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Патент USA US3065661

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Nov. 27, 1962
Original Filed Aug. 8, 1955
5 Sheets-Sheet 1
Nov- 27,‘ 1962
Original Filed Aug. 8, 1955
5 Sheets-Sheet 2
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Nov. 27, 1962
Original Filed Aug. 8, 1955
5 Sheets-Sheet 3
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Original Filed 'Aug. 8, 1955
5 Sheets-Sheet 4
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Original Filed Aug. 8, 1955
5 Sheets-Sheet 5
Patented Nov° 27, 1962
The greater cutter 2 is of appreciably larger diameter
than the lesser cutter ring 1, and is supported from and
for rotation with respect to a slightly smaller non-rota
tive cylindrical shell 3 of rather short axial extent. Like
the lesser cutter l, the greater cutter 2 carries peripheral
Max B. Kirkpatrick, Anchorage, Alaska, asslgnor to
Alkirk, Inc, Seattle, Wash., a corporation of Delaware
ly mounted cutter teeth 20 hingedly mounted at 20a to
swing inwardly, and coal breaker elements 21a and 22a.
It mounts also buckets 22 which rotate with the ring 2
and serve to lift material which has been broken loose
and has fallen to the bottom of the bore, for depositing
Original application Aug. 8, 1955, Ser. No. 527,098, new
‘Patent No. 2,864,600, dated Dec. 16, 1958. Divided
and this applicatien Sept. 24, 1958, Ser. No. 763,038
8 Claims. (Cl. 74-674)
This invention relates to motion transmitting mecha
nism and relates particularly to such mechanism having
special planetary gearing and associated braking con
that material into a hopper 30, supported within the shell
3, so that it may pass out the rear end of the hopper,
for discharge onto a suitable chute or conveyor indicated
at C. A rotative feed screw 23 secured to the greater
The invention provides a transmission mechanism that
15 cutter 2 for rotation with the latter serves to advance the
has been found particularly useful in the selective rota
material rearwardly through the shell 3.
tion of different cutters in mining machines of the type
The lesser cutter ring 1 is preferably mounted .at one
disclosed and claimed in my copending application Serial
No. 527,098, ?led August 8, 1955, which has since ma
tured into U.S. Letters Patent No. 2,864,600, dated
December 16, 1958, and reissued as US. Letters Patent
Reissue No. 24,965, and of which the present is a division.
The invention is shown in the accompanying drawings
in a typical form such as is presently preferred by me.
This particular form will be described in this speci?ca 25
tion, and the principles of this invention will be de?ned,
both as related to the illustrated form and to equivalent
forms and constructions, in the appended claims.
end of a reciprocable and axially movable hollow plunger
rod 13, which receives Within its opposite end a ?xed
plunger head or piston 31. The plunger rod 13 is also
rotatable, and the means for rotating the same will be
described later. It will be understood that the applica
tion of pressure ?uid at one side or the other of the
plunger head 31 will e?ect projection ‘or retraction of
the plunger rod 13 and of the lesser cutter which it car
ries at its outer end.
Distributed about the shell 3, closely behind the greater
cutter ring 2, are several in?atable pads 32, faced with
FIGURE 1 is a generally isometric and pictorial view
metal shoes as skids. The lowermost pad 32 serves as
illustrating a mining machine using the transmission 30 a support for the machine as a whole. If all such pads
mechanism of the invention to drive greater and lesser
32, 32a are expanded with maximum force radially
against the wall of the bore they will grip with su?‘icient
FIGURE 2a is a simpli?ed or diagrammatic isometric
force that the machine cannot be displaced axially nor
view, illustrating a portion of the driving or transmission
rotationally. While they are so expanded they constitute
mechanism, with parts‘ all in idling relationship, and
reaction points whence the rotating lesser cutter 1 may
FIGURE 2b is an illustrative diagram showing the rela
be pushed forwardly, cutting its way ahead of the greater
tionship of certain drive parts when they are operatively
cutter 2, which at such a time would be non-rotative.
disconnected as shown in FIGURE 4b.
By expanding the lower pad 32a only sufficiently to sup
FIGURE 3a is a View similar to FIGURE 2a, and
port the weight of the machine, and the remaining pads
FIGURE 3b is a diagram similar to FIGURE 212, these
32 less than is required for gripping, they accomplish the
FIGURES 3a and 3b illustrating the drive mechanism
very important functions of steadying and guiding the
with parts in a drive relationship such as will effect rota
tion of the lesser cutter.
