U.S. patent number 3,673,878 [Application Number 04/888,406] was granted by the patent office on 1972-07-04 for shaft rotating mechanism.
This patent grant is currently assigned to The Globe Tool and Engineering Company. Invention is credited to John M. Biddison.
United States Patent |
3,673,878 |
Biddison |
July 4, 1972 |
**Please see images for:
( Certificate of Correction ) ** |
SHAFT ROTATING MECHANISM
Abstract
The spindle to which an armature is chucked is driven by a drive
shaft stopped at plural different predetermined positions by the
engagement of stop dogs with cams mounted thereon. In one
embodiment there are four cams mounted on the drive shaft for
stopping the drive shaft at any one of four positions for winding
armatures having two coils per slot. The angular positions of the
four cams are pre-adjustable on the drive shaft whereby the
predetermined stopped positions thereof can be changed to
accommodate different types of armatures and different patterns of
wind. Two of the cams are adjustably connected by a sleeve having
gear teeth meshing with gear teeth relatively fixed to one of the
cams and an eccentric connection to the other of the cams. These
cams are rotatable relative to other cams and locked in adjusted
positions by pins projecting through apertures therein. The
apertures are appropriately marked in terms of the types of
armatures and winding patterns. Two other embodiments of relatively
adjustable cams are illustrated. In one embodiment, cams have
radially directed slots, portions of which are aligned to obtain
the desired angular relation between them. In a further embodiment
cams are connected by eccentric pin means used to obtain the
desired relative angular positions. In still another embodiment,
only two relatively adjustable cams are used, but with four stop
dogs, two of which are angularly adjustable. The operation of the
armature rotating mechanism is described for the winding of both
one and two coil per slot armatures. In all embodiments only two of
the dogs are used for stopping the armature at predetermined
positions for winding armatures having only one coil per slot.
Inventors: |
Biddison; John M. (Dayton,
OH) |
Assignee: |
The Globe Tool and Engineering
Company (Dayton, OH)
|
Family
ID: |
25393126 |
Appl.
No.: |
04/888,406 |
Filed: |
December 29, 1969 |
Current U.S.
Class: |
74/125.5; 29/732;
192/48.3; 242/433.3; 242/433.4; 29/597 |
Current CPC
Class: |
H02K
15/09 (20130101); F16D 71/00 (20130101); Y10T
29/53143 (20150115); Y10T 74/1524 (20150115); Y10T
29/49011 (20150115) |
Current International
Class: |
F16D
71/00 (20060101); H02K 15/09 (20060101); H02K
15/08 (20060101); F16d 027/10 () |
Field of
Search: |
;74/125.5 ;242/7.5B,7.5A
;192/48.3 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: O'Dea; William F.
Assistant Examiner: Ratliff, Jr.; Wesley S.
Claims
Having thus described my invention, I claim:
1. A spindle drive mechanism for repeatedly rotating a spindle
about a predetermined axis through predetermined different angular
degrees comprising a drive shaft mounted for rotation about said
predetermined axis, means including a one-way clutch and a slip
clutch coacting between said spindle and said drive shaft and
adapted to drive said spindle upon rotation of said drive shaft,
drive means for rotating said drive shaft through a predetermined
angle in both a forward and a reverse direction, said spindle being
driven by said one-way clutch in the forward direction and by said
slip clutch in the reverse direction, cam means on said drive
shaft, cam follower means following upon said cam means and
selectively operable to stop the rotation of said drive shaft in
the forward direction, and abutment means engageable with a part
fixed in relation to said spindle for stopping rotation of said
spindle in the reverse direction.
2. The apparatus of claim 1 further including a coupling sleeve
connected to one end of said drive shaft and receiving the adjacent
end of said spindle, said one-way clutch and said slip clutch both
coacting between said coupling sleeve and said spindle.
3. A spindle drive mechanism for repeatedly rotating a spindle
through predetermined different angular degrees comprising a drive
shaft, means including a one-way clutch and a slip clutch coacting
between said spindle and said drive shaft and adapted to drive said
spindle upon rotation of said drive shaft, drive means including an
air actuator drivingly engaged with said drive shaft for rotating
said drive shaft through a predetermined angle in both a forward
and a reverse direction, said spindle being driven by said one-way
clutch in the forward direction and by said slip clutch in the
reverse direction, cam means on said drive shaft, said cam means
including a plurality of cams each having a stop surface, cam
follower means following upon said cam means and selectively
operable to stop the rotation of said drive shaft in the forward
direction, said cam follower means comprising stop dogs moved into
engagement with said cams whereupon rotation of said drive shaft in
the forward direction is stopped by engagement of one of said stop
dogs with its associated cam, and abutment means engageable with a
part fixed in relation to said spindle for stopping rotation of
said spindle in the reverse direction.
4. A spindle drive mechanism for repeatedly rotating a spindle
through predetermined different angular degrees comprising a drive
shaft, means including a one-way clutch and a slip clutch coacting
between said spindle and said drive shaft and adapted to drive said
spindle upon rotation of said drive shaft, drive means for rotating
said drive shaft through a predetermined angle in both a forward
and a reverse direction, said spindle being driven by said one-way
clutch in the forward direction and by said slip clutch in the
reverse direction, cam means on said drive shaft, said cam means
comprising at least two cams, one of said cams being affixed to
said drive shaft, the other of said cams being mounted coaxially
with said first cam on said drive shaft and connected to said first
cam by a sleeve affixed to one of said two cams and relatively
adjustable with respect to the other of said two cams, cam follower
means following upon said cam means and selectively operable to
stop the rotation of said drive shaft in the forward direction, and
abutment means engageable with a part fixed in relation to said
spindle for stopping rotation of said spindle in the reverse
direction.
5. The apparatus of claim 4 wherein said sleeve is connected to
said other of said two cams by intermeshing teeth.
6. The apparatus of claim 4 wherein said cam means comprises a
total of four cams there being one cam connected to each of said
two first mentioned cams and relatively adjustable with respect
thereto.
7. The apparatus of claim 4 wherein said cam follower means
includes four cam followers, two adapted to be engaged with each of
said two cams, and two of said cam followers, one for each of said
two cams, being relatively adjustable with respect to the others of
said cam followers about the axis of rotation of said cams.
8. The cam assembly of claim 4 wherein said sleeve is connected by
said teeth to said first of said cams and thereby adjustably fixed
relative to said shaft.
9. A cam assembly for use in controlling the angular rotation of a
shaft, said cam assembly including a first cam affixed to said
shaft, a second cam rotatable upon said shaft, a sleeve
interconnecting said first cam and said second cam, said sleeve
being rotatable upon said shaft and having a first end portion with
peripheral radially outwardly projecting teeth engageable with
inwardly directed teeth affixed in relation to one of said first
and second cams, and said sleeve having a second end portion
adjacent the other of said first and second cams and an eccentric
element interconnecting said second end portion of said sleeve and
said other of said cams.
