine. In the mechanism which I employ, the
lift of the ‘other eccentric automatically adjusts
same elements which give the reciprocation are
itself to equality.
progressively used to reduce the lift or reciproca
In my Patent No. 2,316,114, dated April 6, 1943,
for a Machine element, there is shown a mecha 25 tion to zero and then to increase the lift in the
opposite direction. As shown, for example, in my
nism for translating rotary motion to or from re
the lift of one of the eccentrics is changed, the
ciprocatory motion by means of a straight-line
movement which theretofore had been obtained
by the well-known “Scotch yoke.” The two cir
cular eccentrics, one inside the other, of that prior
patent are embodied in the present invention,
which may be considered an improvement upon
that earlier invention. The subjects-matter of
my pending-applications Ser. No. 481,336, ?led.
March 31., 1943, and. Ser. No. 403,896, ?led July
24, 1941, are also embodied in the mechanism
shown in the present application.
' 'In straight-line motion mechanisms in which
two circular eccentrics, one inside the other, are
employed in connection with the conversion of
rotary motion to or from reciprocatory motion,
.the two eccentrics revolve in opposite directions
to give the reciprocatory motion. In the present
speci?cation the elements ‘which go to make up
the inner eccentric will be termed the “primary
eccentric assembly,” and the elements which go
to make up the outer eccentric ‘will be termed
the “secondary eccentric assembly.” The two
‘eccentrics cooperate together to accumulate the
total‘lift. The movement of each assembly as a '
unit with relation to the other assembly should
be distinguished carefully in function from the
movement of the elements within one assembly
with relation to each other. in obtaining the vari
ations in length of the part of the reciprocatory
said‘prior application Ser. No. 481,336, the cylin- ‘
ders are arranged in a radial manner in a rotor.
The rotation of the rotor need be merely relative
to the shaft associated with the primary eccen
tric-that is to say, it may be the primary which
will do the rotating, and the rotor containing
the cylinders may be stationary. The present in
vention can be employed in either type of device.
Speaking generally, the present invention con
templates splitting the primary and secondary
eccentric assemblies each into a pair of eccentrics.
Each of these four elements is in itself an ec
centric embracing 0r embraced by the companion
element with which it goes to make up one eccen
' tric pair.
In the drawings:
Fig. 1 is a view in elevation, partly broken away,
of a rotary pump made in accordance with my
invention, viewed from the control end;
Fig. 2 is a view in elevation of the control end
plate of the pump of Fig. 1;‘
‘ Fig. 3 is a view similar to Fig. 2 showing the
parts adjusted for full stroke;
Fig.4 is a vertical view partly in section on th
axis of the rotor through the pump of Fig. 1,
taken on the line 4-4 of Fig. 1;
Fig. 5 is a view in vertical section in a plane
normal to the axis of the rotor taken on the
line 5——5: of Fig. 4;
Fig. 6 is a view in horizontal section of the
pump of Fig. 1, seen along the axis of the rotor
taken on_.the line 0—6 of Fig. l, with the pump
at zero stroke;
Fig. 7 is a view in vertical section similar to
As already mentioned, in the form of pump
shown in the drawings the obtaining of the
Fig. 5, showing the parts in full stroke;
Fig. 8 is a detail view of one piston and cylinder
of Fig. '7, at another rotational position;
necessary reciprocatory motion involves the ro
tation of the rotor 40 and pistons 00 and the
holding stationary of the elements which are
functionally at the other end of the machine
element. These elements are the inner torsion
equalizer shaft 10 and the primary inner eccen
trics 80, which will be described next.