FIGURE 4 is a view similar to FIGURES 2a and 3a,
greater cutter 2, close behind the latter, as the latter ro
tates and .advances. They function similarly to they well
showing the parts in a still further driving relationship,
such as will effect rotation of the greater cutter, and
FIGURE 5 is another similar view, showing parts in a
still further driving relationship, such as will effect simul
cutter 2 be rotated alone or conjointly with the cutter 1.
known catspaws of cylinder-boring machines, whether the
It is this close-up guidance that avoids chattering and
vibration, and leaves a smooth, machined bore.
The lesser cutter 1 also has an in?atable ring 14,
taneous counterrotation of both cutters.
close behind its teeth Elia, but this functions primarily
FIGURE 6 is an axial sectional view through the 50 as an anchorage means. After the lesser cutter has been
machine with particular relation to details of the trans
mission, and FIGURE 7 is a transverse sectional view
stepped back successively along the lines shown in FIG;
URE ‘6 at A, B, C and D, also illustrating details of the
It is believed that the invention will be understood
most readily by, ?rst, describing the principal compo
nents, and then describing its various capabilities and
projected forwardly, while rotating, cutting a bore to the
desired axial extent beyond the. non-advancing, non
rotative greater cutter 2, rotation of the cutter 1 ceases
and the ring 14 is in?ated su?iciently that it grips its
55 bore wall to serve as a reaction point whence the greater
cutter 2, now rotative, can be dragged ahead. As the
greater cutter advances it cuts its way into the vein,
and enlarges the bore. This push-drag procedure can
be repeated, but ordinarily is used only to start a bore,
transmission mechanism and of the effect thereof on the 60 and advance is usually accomplished by effecting simul~
operation of the machine.
taneous counterrotation of the cutters 1 and 2, at like
functions, concluding with a detailed description of the
peripheral speeds, while advancing the machine axially
The lesser cutter ring 1 is a short cylinder, or annulus,
having cutter teeth 10a of suitable shape and material
by traction means 33. Outboard wheels 34 effect guid
ance only, and are not depended upon to resist'vibration.
spaced at angular intervals about its periphery. In ad
Wheels 33, controlled by r-ams 334 are primarily for
dition, there is an inner pilot annulus or stinger 11, also 65
traction by means of the motor 33b, either when the
provided with cutter teeth 10b. These two annuli are
machine is not entered within a bore, or while it is
connected together, as by the spokes 12, for conjoint ro
being advanced within a bore during simultaneous coun
tation, and coal-breaking elements 12a, 11a and 11b are ‘
terrotation, or while it is being backed from a bore.
provided intermediate the annuli l and 11 and within the
latter, to break loose the friable coal left when the cutter 70 Advance of the machine by the push-drag procedure of
?rst pushing the lesser cutter ahead, then anchoring the
teeth Ida and 10b cut narrow annular grooves into the
latter and dragging ahead the greater cutter is normally
face of the seam or vein.
employed only when there is inadequate traction for the
wheel 33. During operation of the machine accord
ing to -the push-drag procedure the wheels 33 can be
retracted from contact with the bore walls, ‘and the
machine is supported wholly upon the lower pad 32a.
'46, which halts rotation of ‘the lesser cutter 1. The
application of these several braking means is under con
trol of an operator such as would ordinarily occupy
the seat S at the rear end of the machine, and who has
his operating handles H and H1 conveniently in front
This serves also as a skid during axial advance of the
‘shell 3 and greater cutter 2.
of him.
Before describing the detailed operation of the trans
Assuming the machine to be about to commence a
mission mechanism thus described in general, it should
new 'bore, the shell 3 is suitably anchored or hacked,
be noted that the ?exible conduit 15, previously men
and the lesser cutter 1 is pushed ahead ‘by thrusting 10 tioned, extends through the plunger means vfrom a con
on the plunger rod 13, while rotating; the greater cutter
nection at 15a to a pressure ?uid source, and at its
2 is held stationary. The cutter 1 cuts its way into the
outer end to the distensible or in?atable ring 14 of the
vein V, until it has advanced as vfar as is practicable.
lesser cutter 1. The connections of 31a and 31b are
When the lesser cutter 1 has advanced as far as is
for application of ?uid under pressure to force the
practicable the ring 14 is expanded with su?icient force
plunger rod 13 inwardly, acting on the annular pressure
to grip the bore wall, and rotation of the lesser cutter
head 31c, or outwardly, acting on the plunger head 31,
1 is stopped ‘by disengaging it from its drive, through
transmission'mechanism still to be described. Through
the transmission the greater cutter 2 is rotated. By re
action from the now-anchored lesser cutter 1, through
the hollow plunger rod 13, the rotating greater cutter 2
in the axial direction. Other pressure ?uid connections,
not shown, will accomplish the distension and permit re
traction of the pads 32 conjointly, and of the pad 32a
alone, all of which are on the non-rotative shell 2.