Description
This invention relates to a shaft rotating mechanism and more
particularly to a shaft rotating mechanism of an armature winding
machine.
In the application of Jerry E. Miller, Ser. No. 704,342, titled
Armature Winding and filed in the U.S. Pat. Office On Feb. 9, 1968,
now U.S. Pat. No. 3,506,864 which application is assigned to the
same owner as the instant application, a winding procedure is
disclosed wherein, after pairs of coils are wound in an armature
and while the fliers are at rest, the armature is rotated in one
direction about its axis to loop the lead wires around the armature
shaft. At some point, the armature rotation is temporarily halted
and a pair of commutator tangs exposed so that the fliers may be
reversed to hook a portion of the lead wires onto a pair of tangs.
As discussed in the aforementioned Miller application, this winding
procedure has several advantages, both in connection with the
armature itself and in connection with the design of the armature
winding machine. In the application of John M. Biddison and Otto F.
Steinke, Ser. No. 746,863, titled Armature Winding, and filed in
the U.S. Pat. Office on July 23, 1968, now U.S. Pat. No. 3,524,601
apparatus is disclosed wherein the armature is chucked to a
spindle, and a detent mechanism, which can conveniently be located
in one of the winding forms, coacts with the teeth of the armature
so that, upon rotation of the spindle in the reverse direction, the
armature is accurately stopped at a predetermined position. The
spindle is positively driven in a forward direction by drive
mechanism including a one-way clutch. In the reverse direction of
rotation the spindle is driven through a slip clutch which slips
when the detent mechanism is engaged with an armature tooth.
An object of this invention is to provide a simple, high speed
shaft rotating mechanism incorporating a one-way clutch and a slip
clutch for driving a spindle in a forward and a reverse direction
and improved means for accurately stopping the spindle after
predetermined degrees of angular rotation thereof. The invention as
described herein is especially designed for use in an armature
winding machine but the invention is generally useful in any
application wherein a shaft is intermittently and repeatedly
rotated through various different predetermined angles.
In accordance with this invention, the driven spindle is driven in
unison or one-to-one relation by a drive shaft. A one-way clutch on
a slip clutch are connected between the drive shaft and the driven
spindle whereupon the spindle is positively driven in a "forward"
direction only. The drive shaft may be rotated by a rack meshing
with a pinion on the drive shaft and designed to permit total
rotation of the drive shaft through an angle in excess of
360.degree.. After the spindle has been rotated in a forward
direction through the total desired angular rotation thereof, the
drive shaft is reversely rotated to reposition it at a start
position. During the reverse rotation of the drive shaft the driven
spindle is stopped, such as by the aforementioned detent
mechanism.
Further in accordance with this invention, the forward rotation of
the drive shaft and, therefore, the driven spindle is stopped at
any one of plural stop positions by dogs which engage notches of
cams mounted on the drive shaft. One of the cams is affixed to the
drive shaft and the other cams are adjustably rotatable relative
thereto. In one embodiment there are only two cams for stopping the
rotation of the drive shaft at any one of four positions, the two
cams each being engaged by a set of two dogs, one dog of each set
being relatively rotatable thereto. In other embodiments there are
four cams, three of the cams being adjustable relative to a cam
affixed to the drive shaft and four fixed dogs, one for each
cam.
Another object of this invention is to provide a simple, high speed
and flexible method and apparatus for repeatedly rotating an
armature during the automatic winding cycle of an armature winding
machine and to insure that the armature is at all times accurately
oriented with respect to the filters and winding forms. The
ultimate positions of the armature being wound with respect to the
winding forms is preferably determined by the aforementioned detent
mechanism because the detent mechanism provides an accurate and
positive stop against one of the armature teeth. When winding an
armature having only one coil per slot, two of the aforementioned
cams and their associated dogs are used, one cam and dog being used
to stop the armature spindle at the position of the armature in
which the fliers are reversed to form the commutator connections.
The other cam and its associated dog are used to stop the armature
substantially at the indexed position thereof wherein it is located
to receive another pair of coils. The latter position is positively
obtained during the reverse rotation of the armature spindle by
means of the detent mechanism. When winding armatures having two
coils per slot, the other two cams and their associated dogs are
also used, one of them to stop the armature at the desired position
for forming the lead wire connections for the first pairs of coils
wound in the armature, the other being used to stop the rotation of
the armature at substantially 360.degree. so that the armature can
appropriately be positioned for receiving the second pair of coils
to be wound in the same pair of slots. The first mentioned cams and
their associated dogs are then used for stopping the armature in
the described positions after the winding of the second pair of
coils in each pair of slots.
Another object of this invention is to provide an improved cam
mechanism having a plurality of relatively adjustable cams fixed on
a shaft for controlling a sequence of events responsive to the
number of degrees of rotation of the shaft. The cams in accordance
with this invention are adjustably rotatable relative to cam
followers while the shaft upon which they are mounted is not
rotating so that the cams may be pre-adjusted. The cam followers
could constitute ordinary followers which follow upon lobed cams,
proximity switches or, as preferred in the armature winding machine
application of this invention, the cams have stop surfaces and the
cam followers or dogs engage the stop surfaces, the events
controlled by the cam mechanisms of this invention being the
stopping of the armature rotation. One cam is fixed on its drive
shaft and the other cams are rotatable relative to the fixed cam
and means are provided to lock all of the rotatable cams relative
to the fixed cam. In another embodiment some of the dogs are
rotated relative to the drive shaft and, hence, to the cams to
obtain the pre-adjustment.
Still another object of this invention is to provide a shaft
position control mechanism including a plurality of relatively
adjustable cams designed to permit raid changes in the relative
positions of the cams and which can be used in an armature winding
machine for quickly and easily changing the setup of the machine.
The shaft position control mechanism includes two sets of cams
interconnected by a sleeve having a toothed connection to one of
the sets of cams and an eccentric connection to the other of the
sets of cams. By partially disassembling the mechanism, the
relative positions of the teeth on the sleeve with respect to the
toothed cam can be changed to provide a coarse adjustment of the
two sets of cams. The eccentric can then be adjusted for a fine
adjustment of the positions of the two sets of cams. If the two
sets of cams each comprise two cams, the two cams of each set can
be interconnected either by pin and slots or eccentrics. One cam of
each set can conveniently be marked with indicia indicating the
event to be controlled.
The shaft position control mechanism is especially useful in a
double flier armature winding machine following the procedure
discussed in the aforementioned Miller application, Ser. No.