The eccentrics are divided into two pairs, the
Figs. 9 to 11 inclusive show the means articu
lating the secondary assembly; Fig, 9 being an
end view of the three eccentrics at zero stroke
inner pair being known as the primary assembly.
position; Fig. 10 being a view of the parts in side
In this primary assembly the inner part is turned
elevation at zero stroke; and Fig. 11 an end
"inside out” in a manner similar to that in
elevation of the parts at full'stroke;
which the primary is turned inside out in my
Figs. 12 and 13 are diagrammatic views of the 15 application Ser. No. 403,896, above referred to.
movements of the eccentrics and yoke about
This is a source of simplicity of construction
pump center, Fig. 12 showing the parts at .zero
and——what is probably even more important
stroke, and Fig. 13 the same parts at the end of
compactness. The primary inner eccentric con
a stroke; the small dotted circle indicating‘pump
sists of the round, so-called torsion equalizer
shaft 10 held in an eccentric position with re
The invention will be shown and described
lation to pump center by two inner eccentrics
embodied in a pump, i. e., a device in which
80 which support it at its ends. These two ec
rotary motion is being converted into recipro
centrics 80 are keyed on ‘the shaft 10 and are
catory motion. In order to simplify the descrip
held in position by roller bearings 80! (Fig. 6)
tion of the machine, I will ?rst describe .the
movement of the parts when in ‘motion during
constant operation and while no adjustment of
the stroke or lift is being made. Then I will
draw attention to the mechanisms and connec
which in turn are supported by the end plate
305 and ?ange 402. The end plate 305 at the
control end of the housing is bolted to the hous
ing end plate 303 and can be seen in Figs. 2, 3,
4 and 6. Except when the stroke of the pump
tions which make it possible'to adjust the stroke. . is being adjusted, there is no movement of the
It should be noted that the movements of
roller bearings BM in the stationary end plate
the parts are relative and that while in the ex
305. The ?ange 402 supporting the eccentric 80
ample shown in the ‘drawings the primary eccen
at the drive end of the housing is bolted to the
tric assembly does not rotate when the machine
rotor 40 and the drive shaft 50 and rotates with
is merely pumping, the cylinders and pistons 35 them. There are roller bearings 403 between
rotate. In other words, the device, in analogy
.the outer shoulder of the ?ange 402 and the
to the terminology for engines, is a “rotary”
stationary drive end plate 3!" of the casing. The
pump, i. e., the cylinders and pistons rotate about
means for adjusting the stroke and which keeps
the pump center and the casing stands still.
the inner primary eccentric from turning at
The invention, of course, is equally useful in a
other times will be described later.
“radial” pump or engine, 1. ‘e., one in which
In the so-called “reversal” of the primary inner
the cylinders do not rotate and the relative mo
eccentric, the small torsion shaft 10 occupies only
tion is obtained by rotation applied at the pri
a. minimum diameter which makes it possible to
mary assembly. The principal parts of the eas
have the primary outer eccentric 9E3 lie within the
ing are the drive end plate 301, the rotor .hous
radial dimensions of theeccentrics 60. This outer
ing 302 and the control end plate 303 (see Fig. v6) .
eccentric 90 extends the complete distance be
Mounted for rotation about pump center is a
tween the two eccentrics ~80 and, like the eccen
rotor 40 in which are six radial openings con
trics ‘BU-except when the stroke or lift of the
stituting the cylinders in which pistons 60 re
pump is being changed (as will be explained
ciprocate radially. These Openings are distrib
later)--turns with the torsion shaft ‘i0 and the
uted equi-angularly about pump center. The
eccentrics 80. These elements, by turning ,in the
rotoris turned by a drive shaft 50 which passes
one direction, combine with the secondary eccen
freely‘through an opening in the drive end plate
tric assembly turning in the opposite direction, to
30! and is connected directly to the rotor by a
give the “lift” or stroke of the pump.
flange 402.