Valves and valve handles H to control these are also
under control of the operator at his station.
It will now be in order to describe in detail the opera
an the sheel 3 are dragged ahead. The pads 32 and 32a
act as steadying guides close behind the greater cutter
'2. and prevent vibration. When advance of the greater
tion, under varying conditions, of the transmission mecha
cutter has proceeded as'far as is practicable, the original 25 msm.
status is restored, and the lesser cutter may resume its
It will be noted that all three brakes 42, 44; 43, 45 and
advance, reacting from the pads 32 and 32a, or the nor
46, 47 are relased. The main sprocket wheel 4 is rotative,
mal mode of operation may commence, in which both
hence, the planet gears 17a, 18a and 27a, 28a revolve
cutters 1 and 2 rotate simultaneously but oppositely,
about the idler gears 17 and the corresponding sun gear
advance being effected by the Wheel 33 and motor 33b. 30 18, and the idler gear 27 and the corresponding sun gear
The drive for rotating the cutters 1 and 2 is from
28. It being assumed that the cutters 1 and 2 are entered
one or several motors M, which may be electric ‘or hy
within their respective portions of a bore, the sun gears
draulic in character. Electric motors are shown. If
18 and 28 are held stationary against the resistance of the
there be several such motors, and this is preferred be
material with which they are engaged; this holds the
cause of the limitations of space, they would be con 35 gears 18' and 28 stationary. Through the‘planet gears, the
nected by individual or common driving chains 40 to a
idler gears 17 and 27, respectively, merely rotate idly,
common drive sprocket wheel 4. This sprocket wheel
since the corresponding brakes are off. No external
4 is mounted by a bearing 4a to rotate about a rotative
movement occurs. It would be feasible, of course, to
sleeve 19, which in turn is journalled at 37a ‘and 37b
apply the brake at 46, 47, and no harm would result.
within the forward end and the rear cover 37c of a 40
The principle of operation with parts in this operative
‘transmission casing 37 which is ?xed with relation to the
relationship is illustrated in FIGURE 2b, wherein the
stationary shell 3. The internal hollow plunger rod 13
coaxial idler and sun gears 17 and 18 of different diameter
is keyed at 13a to slide axially with relation to the ro—
are straightened out as though they were racks. ‘If we
tative sleeve 19‘, and the latter is, in turn, keyed to a sun
assume that the sun gear 18 is held against rotation, as
gear 18 which is‘ the immediate means for driving the
it is in ‘fact by the resistance of the working face to rota
lesser cutter 1. The greater cutter 2 is supported upon 45 tion of the lesser cutter ring 1, and then roll the planet
the outer end of a rotative sleeve 29, which is keyed
gears 17a, 18a along these ?xed racks through 360° of
at its rear end to the sun gear 28, by which the larger
the gears 17a, 18a, the gear 18a will have advanced a
cutter is caused to rotate. The whole is journalled with
distance along the rack 18 equal to 11' times the pitch di
in the transmission casing 37.