704,342. Armature manufacturers frequently wish to change the
operating characteristics of an armature winding machine for
winding various different types of armatures with different winding
patterns. The shaft position control mechanism of this invention
includes relatively adjustable cams and stop dogs which are
pre-adjusted for the winding of armatures having different numbers
of slots and different winding patterns. Because the cam mechanism
can be rapidly pre-adjusted, the setup of the armature winding
machine for winding a particular type of armature with a particular
winding pattern can be accomplished in a matter of moments. The
indicia on the cams of each cam set corresponds to the type of
armature and the winding pattern to be followed.
Other objects and advantages will become apparent from the
following description and the drawings in which:
FIG. 1 is a perspective view of a partially wound armature which
can be wound using the apparatus of this invention;
FIG. 2 is a perspective view with parts broken away and shown in
cross section of a portion of an armature winding machine in
accordance with this invention;
FIG. 3A is a front elevational view with parts in cross section of
a portion of winding forms of the machine of FIG. 2 and showing a
partially wound armature engaged by a detent mechanism;
FIGS. 3B, 3C and 3D are each similar to FIG. 3A and illustrate in
sequence various rotary positions of the armature between the
winding of pairs of coils;
FIG. 4 is a side elevation view with parts in cross section of a
form of apparatus for rotating the armature between the winding of
coils in accordance with this invention;
FIG. 5 is a cross sectional view, with parts broken away, of the
apparatus for rotating the armature between the winding of coils
and taken along line 5--5 of FIG. 4;
FIG. 6 is a rear elevational view of the apparatus for rotating the
armature between the winding of coils;
FIG. 7 is a sectional view of a cam assembly forming part of a
shaft position control mechanism incorporated in the armature
winding machine and taken along section line 7--7 of FIG. 6;
FIGS. 8, 9 and 10 are each elevational views of different
relatively adjustable cams forming part of the shaft position
control cam assembly.
FIG. 11 is a plan view of a pair of modified cams corresponding to
two of the cams of the cam assembly of FIG. 7;
FIG. 12 is an elevational view of the cams of FIG. 11;
FIG. 13 is a plan view of another pair of cams of a different
construction;
FIG. 14 is a front elevational view of the cams of FIG. 13;
FIG. 15 is a plan view with parts broken away and parts shown in
cross section of another embodiment of a shaft position control
mechanism in accordance with this invention;
FIG. 16 is a vertical cross sectional view of the embodiment of
FIG. 15 taken along section line 16--16 thereof;
FIG. 17 is an end elevational view, with parts broken away, of the
embodiment of FIG. 15 as viewed in the direction of arrows 17--17
thereof;
FIG. 18 is a side elevational view with parts omitted and parts in
cross section of another and presently preferred apparatus for
rotating the armature between the winding of coils; and
FIGS. 19 and 20 are cross sectional views of the modification of
FIG. 18 as viewed in the direction of arrows 19--19 and 20--20,
respectively.
For purposes of illustration, an armature, generally designated 10,
is shown in FIG. 1 partially wound as described in the
aforementioned Miller application, Ser. No. 704,342. The armature
10 includes a slotted armature core 12 mounted on an armature shaft
14 upon which a commutator 16 is also mounted. Between the armature
core 12 and the commutator 16 is an insulating sleeve 18 overlying
the shaft 14. Another insulating sleeve 20 projects from an
insulating end lamination 22 on the end of the shaft 14 opposite
from the commutator 16. The armature 10 in FIG. 1 is only partially
wound with coils 24 which have sides passing through spaced
armature slots 26 separated by armature teeth 28. The commutator 16
is of the type having a plurality of peripherally spaced, mutually
insulated segments 30 with hooks or tangs 32 at the ends thereof
adjacent the armature core 12 adapted to receive lead wires 34
which extend between adjacent coils. The armature 10 has twice as
many tangs 32 as there are armature slots 26 because two coils 24
are wound in each pair of slots 26. A commutator or commutator tang
connection is made by a lead wire 34 between each of the pairs of
coils 24 wound in a pair of slots 26 as well as between
successively wound coils 24 in different pairs of slots 26. It will
be noted in FIG. 1 that the lead wires 34 are looped about the
armature shaft 14 and that a portion of each lead wire 34 is also
looped about a commutator tang 32. FIG. 1 shows six coils 24, two
in each of three pairs of slots, and their commutator lead
connections. Of course it will be appreciated that the complete
winding for the armature will include a pair of coils in each of
the armature slots 26.
The armature of FIG. 1 can be wound as follows. Referring to FIG.
2, an unwound armature is first located between a pair of wire
guide wings or winding forms 36 of a double flier armature winding
machine, generally designated 38, the armature being supported
partly by the concavely curved surfaces of the wire guide wings 36
and partly by a chuck assembly 40 gripping the end of the armature
shaft 14 adjacent the commutator 16. The wire guide wings 36 are
mounted upon mounting plates 42 which have bearing housings 44
thereon that rotatably receive flier spindles 46 upon which are
affixed fliers 48. Two wires, designated W, for winding pairs of
coils 24 in the armature slots 26 are coursed through the flier
spindles 46 and around wire guide pulleys 50 on the fliers 48. The
free ends of the wires W are attached to a combined clamp and
cutter mechanism 52. The wires W emanate from wire supplies (not
shown) and are placed under tension at or near the wire supplies so
that, as the fliers 48 rotate, the wires W will be drawn from the
wire supplies and guided by the sloping surfaces of the wire guide
wings 36 to form a pair of coils 24 into pairs of slots 26 aligned
with the wire guiding surfaces of the winding forms 36.
Referring to FIG. 3A, the right hand wire guide wing or winding
form 36 has a cavity 54 therein in which is located a detent
mechanism comprising a pawl support block 56 and a pawl 58
pivotally mounted thereon. The pawl 58 is biased by a coil spring
60 located in the pawl support block 56 toward the armature core 12
whereby the free end of the pawl 58 projects out of the concavely
curved face of the winding form 36 into a slot 26 of the armature
10. Upon rotation of the armature 10 in a counterclockwise
direction, the pawl 58 is cammed out of the slots 26. On a reverse
or clockwise rotation of the armature 10, the pawl 58, upon
entering one of the slots 26, will engage the surface of the
adjacent tooth 28 and thereby positively stop rotation of the
armature 10.
For convenience, the slots 26 in FIGS. 3A, 3B, 3C and 3D have been
separately identified by the numbers "1" through "8." In FIG. 3A it
will be noted that the first pairs of coils 24 have been wound in
slots "1" and "4" and in slots "5" and "8" while the pawl 58 is
engaged with the adjacent surface of the tooth 28 between the slots
"1" and "2." FIG. 2 also shows parts of the machine 38 at the end
of the winding of the first pair of coils 24. The fliers 48 are
stopped adjacent the commutator end of the armature 10 and the lead
wires 34 extend from the wound coils 24 and adjacent the commutator
16 to the flier pulleys 50. At this time and also during the
winding of the coils 24, a tubular tang shield 62, which overlies
the commutator 16 and abuts the free end portions of the tangs 32,
prevents wire from hooking onto any of the tangs 32.