It will be noted that with the primary inner ec
The piston 50 in each cylinder is connected
centric reversed and the primary outer eccentric
to a piston in the cylinder diametrically opposite
member 90 of straight uniform diameter, the ec
vto it. forming one unitary element, as can be
centricity 0r lift transmitted to the secondary
seen in Fig. 5. As can be seen in this side eleva
assembly does not occur around the center of the
tion, the pistons and piston rods 602 are con 60 internal diameter of the secondary eccentric as
nected by a yoke 60! and the circular eccentrics
sembly, where the lobes of the latter element are
which cause them to reciprocate are located in
spaced. When the stroke of the primary is be—
this yoke. This unitary structure can be termed
ing adjusted the torsion shaft 10 .moves up and
the yoke element. The ‘length of the element is
down a predetermined center line of the pump.
such that when one'piston is fully retracted its
As in the case of the primary eccentric, the
mate is fully advanced. There are six istons
secondary eccentric also is composed functional
in the preferred embodiment-shown in the draw
-ly of two main elements-an inner and an outer
ings. The pistons arearranged in equiiangular
eccentric. The inner part or element of the sec
relation so that the cylinders .in the ‘rotor are
60° apart. If a different number of pistons are
ondary eccentric may also ‘be termed a main cam
shaft. In the structure shown in Figs. 5 and 6
of the drawings, it is composed of two parts, a
single ribbed unitary sleeve I00 and three eccen
used, the angle between two pistons will be dif
ferent. The number of pistons should be even.
‘It will be seen thatthe yokes Bill and pistons
60 have equi-angularly spaced ‘reciprocatory
paths of movement.
tric lobes i0l for the pairs of pistons spaced
around the element in equi-angular relation.
These angularly spaced pistons are about 60°
apart, as can also bev seen, for example, in my
application Ser. No. 403,896, above referred to.
There is a space between each lobe and its ‘neigh
bor in which to place articulating ‘disks, to be
described later.
In distinction to the inner secondary cam or
eccentric cluster I00, the outer eccentrics'for the
three pistons are separate from each other and
each surrounds merely its own lobe of the inner
part of the secondary eccentric. These outer ec
centrics are designated in the drawings by the
reference characters III], III, H2. If desired,
roller bearings H3 can be placed between the
outer secondary eccentrics H0, HI, H2 and the
yoke 6M, and smaller roller bearings I M can be
placed between the inner and outer secondary ec
It will be well at this point to review the gen
eral manner of operation of the four eccentrics
which constitute the primary and secondary ec
centrics. While each pair of eccentrics can be
‘It may be noted at this point by looking at Fig. 7
that with the pistons in one extreme position, the
inner and outer eccentrics of the primary as
sembly are not giving their maximum lift. I
have found it desirable not to use the remainder
of possible lift in the primary, and it will be noted
that the part of the movement which is used is
the one which has the larger component of move
ment in the straight-line motion direction.
‘order that the reader may not be confused, it is
pointed outthat the outer primary eccentric 9!}
and the elements 10 and 80 composing the pri
mary inner eccentric are not rotated relatively to
each other to give a higher lift than is shown in
Figs. '7 and 13, and therefore the maximum theo
retical lift of the primary will not occur. The
effective lifts of the inner and outer eccentrics
are‘ equal.
Figs. l2and 13 are merely diagrammatic illus
trations of the positions of the eccentrics and
yokes at zero and full stroke of the embodiment
of the invention shown in the drawings. These
functionally considered as one eccentric in cer
correspond to Figs. 9 and 11. The small dotted
tain'respects, I shall call each pair of eccentrics
circle in each case is pump center and the small
and associated parts an eccentric assembly.
est solid circle is the position of the inner torsion
When the stroke is not being changed, 1. e., ad
equalizer shaft 10 and of the inner primary ec
justed or varied, the two eccentrics of the primary
centrics 80.
assembly turn relatively in one direction with a
As already referred to, in the example shown in
?xed lift, and the two eccentrics of the secondary
the drawings, the manual adjustment of the
assembly turn in the opposite direction with. a
.?xed but equal lift providing the cumulated or 30 stroke of the pump is obtained by movement of
the primary eccentric assembly only. The parts
total lift. This causes reciprocation of the pis
about to he described can be seen best in Figs.