ameter of 18a. The gear 17a, being integral with the
It will be noted that the two sun gears 18 and 28 are
gear 18a, will have advanced along its rack 17 by an
at opposite faces of the main driving sprocket wheel
identical distance. The distance along the rack 17 neces
4. Associated with the sun gear 18 is a coaxial idler
sary for a 360° rotation of gear 17a is, however, shorter
gear 17 slightly larger in diameter than the sun gear 18,
than the distance 18a advances along its rack 18 during
and the two are interconnected by integral planet gears 55 360° of rotation, by the distance (difference) 170. ‘In
17a and 18a (of which there are several sets distributed
order that 17a can keep up with 18a, with which it is
angularly about the sprocket wheel 4) rotative about
integral, the rack 17 must advance through the distance
a common stub shaft 41 which is ?xed with relation to
170. Since the idler gear'1-7 is not braked under the
assumed conditions (see FIGURE 2a), this idler gear 17
and rotative with the driving sprocket wheel 4. A simi~
lar idler gear 27 coaxial with the sun gear 28, and in
rotates with respect to its sun gear 18, in accordance with
tegral connecting planet gears 27a and 28:: on the oppo 60 arrow 17b. The idler gear 17 being free of positive con
site end of the same stub shaft 41, complete the con
nection to the sprocket wheel 4, the lesser cutter 1 does
nection between the gears 28 and 27. The gear 27 in
not rotate. The same situation holds true as to the rota
this instance is somewhat smaller than the sun gear 28,
tion about the gear 218, which is held immovable by the
and the gears 17 and 27 are of like diameter.
resistance applied externally to the greater cutter 2.
A brake drum 42 is fast to the gear 17 and a brake
drum 43 is fast to the gear 27. By application of spiral
brake bands 44 and 45 to the respective drums 42 and
43,, the rotation of the gear 17 or of the gear 27 can
Revolutionof planet gears 27a, 28a effects rotation of the
idler gear 27, but since the brake at 43, 45 is released,
the parts merely rotate idly within the transmission, and
no external movement is effected.
be stopped. Stoppage of gear 17 effects rotation of the
3a illustrates the relationship of parts when
complemental driving gear 18, and of the lesser cutter 70 theFIGURE
lesser cutter 1 alone is rotating. In this view the
1, while stoppage of gear 27 effects rotation of the gear
brake band 44 is applied to the brake drum 42, stopping
28 and of the greater cutter 2. A third brake drum
rotation of the idler gear 17. As the main sprocket
47,.keyed-to an. extension 19a of the rotative sleeve 19,
wheel 4 continues to rotate the planet gears 17a, 18a and
can be stopped by ‘application of expanding brake shoes 75 27a, 28a continue to revolve with the sprocket wheel 4.
Since the brake drum 45 is released from the brake drum
43 and the resistance of the greater cutter 2 to rotation
holds the gear 28 against rotation, as in the case of
FIGURE 2a, the gear 27 and the brake drum 43 continue
the greater cutter 2 While it is rotating, by reaction from
the lesser cutter 1 and its expanded ring 14.
FIGURE 5 indicates the condition which would apply
to rotate as before, as indicated by the arrow 27b, but
tive senses counter to one another.
42, 44.
By proper application of the correctly selected brake
is counter to the sense 1a.
drum and by virtue of the relationship as to siZe of the
rotation of the greater cutter 2 in the sense 2a can be
is stationary, is accomplished, and by expanding the pads
32 tightly during this time and de?ating the ring 14 suffi
ciently that it will steady but not bind, and thrusting
axially forward the plunger rod 13, the lesser cutter 1
erally equal, and the circumferential rate of cutting may
when both cutters are rotated simultaneously and in rota
(This is the pre
ferred mode of operation.) In this instance, the machine
since the brake shoe 46 is released from the brake drum
is advanced as a whole by energization of the motor 33b
47, the hollow plunger rod 13 and the lesser cutter 1 at
applied to the lower wheel 33, or to the several wheels 33.
its outer end are free to rotate, the brake 42, 44 halts
The sprocket wheel 4 continues to rotate as before and
rotation of the idler gear 17, hence, the continued revolu
tion of the planet gears 17a and 18a effects rotation of 10 in the same sense. Brakes 42, 44 and 43, 45 are both
applied, but the'brake 46, 47 is released. It follows that
the sun gear 18 in the sense indicated by the arrow 13b.
the idler gears 17 and 27 are ?xed with relation to the
Since the latter is, in effect, integral with the hollow
shell 3, the ring 14 is de?ated, the pads 32 are de?ated,
plunger rod 13, the latter is caused to rotate in the direc
SU?lClCIlily that they do not bind, although they continue
tion indicated by the arrow 13b, effecting rotation of the
to steady the machine, and pad 32a to support it, and
lesser cutter 1, as at In. Again this is understandable by
both cutters 1 and 2 are free to rotate.