The fliers 48 temporarily remain at rest in the position shown in
FIG. 2, and the armature 10 is rotated, by rotation of the chuck
assembly 40, as will be described below, about its longitudinal
axis through a predetermined angle in a generally counterclockwise
direction. In FIG. 3B, the armature 10 is shown after being rotated
in a counterclockwise direction through such a predetermined angle,
at which time the rotation of the armature 10 is stopped for the
purpose of hooking the lead wires 34 about preselected commutator
tangs 32. The tang shield 62 is, accordingly, retracted so that the
lead wires 34 will be free to engage the tangs 32. At this time the
fliers 48 are rotated in a direction opposite to the direction used
in winding the coils 24 through an angle sufficient to lay a
portion of the lead wires 34 into the bight portions of oppositely
disposed commutator tangs 32. The tang shield 62 is then moved back
into a position whereat it shields the tangs 32 and is effective to
confine the lead wires 34 in the bight portions of the tangs 32.
The counterclockwise rotation of the armature 10 is then resumed
and continued until the armature 10 is a few degrees past the
desired position for aligning the pairs of armature slots 26 to
receive the next pair of coils with the wire guide surfaces of the
winding forms 36. Because the armature 10 illustrated herein has
two coils per slot, the second pair of coils 24 to be wound will be
wound in the same slots, namely slots "1" and "4" and "5" and "8"
as were the first pair of coils 24. Figure FIG. 3C shows the
position of the armature 10 at the end of this counterclockwise
rotation which, as can be determined from a comparison with FIG.
3A, is through an angle in excess of 360.degree.. The
counterclockwise rotation is not so great, however, as to permit
the pawl 58 to enter the slot "3."
After reaching the position shown in FIG. 3C, the armature 10 is
rotated in a reverse direction, that is a clockwise direction as
viewed in FIG. 3C, until the armature 10 reaches the position
illustrated in FIG. 3D at which time the pawl 58 again enters the
armature slot designated "2" and is engaged by the adjacent surface
of the tooth 28 between the slots "1" and "2." The armature 10 is
now in a position to receive the second pair of coils 24. It will
be noted that this position of the armature 10 is predetermined
quite accurately because it relies upon the fixed stop provided by
the pawl 58. Further, the entire detent assembly may be accurately
positioned within the right side winding form 36 by adjusting
screws 64, the adjusted position of which is maintained by jamb
nuts 66.
The foregoing procedure is repeated except that, after the winding
of the next pair of coils 24 in the same pair of slots 26, the
armature 10 will be stopped at a different position so that pairs
of coils 24 will then be wound into different pairs of adjacent
slots 26. Thus, the third pairs of coils wound could be located in
slots "2" and "5" and slots "6" and "1" or else in slots "8" and
"3" and slots "4" and "7."
Those skilled in the art will understand that the foregoing
operations are continued until the armature 10 is fully wound. The
armature 10 is then removed from the winding area between the
winding forms 36 and an unwound armature 10 replaced thereby. It
will also be realized by those skilled in the art that the loading
and unloading of the armature 10 can be accomplished automatically
and that, for example, the cutting of the wire from the wound
armature 10 as well as the handling of the armature 10 after the
winding can be accomplished in various fashions. Suitable hydraulic
or electromechanical drives for synchronously rotating fliers are
known and in use and, therefore, the drive mechanisms for the
fliers 48 are not illustrated in detail herein. U.S. Pat. No.
3,013,737, issued to Harry W. Moore on Dec. 19, 1961, illustrates a
hydraulic drive mechanism which could be used with the apparatus
shown in FIG. 2. It will be appreciated that the wire guide wings
or winding forms 36 must be moved slightly away from the armature
core 12 when the armature 10 is rotated. The same U.S. Pat. No.
3,013,737, shows an air actuator arrangement for accomplishing this
movement.
Those familiar with the armature winding art are aware that
essentially the same procedure for winding armatures having even
numbered slots is followed when winding an armature having an odd
number of slots. However, when winding the so-called "odd-slot"
armature, one flier 48 is normally not rotated while the other
flier 48 is winding the first coil in a pair of slots. Thereafter
the armature is indexed and both fliers then operate to wind the
rest of the coils in an armature as if the armature had an even
number of slots. Of course it will be appreciated that when the
armature winding machine 38 is used to wind different armatures,
certain tooling changes such as the shape of the wire guide wings
36 would necessarily be made.
Referring again to FIG 3A, all the teeth of an armature are
normally identical. Accordingly, when the position of the pawl 58
is properly adjusted to locate pairs of slots in position for
receiving coils, other pairs of slots will be similarly positioned
when the pawl 58 engages any of the other armature teeth. For the
eight slot armature 10, a different pair of armature slots 26 will
be in a proper position to receive a pair of coils when the
armature has been rotated through 45.degree. from that position
illustrated in FIG. 3A. If, instead of the eight slot armature
illustrated, a ten slot armature were to be wound, then it is known
that, after the position of the pawl 58 is properly adjusted for
the winding of coils in a first pair of slots, the armature can
then be successively indexed through increments of 36.degree. for
positioning different pairs of slots to receive subsequently wound
coils. Generally, then, the armature is indexed through an angle
equal to 360.degree. divided by N where N is the number of slots.
This invention provides a shaft rotating mechanism described in
connection with the armature winding machine 38 by which armatures
are rotated and indexed in the manner described above and
incorporates a shaft position control mechanism for accurately
stopping the rotation of the armature. The setup of the shaft
position control mechanism can be rapidly changed so as to
accommodate armatures having various different numbers of
slots.
Referring to FIG. 4, the chuck assembly 40 is shown as including a
collet 68 which grips the armature shaft 14 in response to movement
of a generally tubular collet actuator 70 driven by a collet
operator shaft 72 that extends through a hollow main drive spindle
74. Rotatably mounted on the end of the collet operator shaft 72
remote from the collet 68 is a bearing 78 confined between spaced
bearing retainer rings 80 which together form a yoke ring receiving
confronting drive pins 82 of a double ended yoke 84 pivotally
mounted on a bifurcated bracket 86 (FIGS. 4 and 6). The yoke 84 is
driven by a linear air actuator 88 having a piston rod 90 pivotally
connected to the top of the yoke 84. As apparent, movement of the
collet operator shaft 72 to the left, as viewed in FIG. 4, will
cause the collet actuator 70 to bear against the collet 68. The
collet 68 and the collet actuator 70 are partially surrounded by a
tubular collet retainer 92 which holds the collet 68 in place and
against which the collet actuator 70 is urged. The collet retainer
92 is affixed to the main drive spindle 74 for rotation therewith.