tons. As long as one pair of the four eccentrics
1 to 4, and in Fig. 6. The manual adjustment
is so mounted that the eccentrics in that pair are
is rotational in a plane normal to the drive shaft
not at liberty to turn with relation to each other,
50 and it is controllably obtained by rotation of
it has been found that the eccentrics forming the 1
the hand-wheel ‘fill located on the upper end of
other assembly will not change their relation to
a worm screw shaft 102 carried by a bracket 1&3 .
each other. I have discovered that with the struc
mounted on the outer end of the ?ange 364 on the
ture shown, despite the lack of direct connection
control end plate 393 (Fig. 4). The rotation of
between the parts, the lift of the primary and
secondary eccentrics will automatically maintain
4-0 the worm screw shaft 102 is translated into verti»
equality if the two elements of one eccentric are
cal movement by means of a primary control
block 164 threaded on theworm screw shaft and
rotated in opposite directions with relation to
each other. Thus, for example, in the pump
shown‘ in the drawings if the parts 80 and 90 of
the primary eccentric are turned slightly in o‘p
posite directions from the positions shown in Figs.
v6 and '7, thereby changing the lift of the primary
eccentric, the combined effect of the change in
the primary and of the yoke opening 69! is si
multaneously to cause the two parts of the sec
ondary eccentric to rotate in opposite directions,
thereby equalizing their lift to that of thepl‘i
mary eccentric. I believe it to be novel to have
two cams or eccentrics, one inside the other, ro
tating in opposite directions to cause reciproca
tion of a third element, and at the same time to
guided vertically by the bracket ‘563. ‘This block
is connected to the inner and outer eccentrics of
the primary eccentric assembly by two arms 1'65,
106 which extend laterally on opposite sides of
the screw shaft ‘M2 at a level approximately op
posite the center of the drive shaft 5%. Each of
these arms provides the necessary turning ad
50 justment for one of the eccentrics of the primary
assembly. The angular movement of the eccen
trics caused by these arms is equal. Thus the
arm 135 at the left of the screw shaft m2, as
viewed in Fig. 1, connects with the outer primary
55 eccentric 9i] and the right arm 16% serves to turn
the inner eccentric cams 3&1 and torsion shaft ‘H1.
As can be seen in the vertical sectional view, Fig.
so construct each of those two eccentrics that the
6, the left arm ‘Hi5 has a horizontal slot 10‘? in
lift of the two eccentrics can be changed while
which slides the outer end of a pin ‘Hill mounted in
the mechanism is continuing to cause reciproca
tion of the third element, and to do this in such a 60 a collar 139 which‘ fits around the outer eccen
tric 99 and is keyed thereto by key l iii. There is
manner that the machine automatically keeps the
an open slot ‘H5 in the end plate 335 to permit
lift of the two eccentrics equal.
the movement of the pin ‘F98 without conflict
I will now describe the mechanism which is the
with the end plate. It will be seen that unless
direct or primary means of adjusting or varying
the screw shaft 702 is turned, the primary control
the stroke or lift of the pump. The fundamental
block ‘Hi4, arm ‘Hi5, collar led and key ‘Hi3 will
requirement is that the two eccentrics which with
serve to hold the outer primary eccentric 99
their associated parts constitute the primary ec
against rotation, but that if the screw is turned,
centric, may be rotated slightly in opposite direc
the resultant raising or lowering of the arm ‘Hi5
tions. Since the two eccentrics are circular ec—
rotate‘the eccentric. Lowering of the control
centrics, it will be seen that the cumulated lift
block ‘H14 will turn the eccentric counterclock
of ‘the primary will be changed.‘ > It will be
wise, as viewed in Fig. 1. Correspondingly, lower
changed, for one thing, in the maximum lift to
ing of the control block ‘164 will serve to turn the
be obtained from the primary assembly because
, cams 80 ‘and torsion shaft l3 clockwise. The
the high points of the inner and outer eccentrics
imechanism to do this can be seen in Figs. 2 ‘and
- 8'0 and 9B are further separated than heretofore.