reference to FIGURE 3b. Rolling the planet gears 17a
Revolution of the planet gears 17a and 18a effects
and 18a through 360° along their racks 1'7 and 18 respec
a reaction from the brake-held, now-stationary idler gear
tively, but now with the rack 17 held (by application of
17 to effect rotation of the coaxial gear 18 in the sense
the brake at 42, 44) against rotation, obviously the lesser
distance of 1r times the diameter of 17a as compared to 1r 20 181). In similar fashion, revolution of the planet gears 27a
and 28a effects a reaction from the brake-held, now-sta
times the diameter of 18a will exert a thrust on the rack
tionary idler gear 27 to effect rotation of the gear 28 in
18, tending to displace it in the direction and by the
the sense indicated by the arrow 28b. The gear 18 is
amount indicated at 18b in FIGURE 3b. The gear 18
connected to rotate the lesser cutter 1 in the sense indi
tendsto rotate as shown at 18b in FIGURE 3a, and since
cated at 1a, while rotation of the gear 28 effects rotation ,
the lesser cutter 1 is in effect fast to 18, this lesser cutter
of the greater cutter 2 in the sense indicated at 2a, which
iscaused to rotate against the reaction of the brake at
By proper choice of gear relationships, the rapidity of
idler gear 17 and sun gear 18 and of, the connected integral 30 somewhat less than the rapidity of rotation of the lesser
cutter 1 in the sense 1a, so that, in effect, the torques
planet gears 17a and 18a, it is seen above that rotation
produced by the two cutters 1 and 2 are counter and gen
of the single lesser cutter 1, while the greater cutter 2
be made equal. In this manner, the two cutters 1 and 2
neutralize each other, consequently, there is no need for
provision to otherwise neutralize the torque. The ma
chine as a 'whole is readily advanced along the bore by
cuts as it rotates and advances, reacting from the grip
the motor 33b; meanwhile the cutters cut their Way into
afforded by the pads 32 on the exterior of the bore which
the bore, the loosened material being deposited within the
has been cut by the greater cutter 2.
‘Coming now to FIGURE 4, this illustrates the situation 40 hopper 30 by means of the buckets 22 and so being re
moved at the rear end of the hopper 30 by means of the
wherein the lesser cutter 1 has advanced as far as it is
chute C or other convenient means.
desired to advance it for the time being, and is held
The invention may be embodied in other speci?c forms
stationary by the expansion of the ring 14. The pads 32
without departing from the spirit or essential character
have now been de?ated sufficiently that they steady but
do not bind, and the greater cutter 2 is rotating in the 45 istics thereof. The present embodiment is therefore to be
considered in all respects as illustrative and not restric
sense indicated by the arrow 2a which, it will be noted
tive, the scope of the invention being indicated by the ap
by comparison with FIGURE 3a, is counter to the sense
pended claims rather than by the foregoing description,
of rotation 1a for the cutter 1 in the latter ?gure.
and all changes which come within the meaning and range
To accomplish the rotation 2a in FIGURE 4, the still
rotation sprocket wheel 4 is connected to the sun gear 50 of equivalency of the claims are therefore intended to be
embraced therein.
28, the brakes 43, 45 and 46, 4'7 are engaged, as indicated
in FIGURE 4, but the brake 42, 44 is released. Release
What is claimed and desired to be secured by United
of the brake 42, '44 enables the idler gear 17 to rotate
States Letters Patent is:
idly, reacting from the gear 18, which is held against ro
tation by the external reaction applied to the lesser cutter
1, but the revolution of the planet gears 27a and 23a.
effects a reaction from the now-stationary idler gear 27,
held by the applied brake 43, 45, to effect rotation of the
gear 28 by reaction from the now-stationary gear 27.
1. Transmission mechanism for rotating either or both
of coaxial inner and outer members, comprising two sun
gears each ?xed for rotation with its respective one of said
members, idler gears coaxial with and respectively adja
cent each sun gear, a drive wheel rotatably supported on
one of said members coaxial with the sun and idler gears,
Rotation of the gear 28 is effected in the rotative sense 60 two pairs of conjointly rotative and operatively connected
planet pinion gears mounted upon and revoluble with the
indicated as 23b in FIGURE 4, consequently, the sleeve
drive wheel, the individual pinions of one pair intermesh
29 is rotated in the sense indicated by the arrow 2%, and
ing with the sun gear and idler gear, respectively, of the
effects rotation of the greater cutter 2 in the sense indi
inner member, and the individual pinions of the other
cated by the arrow 2a. A diagram similar to FIGURES
pair intermeshing with the sun gear and idler gear, respec
2b or 3b could be drawn to indicate how this is accom
tively, of the outer member, brake means selectively ap
plished, but the principle has been indicated in the dia
plicable to halt rotation of either idler gear, and further
grams in FIGURES 2a and 3b, and it is believed to be
brake means applicable to halt rotation of the inner
unnecssary in connection with FIGURES 4 and 5.