This can be done in any convenient fashion and the lock illustrated
in FIG. 4 is in the form of a clamp ring 94. The main drive spindle
74 is journalled by a bushing 96 and a bearing 98 in a front
stanchion 100 and a rear stanchion 102, respectively, mounted upon
a suitable base or support plate 104. Axial movement of the spindle
74 is prevented by a collar 105 threaded thereon and cooperating
with a clutch disc 122 shouldered against a larger diameter portion
thereof. The aforementioned collet air actuator 88 is mounted on
the rear stanchion 102.
FIG. 4 also shows the aforementioned movable shield 62 which, in
the particular embodiment illustrated, surrounds an adjustably
fixed inner shield 106 to which a guide rod 108 is connected that
projects through an aperture in the front stanchion 100 and which
is held in adjustably fixed position therein by a lock screw 110.
This connection of the guide rod 108 to the front stanchion 100
prevents the inner shield 106 from rotating with the chuck assembly
40. As will be understood by those skilled in the art, the inner
shield 106 has notches at its free end adjacent the commutator
tangs 32 which are to be exposed when the movable shield 62 is
retracted. The inner shield 106, accordingly, prevents the wires W
from accidentally catching on any but the desired exposed tangs 32.
The movable tang shield 62 is advanced and retracted from its tang
shielding position by a shield actuator 112 mounted on the front
stanchion 100 and having a piston rod 114 connected to a bracket
116 that is connected to or integral with the tang shield 62.
With continued reference to FIG. 4, a driven gear 118 coaxial with
the main drive spindle 74 is loosely received thereon between the
two stanchions 100 and 102. The driven gear 118 is connected to the
main drive spindle 74 by a one-way or sprag clutch 120 of
conventional design. The one-way clutch 120 positively drives the
spindle 74 in the "forward" or first direction described above,
that is, counterclockwise as viewed in FIG. 2, but the clutch 120
is free wheeling when the driven gear 118 is rotated in a reverse
direction. Because, as discussed above, it is desired to rotate the
armature 10 through a small angle in a reverse direction after it
has been rotated slightly past its stop position, a slip clutch is
provided between the driven gear 118 and the main drive spindle 74.
The slip clutch includes the clutch disc 122 keyed to the spindle
74 adjacent the driven gear 118 and a friction clutch pad 124 which
may comprise a leather washer or the like interposed between the
rear face of the driven gear 118 and the clutch disc 122 to
constantly maintain engagement of the clutch pad 124 with both the
driven gear 118 and the clutch disc 122. Both the driven gear 118
and the one-way clutch 120 are slidably mounted on the spindle 74.
A coil spring 126 urges the one-way clutch 120 and the driven gear
118 toward the clutch disc 122, that is, to the right as viewed in
FIG. 4. For this purpose the coil spring 126 is shown with one end
engaged with a collar 128 affixed to the spindle 74 and its other
end engaged with a washer 130 abutted against the one-way clutch
120.
The driven gear 118 is driven by a drive gear 132 keyed to a drive
shaft 134 journalled for rotation in the stanchions 100 and 102 and
a support plate 136 which is also mounted upon the base plate 104.
Keyed to the drive shaft 134 is a drive pinion 138 driven by
suitable means such as a vertically reciprocating rack 140 (FIG. 5)
powered by a double acting linear air actuator 142 mounted by a
bracket 144 to a support plate 146 mounted on the stanchion 102.
The piston 148 of the actuator 142 is connected by a coupling 150
to a bracket 154 connected to the rack 140. The bracket 154 has a
vertically extending aperture therethrough receiving a guide sleeve
156 and a bushing 158 slidable upon a vertical guide post 160
extended between the base plate 104 and the air actuator support
bracket 144. As apparent from an inspection of FIG. 5, the driven
gear 118 and, accordingly, the main spindle 74 and chuck 40 will be
rotated in a counterclockwise direction, that is, the "forward"
direction described above, when the piston 148 of the main drive
actuator 142 moves vertically downwardly. For reasons which will
become apparent, the drive shaft 134 and the drive spindle 74 are
driven in unison because the drive ratio between the gears 132 and
118 is one-to-one. Also, the relative dimensions of the drive
pinion 138 and the drive gear 132 are so selected that the total
throw of the piston 148 will cause a counterclockwise rotation of
the main drive spindle 74 through an angle considerably in excess
of 360.degree. .
In accordance with this invention the angular rotation of the main
drive spindle 74 is stopped at predetermined positions by a shaft
position control or cam assembly, generally designated 162, mounted
on the drive shaft 134 and having two sets of stop cams, a first
stop cam set 164 and a second stop cam set 166. The first cam set
164 constitutes a "slot selector" because these cams are used in
stopping the rotation of the main drive spindle 74 in a position
whereat the slots 26 of the armature 10 will be appropriately
positioned with respect to the winding forms 36 for receiving pairs
of coils. The second cam set 166 constitutes a "tang selector"
because the second cam set is used for stopping rotation of the
main drive spindle 74 with the appropriate commutator tangs in
position to receive lead wires.
In the embodiment of this invention illustrated in FIGS. 4 through
10, the first cam set 164 includes a first slot selector cam 168
(FIGS. 7 and 8) affixed to the drive shaft 134 for rotation
therewith. For this purpose the first slot selector cam 168 has a
keyway 169 receiving a key 172. The first cam set 164 also includes
a second slot selector cam 170 mounted on a forwardly extending hub
portion 174 of the first cam 168. As will be described below, the
first slot selector cam 168 constitutes a "second coil stop" and is
used to stop the rotation of the armature after approximately
360.degree. for stopping the armature in a position to receive the
second coil in a given pair of slots. The second slot selector cam
170 constitutes an index cam which stops rotation of the armature
in an indexed position for receiving pairs of coils in slots
adjacent to the slots receiving previously wound coils.
The second cam set 166 includes a first tang selector cam 176 and a
second tang selector cam 178, both of which are rotatably mounted
upon the drive shaft 134. Between the two cam sets 164 and 166 is a
hollow adjusting sleeve 180 received upon the drive shaft 134. The
adjusting sleeve 180 has a forward circular end plate 182, the
outer periphery of which has radially outwardly extending gear
teeth which mesh with radially inwardly extending gear teeth
located on the inner surface of an annular flange 184 projecting
from the rear face of the first slot selector cam 168. The sleeve
180 further has a circular rear plate 186 journalled in a forwardly
extending annular flange 188 on the front face of the first tang
selector cam 176. An eccentric adjustment is provided between the
adjusting sleeve rear plate 186 and the first tang selector cam
176, the eccentric constituting a threaded shank 190 extending
through and snugly received by an aperture in the sleeve rear plate
186 and having a slotted eccentric head 192 received within an
oblong aperture 194 in the first tang selector cam 176. The
eccentric 190, 192 can be releasably locked in position by a lock
nut 196 threaded on the shank 190.