'3 and in the .upper right-hand corner of Fig. 6.
There is a slot 10? in the arm 106 corresponding
to the slot in the arm 195 and moving horizontally
in that slot ‘H3’! is a pin l'l I fastened in the end of
an arm ‘H2 (see Figs. 2 and 3).
This arm is
automatically whether the pump is standing still
or operating.
If we were dealing with a construction in which
there was only one yoke Gill and one outer second
ary eccentric, the secondary assembly would have
mounted on the end of the torsion shaft '10 by a
to be adjusted simultaneously with the primary
screw l 53 and is locked to the cam 80 at the right
by means connected to the secondary.
end of the machine by a pin 1 it (see Fig. 6). The
It will be obvious from the description hereto
screw 7 I3 and the pin ‘H4 are on opposite sides of
pump-center and swingingthe arm 1 I 2 causes ro 10 fore given that the rotor turns in a clockwise
direction as viewed in Fig. 5 and that as a result
tation of the cam 89 and the torsion shaft 10 an
of that turning the pistons move radially back
and forth in their cylinders between the bottom
and top positions shown in Fig. 7. At the bottom
shaft and therefore turns with the shaft and the
and top positions the periphery of the rotor is
?rst-mentioned cam 80. In Figs. 1, 2, 4 and 5
in contact with ?ller pieces 1504, 405 which present
the parts are shown set at zero, the position in
curved contact faces to the periphery of the rotor.
which no lift is caused by turning of the rotor 40.
As can be seen by comparing the positions of the
In Fig. 3 the block ‘194 is shown lowered to the
parts in Fig. 7 and in Fig. 8, this separating of
maximum degree used in the machine, which cor
the plates around the periphery of the rotor
responds with the position of the parts in Figs.
20 inside the casing in the two parts makes it pos
6 and '7.
sible to give apumping action. As seen in Fig. 7,
As set forth in my previous applications, the
equi-angular amount. The cam 80 at the other
end of the torsion shaft is rigidly fastened on the
mechanism herein used is a straight-line motion
mechanism in which circular eccentrics are used
that are mounted one inside the other and which
occupy the entire space inside the element next
outside of it. The outside eccentric of the sec
ondary assembly fills the entire space inside its
for example, there is a space outside between the
rotor and the inside of the casing which is ta
pered from the inlet port 406 toward the filler
pieces 494, 495, and the tapered structure exists
between the ?ller pieces and the discharge outlet
467. It is believed that the operation of the
device will be obvious from the description ‘here
tofore given, but it is desired to point out that
I have found that adjustment of vthe two eccen
the direction in which the liquid is pumped can
trics forming the primary assembly by means of
be changed if the adjustment of stroke above
turning the screw shaft 102 will cause the sec
described is carried to the opposite side of the
ondary assembly to adjust its eccentricity auto
zero position (pump center) shown in Figs. 1, 2,
matically to equal that of the primary. This, of
4 and 5. Thus if the block 104 were screwed
course, simpli?es the mechanism needed and only
upwardly instead of downwardly, the torsion shaft
manual adjustment of the primary assembly is
it’! would be moved in a straight line to the other
necessary to cause the entire apparatus to be
side of pump center, causing the top piston in
adjusted to the new setting. (It is fundamental
Fig. '7 to go to the top point of its stroke. It
in straight-line motion mechanism that circular
will be seen that there would be liquid in the
eccentrics be used inside one another with the
lift of the primary and secondary means at all 40 cylinder as it is cut off from the discharge outlet
dill’ by the ?ller piece 405 and that the subse
times equal.) I have found that this adjustment
quent movement of the cylinder would carry it
takes place in spite of the fact that one part of
into contact with the port 1306 which theretofore
the secondary assembly rotates in one direction
was the intake port, and the piston would push
and the other part in the opposite direction. The
the liquid out into that port. The effect of chang
mechanism shown in the drawings, however, does
have dead center at the top and bottom positions
ing the timing of the pistons in this manner in