In FIGURE 4, then, the lesser cutter 1 having been 70
2. A transmission mechanism as in claim 1, wherein
advanced to the limit of its desired axial advance for the
said outer member is tubular and extends in telescoping
time being, and being held non-rotative by tight expansion
relation over said inner member, and said drive wheel
of the ring 14, the greater cutter 2 is rotated and mean
is mounted on said inner member.
3. Motion transmitting mechanism comprising a ro
while is being advanced by aplication of pressure to the
proper side of the plunger 31, to effect axial advance of 75 tatable power transmitting member, two power transmit
ting shafts, one being hollow and the other extending
pound gears journalled onsaid' member and each com
pound gear having one gear section meshed with said
therethrough, coaxial rotatable sun gears ?xed on the re
spective shafts adjacent said member, a rotatable idler
other sun gear and another gear section meshed with the
gear rotatably mounted on each said shaft coaxial with
associated idler gear and means for selectively braking
said sun gears, means rotatably supporting said member C21 each of said idler gears.
on one of said shafts, a system of planet gearing carried
6. In the motion transmitting mechanism de?ned in
by said member and interconnecting each sun gear With
claim 5, the compound planet gears of the ?rst plurality
its associated idler gear and brake means for selectively
being coaxial with compound‘ gears of the second plu
arresting rotation of either idler gear.
4. Motion transmitting mechanism comprising a sup
port, two coaxial shafts rotatably mounted on said sup
port, a rotatable power transmitting member rotatably
supported on one of said shafts, sun gears coaxial with
7. In the motion transmitting mechanism de?ned in
claim 6, said coaxial compound gears being rotatably
mounted on a common shaft rigid with said rotatable
power transmitting member.
said member and rigidly mounted on the respective shafts
_ 8. In a power transmission, a support, two coaxial
at opposite sides of said‘ member, idler gears rotatably 15 power output members rotatably mounted on said sup
mounted on the respective shafts adjacent each sun gear,
port, a power input member, bearing means supporting
a plurality of compound planet gears rotatably mounted
said input member on one of said output members ad
on said member and interposed between and meshed with
jacent one end of the other output member, two sun
each sun gearland its associated idler gear and means
gears, one rigid with each output member and disposed
for selectively braking rotation of either idler gear.
20 on opposite sides of the input member, idler gears jour
5. Motion transmitting mechanism comprising a sup
nalled on the output members adjacent the sun gears,
port, two coaxial shafts rotatably mounted on said sup
compound planet gears mounted on the input member and
port, one of said shafts being hollow and the other ex
operably connecting the respective sun and idler gears,
tending therethrough, a rotatable power transmitting
brake means for selectively arresting the idler gears, and
rotatably mounted on the respective shafts at opposite 25 a bearinginterposed between the other ends of said‘ out
sides of said member coaxial with said member, idler
put members.
gears rotatably mounted on the respective shafts coax
ially of said sun gears, a ?rst planet gearing connecting
References Cited in the ?le of this patent
one of said sun gears with its associated idler gear com- ,
prising a ?rst plurality of compound’ gears journalled on 30
said member and each compound gear having one gear
member journalled on the inner of said shafts, sun gears
section meshed with said one sun gear and another gear
section meshed with the associated idler gear, a second
planet gearing interconnecting the other sun gear with
its associated idler comprising a second plurality of com
Twomley _______ _'__..__ Aug. 21, 1923
Seybold ____________ __ Mar. 13, 1956
France ______________ __ Oct. 22, 1929
‘Italy _' _______________ __ Mar. 24, 1939
Patent No, 3,065@65l
November 27, 1962
Max B. Kirkpatrick
It is hereby certified that error appears in the above numbered pat
ent requiring correction and that the said Letters Patent should read as
corrected below.
Column 3, line 22, for "sheel" read —— shell ——; column 4!
line 27, for "relased" read —— released ——; column 7, line 32,
strike out "member journalled on the inner of said shafts, sun
Signed and sealed this 12th day of November 1963.
Attesting Officer
AC ting Commissioner of Patents
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