The cam assembly 162 is mounted upon a reduced diameter end portion
of the drive shaft 134 and held thereon by a nut 200 bearing
against a washer 202 and threaded on the rearward end of the drive
shaft 134. In order to adjust the relative rotary positions of the
first cam set 164 and the second cam set 166, the nut 200 is
removed or loosened and the sleeve 180 is moved away from toothed
engagement with the cam 168 of the first cam set 164. The second
cam set 166 and the sleeve 180 can then be rotated through any
desired angle and then reassembled with the teeth of the sleeve 180
again meshed with the teeth of the first slot selector cam 168.
This provides a coarse adjustment. As a matter of convenience there
can be 36 teeth so that adjacent teeth are separated by ten
degrees. Accordingly, as a result of this coarse adjustment, the
relative positions of the two cam sets 164 and 166 should be within
10.degree. of that desired. A fine adjustment can thereafter be
accomplished by rotating the eccentric pin head 192. It will be
observed in FIGS. 6 and 7 that the rearmost cam 178 is cut away to
provide convenient access to the eccentric pin head 192.
The two cams forming each cam set are also relatively rotatable.
The first cams 168 and 176 of both cam sets each have radially
spaced threaded holes 204 and 206, respectively, and the second
cams 170 and 178 of the two cam sets each have a plurality of
apertures 208 and 210, respectively. As will be explained below,
the holes 204 and 206 and the apertures 208 and 210 are so located
that selected ones of the holes and apertures are pre-aligned when
the machine is set up for a particular type of armature. The two
slot selector cams 168 and 170 are held in the pre-aligned,
adjusted rotary position by a pin 212 having a threaded shank
engaged in one of the holes 204 and the two cams 176, 178 forming
the second cam set 166 are similarly held in the desired adjusted
rotary position by a threaded pin 214.
The stop cams have radially extending stop surfaces, designated
168a, 170a, 176a and 178a. These stop surfaces are adapted to be
engaged, respectively, by cam followers comprising first, second,
third and fourth stop dogs 216, 218, 220 and 222 (FIGS. 4 and 6),
all of which are rotatably mounted on a pivot pin 224 supported by
the support plate 136 and a rear support plate 226. FIG. 6 shows
the stop surface 178a stopped against the stop dog 222. When any
one of the cams is so stopped, the main drive actuator 142 stops
driving the rack 140. The stop dogs 216, 218, 220 and 222 are
separately driven by four air actuators 228, 230, 232 and 234,
respectively, the pistons of which are connected by adapters 236
and shoulder bolts 238 to their associated stop dogs. With
reference to FIGS. 4 and 6, the air actuators 228, 230, 232 and 234
are pivotally supported by a pivot pin 240 mounted above the
support plate 104 by spaced stanchions 242.
The operation of the cam assembly 162 during the winding of the
armature 10 is as follows. With reference to FIGS. 3A, 3B, 3C, and
3D, 5, 6 and 7, after the winding of a pair of coils is complete,
as shown in FIG. 3A, the main drive cylinder 142 is energized to
extend its piston 148 whereupon the armature 10 is rotated in a
counterclockwise or "forward" direction. The stop dog 220
associated with the first tang selector cam 176 engages the outer
periphery of the cam 176 shortly after the counterclockwise
rotation of the armature commences. As soon as the cam stop surface
176a engages the stop dog it is positively stopped and the armature
is properly positioned for the first pair of lead wires to be
looped about the commutator tangs upon movement of the fliers 48 as
described above. After the fliers have been rotated to course wires
about a pair of commutator tangs, the stop dog 220 is pivoted away
from its associated cam 176 permitting operation of the drive
mechanism to continue. Shortly thereafter the stop dog 216
associated with the first slot selector cam 168 engages the outer
periphery of that cam so that, when its stop surface 168a strikes
the stop dog 216, the armature rotation is then stopped. Because
the first slot selector cam 168 is keyed to the drive shaft 134,
the drive shaft 134 and, accordingly, the main drive spindle 174
and the armature 10 have undergone substantially 360.degree.
rotation. As discussed above, the rotation is actually slightly
more than 360.degree.. As soon as the armature rotation is stopped,
the cylinder 142 retracts its piston 148 whereupon the drive shaft
134 is rotated in a reverse or counterclockwise direction as viewed
in FIG. 5. At the start of the reverse rotation, the main drive
spindle 74 and the armature 10 are driven through the slip clutch
122, 124 in their reverse or clockwise direction (FIGS. 3C and 5)
but only until the pawl 58 engages against the armature tooth 28
between slots "1" and "2." The main drive cylinder 142 returns its
piston 148 fully to its home position, which is the retracted
position shown in FIG. 5. At this time the armature is properly
positioned for receiving the second pair of coils in the same
slots, that is, with reference to FIG. 3D, slots "1" and "4" and
slots "5" and "8."
After the winding of the second pair of coils in the same pairs of
slots, the main drive cylinder 142 is again energized to extend its
piston 148 causing a forward rotation of the armature 10. At this
time the stop dog 222 engages the second tang selector cam 178,
causing it to stop when its stop surface 178a strikes the dog 222.
The armature 10 is then positioned for the coursing of lead loops
34 about a pair of commutator tangs 32 which are adjacent to those
tangs 32 about which the lead wires were previously looped. After
the lead wires are coursed about the tangs, the stop dog 222 is
retracted to permit continued rotation of the armature 10 in the
forward direction and the stop dog 218 then engages the second slot
selector or index cam 170. When the stop surface 170a of the latter
cam engages the dog 218, the rotation of the armature is again
stopped and the piston 148 of the main drive cylinder 142
retracted, driving the armature in a reverse direction as described
above until the pawl 58 engages another armature tooth 26,
whereupon the armature 10 is now located in a position to receive a
pair of coils in slots adjacent to the slots receiving the
previously wound coils. The foregoing operations of the cam
assembly 162 and the main drive cylinder 142 are repeated between
the winding of pairs of coils until all of the coils for the
armature 10 have been wound.
In setting up the machine to wind a particular armature, the piston
148 of the main drive cylinder 142 is retracted and an armature is
chucked to the main drive spindle 74, then manually rotated until
its commutator tangs are in a proper position to receive lead
wires. At this point the cam sets 162 and 164 are separated and the
first tang selector cam 176 moved to a position whereat its stop
surface 176a would stop against its associated dog 220. The
adjusted position of the first tang selector cam 176 is obtained by
relatively positioning the teeth on the sleeve end plate 182
relative to the teeth within the flange 184 and further adjustment
of the eccentric pin head 192 as discussed above. The relative
adjustment of the second slot selector cam 170 with respect to the
first slot selector cam 168 and the relative adjustment of the
second tang selector cam 170 relative to the first tang selector
cam 176 can be made either before or after the adjustment of the
first tang selector cam 176 relative to the first slot selector cam
168.