of the rotor and for those positions it is advisable
a pump is to make it possible to change the di
rection in which the liquid is being pumped, with
to provide means insuring that the direction of
rotation of the eccentrics does not change. Thus
out stopping the rotation of the drive shaft at
it is possible at those dead center positions for 50 all. The advantages and uses of such a con
the secondary assembly to go into greater or lesser
struction will be obvious. This is especially true
lift positions. I have devised the following novel
when it is taken in connection with the fact that
means of preventing this and overcoming other
the output of the pump can be varied. Similarly
objections which will be mentioned as the descrip
through a hydraulic torque converter the speed
tion proceeds. In the ?rst place, the outer ec 55 or direction of rotation of the drive shaft of the
centrics of the secondary assembly are kept in
fluid motor can be varied. In other words, by
equi-angular relation to each other by the ar
simply changing the setting of the two eccentric
ticulating means which will be described herein
elements of one of the‘ eccentric assemblies in
after, so that a common point on one, in the case
the mechanical movement, it is possible to go to
of the mechanism shown in the drawings, is 120°
any other portion of a complete cycle of move
away from the corresponding point at the neigh
boring outer eccentric, regardless of the position
Stated another way, my invention provides
that any such outer eccentric is in with relation
means whereby a full stroke in one direction
to the lobe of its inner eccentric. I also ?nd that
can be changed to zero stroke, passing through
it is useful for the proper functioning of the
the zero point into a full stroke in the opposite
mechanism to have the equal radial disposition
direction while the machine is operating, with
of the cylinders about the periphery of the rotor.
out changing or altering the position of the
The ?xed relation of the three lobes of the inner
driving means itself. In. this statement I am as
eccentric of the secondary assembly also per
suming that we are dealing with a pump of the
forms a function in proper operation of the de
type mentioned in the opening of the speci?ca
vice, and with these features each secondary unit
tion; and by “driving means” I refer to the drive
is helped past its dead center position by the
shaft. The same principle will apply in the case
other two units, and the adjustment of the ec
' of an engine.
' centricity of any secondary unit to equal the ad
There is another novel feature shown in the
justment of the primary assembly takes place 75 drawings. This is the articulation. As above
yoke 60!. With circular eccentrics so embraced,
mentioned, it will be noted that the outer ele
ments of the secondary eccentric assembly for
each piston element are free and independent
of each other. (I have already pointed out that
they have no ?xed connection to the other ele
ments of the secondary eccentric to which each
one belongs.)
In placing three outer secondary cams upon
a shaft consisting of three inner secondary cams
at 120° relation to each other, these outer sec
ondary cams must bear a constant rotational
relation to each other at all times to insure the
operation of the variable assembly. Thus where
there are three outer secondary cams they should
always be at 120° relation to each other, regard
operating circular eccentrics and means for ad
justing said eccentrics to vary the lift caused
thereby and for locking‘ these two eccentrics in
adjusted positions a secondary eccentric assem
bly acted upon by said primary eccentric assem
bly and comprising a unitary inner member hav
ing a plurality of eccentric lobes side by side
spaced around the member equi-angularly and an
outer eccentric on each lobe and means associated
with the secondary assembly keeping said outer
eccentrics spaced apart equi-angularly; recipro
cating elements embracing said outer eccentrics
and means guiding said reciprocating elements
wherebyrelative rotation of the primary and-sec
ondary assemblies in opposite directions causes
secondary assembly is varied. Owing to the fact
conversion of motion, and adjustment of the lock
ing means varies the lift of both primary and sec
that the lobes of the three outer elements of the
ondary assemblies equally.
less of how the stroke resulting from the entire
2. In a straight-line harmonic motion mecha
the outer eccentrics are turning about different 20 nism for converting rotary motion to or from re
ciprocatory motion, driving and driven connec
centers, there are no points on the complemental
tions, cooperating primary and secondary eccen
faces of any two of the outer eccentrics opposite
tric assemblies and reciprocatory elements em
each other which remain in ?xed relation to each
bracing the secondary eccentric assembly, said
other when the lift of the secondary eccentric is
primary assembly comprising a pair of co-operat
ing circular eccentrics and means adjustably con
I have shown in Figs. 9, 10 and 11 a form of
trolling the relation of the two eccentrics rela
means for articulating the outer secondary cams
tively to each other, thereby controlling the lift
so that they are always 120° apart, regardless
of the assembly; said secondary assembly engag
of their relation to the inner secondary cams,
secondary eccentric are set 120° apart, so that
this mechanically preferable construction involv 30 ing said primary eccentric assembly and compris
ing the use of diiferential disks and cranks.
in the side view of Fig. 10 the three secondary
cams Hil, HI, H2 have differential disks H5
located between them which are free to rotate
on the inner secondary member about the com
mon center of that inner secondary member.
These articulating differential disks rotate in re
lation to the inner secondary cam assembly one
full revolution for every full revolution of the
inner secondary eccentric member. While its ro- <
tation is not at a uniform rate, its variable speed
is governed by the relation of the cams with
ing a plurality of circular inner eccentrics in ?xed
equi-anguiar relation to each other about a com-J
mon axis but lacking rigid connection to any
other part of the machine, an outer circular ec
centric surrounding each such inner eccentric
and surrounded in turn by one of the driven or
driving connections and means for guiding said
connections in equi-angularly spaced paths of re
ciprocatory movement, whereby when the lift of
the primary assembly is adjusted the secondary
assembly automatically assumes equal lift.
3. In a straight-line harmonic motion mech
anism for converting rotary motion to or from re
which it is joined by the cranks H6. This can
ciprocatory motion the combination of primary
be seen from Figs. 9 and 11. These cranks H6
and secondary circular eccentric assemblies of
are able to swing radially outward at one end
equal lift adapted to act one on the other, the
as the diameter of the path of the outer sec
primary of said eccentric assemblies comprising
ondary cams increases. It will be observed that
two co-operating circular eccentrics and means
there is a crank H6 from each cam to the adja
associated with said primary eccentric assembly
cent diiferential disk I I5, and another crank
from the differential disk to the cam ring eccen 50 adjustably controlling the lift, the secondary of
said eccentric assemblies lacking rigid connection
tric 0n the other side or the disk. This construc
to any other part of the mechanism and com
tion takes care of itself automatically and keeps
prising a unitary element engaging said primary
the lifts equal. The connections between disks
eccentric assembly‘ and having a plurality of ec
and the eccentrics are necessary because the
centrics rigidly ?xed side by side with their lobes
points of connection are not at the points of
in equi-angular relation to each other about a
intersection of the lift lines of the two eccentrics,
nor are they in common relation to the center
lift line.
common axis, a circular eccentric on each such
lobe and a reciprocatory element surrounding
each such eccentric, means guiding said recipro
It will be seen that the pump which I have de
scribed is one which has no operating crank, and 60 catory element and means maintaining each ec
centric on said lobes in ?xed angular relation to
that I have produced a variable pump in which
the other eccentrics on said lobes, whereby when
two sets of two eccentrics each, with equal effec
tive lift, by working simultaneously in oposite
the lift of the primary eccentric assembly is
changed by its adjustable control, the secondary
directions provide reciprocation of a third mem
ber, but at the same time the individual assem 65 assembly automatically equalizes its lift to that
of the primary assembly.