The locations of the threaded holes and apertures in the cams 168,
170, 176 and 178 are predetermined as follows. Referring to FIG. 8,
there is one threaded hole 204 for each armature for which the cam
168 is designed. The cam 168 illustrated is designed for use in
winding armatures having any number of eight through 15 slots. The
several threaded holes 204 are located at radially different
distances from the center of the cam 168. To avoid crowding of the
threaded holes 204, they are also located in circumferentially
spaced positions about a centerline CL which is perpendicular to
the diameter of the cam 168 on which the stop surface 168a is
located. In FIG. 8 the threaded holes 204 for the even slot
armatures 8, 10, 12 and 14 are generally diametrically opposed from
the threaded holes 204 for the odd slot armatures 9, 11, 13 and 15
and alternate threaded holes 204 are spaced by 7.5.degree. from,
and on opposite sides of, the aforementioned centerline.
Referring to FIG. 10, the various apertures 210 in the cam 170 for
the various types of armatures are located at the same radial
distances from the center of the cam 170 as are the corresponding
holes 204. Accordingly, when the pin 214 is inserted into one of
the apertures 210 it can only be aligned with one of the holes 204.
In the cam 170 shown in FIG. 10 there are two apertures 210 for
each of the various types of armatures, there being one aperture
210 for each armature representing the "forward" pattern of wind
and one for the "reverse" pattern of wind. The apertures 210 for
the odd slot armatures are generally diametrically opposed from
those for the even slot armatures and, as in the case of the cam
168, the apertures 210 of the cam 170 are generally clustered about
a centerline CL which is perpendicular to the diameter thereof on
which the stop surface 170a is located.
The proper locations of the apertures 210 are determined in the
following manner. Taking the case of an 8-slot armature as an
example, there are 360.degree. divided by eight, or 45.degree.,
between each armature slot. Accordingly, once the first pairs of
slots of an 8-slot armature are accurately positioned to receive
coils, such as the armature 10 is so located in FIG. 3A, it is
known that the armature will have to be indexed through exactly
45.degree. to position adjacent pairs of slots for receiving
subsequently wound coils. Because the stop surface 168a stops
armature rotation after slightly more than 360.degree., it is also
known that, for the 8-slot armature, the stop surface 170a must be
located 45.degree. from the stop surface 168a. Accordingly, the
apertures 210 for the 8-slot armature must be spaced by 45.degree.
from the threaded hole 204 for the 8-slot armature. Since the two
centerlines drawn in FIGS. 8 and 10 are aligned when the stop
surfaces 168a and 170a are aligned, and the holes 204 are spaced
from the aligned centerlines by 7.5.degree., the apertures 210 of
the cam 178a must be spaced from the centerline of the cam 170 by
45.degree. either plus or minus 7.5.degree. depending upon whether
the pattern of wind is forward or reverse. In the "forward" or
progressive pattern of wind, the armature is indexed in a
counterclockwise or forward direction, as viewed in FIG. 3A, for
example, through an angle in excess of 360.degree.. For the
retrogressive or reverse pattern of wind, each index is less than
360.degree.. Since the threaded hole 204 for the 8-slot armature is
already spaced from the centerline CL by 7.5.degree. in effectively
the forward direction, the aperture 210 for an 8-slot armature to
be wound with a forward pattern will be located 45.degree. minus
7.5.degree. for a total of 37.5.degree. from the centerline CL. The
other aperture 210 for the 8-slot reversely wound armature will
correspondingly be located 52.5.degree. from the same centerline.
The apertures 210 for the other types of armatures are similarly
located from the centerline of the cam 170 by the appropriate
number of degrees, the number of degrees being equal to the angles
between slots, plus or minus 7.5.degree.. For another example, the
aperture 210 for the forward wound 10-slot armature is spaced from
the centerline by 43.5.degree. (i.e. 36.degree. plus 7.5.degree.)
and the 10-slot "reverse" aperture 210 is spaced by 28.5.degree.
(i.e. 36.degree. less 7.5.degree.) from the same centerline.
The proper locations of the threaded holes 206 and the apertures
208 in the tang selector cams 176 and 178 are determined in
essentially the same way. Thus, the first tang selector cam 176 has
one threaded hole for each of the 8 though 15 slot armatures. As
described above, the first tang selector cam 176 is properly
preadjusted at the time the armature winding machine is set up for
stopping the rotation of the armature in its appropriate position
for the coursing of lead wires about a pair of tangs. Its stop
surface 176a, accordingly, is angularly offset from the stop
surface 178a by the desired number of degrees for the armature
being wound. Hence, the threaded holes 206 of the first tang
selector cam 176 can be clustered about a centerline of the cam 176
in exactly the same manner as the holes 204 are clustered about the
centerline CL of the cam 168. The proper locations for the
apertures 208 in the second tang selector cam 178 can be computed
based upon the facts that the armature tangs are equally
circumferentially spaced and that there are twice as many tangs as
there are armature slots for armatures wound with two coils per
slot. Again taking the 8-slot armature as an example, the angle
between each pair of tangs is known to be 22.5.degree.. Therefore,
the stop surface 178a must be offset from the stop surface 176a by
22.5.degree.. Accordingly, the apertures 208 are spaced from the
corresponding centerline of the cam 178 by 22.5.degree. plus or
minus 7.5.degree., for a total of either 30.degree. or 15.degree.,
depending upon whether the reverse or forward pattern of wind is to
be used.
The exposed faces of the cams 170 and 178 are desirably marked as
illustrated in FIGS. 10 and 6 with the legends FDW. and REV. as
well as the numbers representing the number of slots in the
armature to be wound. Because so marked, the setup of the portion
of the machine described herein for rotating the armature can be
accomplished in a matter of moments. In practice, contrary to the
illustrations of FIGS. 8 and 9, the faces of the cams 168 and 176
need not be marked.
Those familiar with the armature winding art will be aware that
only the first tang selector cam 176 and the second slot selector
or index cam 170 will be used when winding an armature having only
one coil per slot. The pre-adjustment of the first tang selector
cam 176 and the index cam 170 in preparation for the winding of an
armature having one coil per slot is the same as that described
above.
Those skilled in the art will also be aware that entirely
conventional machine sequence controls may be used to control the
various operations of the machine parts described above. As usual
the operations of the various parts of the machine are sensed by
limit or sensing switches, the operations of which control the
machine's electric and pneumatic circuitry. Examples of the type of
sensing switches are illustrated in FIGS. 4 and 6 wherein a sensing
switch 244 having a pivotal switch arm 246 is associated with the
cam set 164. The switch arm 246 is biased into the path of movement
of a pair of switch engaging plates 248, there being one switch
engaging plate 248 pinned to each of the stop dogs 216 and 218.