blies of the sets of eccentrics are variable at will
4. In a straight-line harmonic motion mecha
with relation to each other in a very simple man
nism for converting rotary motion to or from re
ner while the pump is working. It is always
ciprocatory motion, primary and secondary pairs
possible to vary the stroke and keep the effective
eccentricity of one assembly to the other equal, 70 of co-operating circular eccentrics, means adapted
‘to lock the primary pair of eccentrics together,
as is necessary in a device of this type.
said means also being adapted to adjust the lift
What I claim is:
of the said pair of eccentrics by rotating them in
1. In a straight-line mechanism for converting
opposite directions, the secondary pair of eccen
rotary motion to or from reciprocatory motion,
a primary eccentric assembly comprising two co 75 trics comprising an inner group of eccentrics with
lobes arranged in ?xed equi-angular relation to
at‘ all times, whereby the secondary assembly is
each other about a common axis and engaging
one of said primary pair of‘eccentrics and an
outer eccentric group'consisting a circular eccen
tric surrounding each lobe of the inner eccen
tric group, in combination with a driving or driven
maintained in‘ proper timed relation.
7'. In a‘ straight-linereciprocating mechanism
connection embracing each outer eccentric, and
means guiding said connections in equi-angularly
spaced‘paths of reciprocatory movement whereby
when the lift of the primary assembly is adjusted
the secondary assembly automatically equalizes
its lift.
5. In a straight-line reciprocating mechanism
adapted to'change rotary motion to or from re
ciprocatory motion, the provision of four cir
cular eccentrics forming‘ cooperating eccentric
assemblies consisting of pairs of adjacent eccen
tries, the reciprocatory motion being functionally
applied'or received at the periphery of one of said
eccentrics, said pairs of adjacent eccentrics be
ing constructed and arranged‘ to have relatively
opposite rotation as'units to give the conversion
for converting, rota-ry'motion to or from recipro
catory motion, a- primary eccentric assembly ad
justable as to its lift, a secondary or outer eccen
tric assembly comprising an inner member hav
ing‘ a plurality of eccentric lobes side by side
spaced arounda center in ?xed equi-angular rela—>
10 tion, and‘ an outer eccentric on each‘lobe, in com
bination' with means adapted to cause movement
of theinner and outer eccentrics of the secondary
assembly with relation toeach other for the‘pur
pose'of changing the lift of thesecondary assem
bly, and articulating‘means holding said outer
eccentrics together in'equi-angular relation when
the-eccentrics are~rotating oppositely to the inner
secondary member to change the lift.
8; In a straight-line‘ mechanism’ for convert
ing rotary motion to or from reciprocatory mo
tion, the provision of four co-operating circular
eccentrics forming primary and secondary ec
of motion to' or from reciprocatory motion, and
means‘ adapted to cause movement of the two‘
secondary eccentric assembly surrounding said
eccentrics of said pairs equally in' opposite direc
primary eccentric assembly, a yoke surrounding
tions with relation to each other for the purpose
justabl'e as‘ to its’ lift, a secondary or outer ec
centric assembly comprising an inner member
an eccentricv of said secondary assembly to and
from which eccentric the reciprocatory motion
is given or received, means guiding the- recipro
catory movements of said yoke in combination
with adjustable control means adapted to-adjust
the-relative-positions of the- primary pair of ec
centrics to each other and of the secondary pair
of eccentrics to-each other and thereby adjust the
having a plurality of eccentric lobes side by side
lift, whereby the‘ application of motion to the
of changing the length of the reciprocatory move
6'. In‘ a straight-line reciprocating mechanism
for‘ converting rotary motion to or from recipro
catory‘motion, a primary eccentric assembly ad'
centric assemblies of 'pairs of'eccentrics withl'said
spaced around a center‘ in ?xed equi-angular 35 yoke will cause- rotation of one pair with a lift
relation, and an outer eccentric on each lobe, in
equal tothe lift of‘the-other pair of eccentrics.
combination with articulating means linking said
outer eccentrics‘ together in‘ equi-angular relation
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