Another sensing switch 250 has a pivotal switch arm 252 biased into
the path of switch operating plates 254 mounted on the stop dogs
220 and 222. Both switches 244 and 250 may be fixed on a plate 256
supported on the bed of the machine or the support plate 104 in any
convenient fashion. The sensing switches 244 and 250 may be used,
for example, to signal the release of the associated stop dogs from
their cams. It may also be noted that the main drive actuator 142
may be energized from a relieved source of air under pressure
whereupon the aforementioned stop dogs can positively stop the
rotation of the drive shaft 134 without damage to any of the parts
of the machine. Also valve means (not shown) may be provided in the
pneumatic circuitry for relieving the pressure within the actuator
142 when it is stopped.
Referring to FIGS. 11 and 12, a pair of cams 258 and 260 are shown
to demonstrate an alternative method for relatively adjusting the
two cams of one of the aforementioned cam sets 164 and 166. The cam
258 is provided with a radially directed slot 262 and the cam 260
is provided with a pair of parallel slots 264 and 266 that are also
parallel to a diameter of the cam 260. The two cams are releasably
locked together by a bolt 268 and a lock nut 268a. By loosening the
lock nut 268a, the cam 260 can be rotated when the bolt 268 is
located both in the slot 262 and the slot 264. This rotation would
be adequate to appropriately adjust the relative positions of the
two cams for all armatures wound with a forward pattern of wind. As
apparent, the bolt 268 can be removed and the cam 260 rotated
sufficiently far that a portion of the slot 266 is aligned with a
portion of the slot 262 and the bolt 268 reinserted. As marked in
FIG. 12, the slot 266, when aligned with the slot 262, could
properly position the cam 260 for winding armatures to be wound
with a reverse pattern of wind. Appropriate indicia (not shown)
could be marked either along the slots 264 and 266 or along the
outer periphery of the two cams for indicating the proper alignment
therebetween.
FIGS. 13 and 14 show two other cams 270 and 272 having still
another construction for relative positioning thereof. In this
case, the cam 270 has a "reverse" aperture 274 and a "forward"
aperture 276 whereas the cam 272 has an oblong aperture 278 which
receives a slotted eccentric head 280 of an eccentric shank 282
threaded at one end for receiving a pair of lock nuts 284. As
believed obvious, the lock nuts 284 can be loosened and the
eccentric 280 rotated or else removed from one of the slots 274,
276 and inserted in the other of the slots. The manner of obtaining
the proper relative adjustment of the cams 270 and 272 is deemed
obvious from the foregoing description.
In the embodiments described above there are four relatively
adjustable cams with four stop dogs, each stop dog having a
predetermined fixed stop position. There may be certain advantages
to a different arrangement in which the stop dogs are relatively
moved with respect to relatively fixed cams. FIGS. 15, 16 and 17
illustrate a modified cam assembly, generally designated 286,
having two relatively adjustable cams, a slot selector cam 288 and
a tang selector cam 290. The two cams 288 and 290 are shown mounted
upon a drive shaft 292, which corresponds to the drive shaft 134
above, and held thereon by a nut 294. The two cams have radially
extending stop surfaces 288a and 290a, respectively. The cam 288 is
keyed to the drive shaft 292 whereas the cam 290 is rotatable on
the drive shaft 292. The two cams 288 and 290 are interconnected by
an adjusting sleeve 296 having one end plate with outwardly
projecting teeth 298 meshing with confronting radially inwardly
directed teeth recessed in the cam 288. The sleeve further has
another end plate 300 confronting an oblong hole 302 in the cam 290
for receiving an eccentric member 304. It is apparent from the
foregoing discussion regarding the adjusting sleeve 180 that the
two cams 288 and 290 are relatively adjustable in precisely the
same manner as are the aforementioned first slot selector cam 168
and the first tang selector cam 176.
With continued reference to FIGS. 15 and 16, the stop surface 288a
of the slot selector cam 288 is sufficiently wide that it can be
engaged and stopped by either one of two slot selector stop dogs, a
first slot selector dog 306 and a second slot selector or index dog
308. The stop dog 306 is mounted by a pivot pin 310 to a bracket
312 which in turn is mounted upon a horizontally oriented mounting
plate 314 fixed to a support plate 316 that may be part of the
machine bed. The fixedly mounted first slot selector stop dog 306
is pivotally driven by an air actuator 318 mounted by a pivot pin
320 on a support bracket 322 supported by the mounting plate 316.
In contrast to the relatively fixed mounting of the stop dog 306,
the second slot selector stop dog 308 is pivotally mounted by a
pivot pin 324 upon a rotatable mounting ring 326 received within an
annular recess in the rear face of the mounting plate 314 for
rotation about the axis of the drive shaft 292. The ring 326 may be
held against the mounting plate 314 by retaining plates 328. The
stop dog 308 is pivotally driven by an air actuator 330 which also
is mounted on the rotatable mounting ring 326.
As shown in FIG. 16, the mounting ring 326 has a plurality of
circumferentially spaced apertures 332, all of which are
equidistant from the center of rotation of the drive shaft 292, and
a second set of apertures 334 which are also equidistant from the
center of rotation of the drive shaft 292 but spaced from the
apertures 332. It will be observed that the apertures 332 are
marked in accordance with even numbered slot armatures for both
reverse and forward patterns of wind and the apertures 334 are
marked with odd numbers representing odd slot armatures. Located
behind the mounting ring 326 in the mounting plate 314 are a pair
of radially aligned and spaced threaded holes 336 and 338 which are
at the same radial distance from the center of the drive shaft 292
as are the apertures 332 and 334, respectively. The mounting ring
326 can be rotated relative to the mounting plate 314 to effect a
relative positioning of the stop dog 308 with respect to the stop
dog 306. When adjusted as desired, the mounting ring 326 is locked
in place by a bolt 340 having a threaded shank engaged selectively
in either the aperture 336 or the aperture 338.
The apertures 332 and 334 are located in radially spaced rows to
avoid overcrowding them. The location of the apertures 332, 334
along the rows is determined in essentially the same manner as that
described above in connection with the relatively rotatable cams.
With reference to FIG. 16, if both stop dogs 306 and 308 were
aligned to stop the rotation of the slot selector cam 288 at the
same point an imaginary radial line, designated x--x, on the
mounting ring 326 would be aligned with the radius along which the
threaded holes 336 and 338 are located. The apertures 332 and 334
in the mounting ring 326 are spaced from the imaginary line x--x by
angles struck from the axis of rotation of the drive shaft 292
equal to the desired angle between the ends of the stop dogs 306
and 308. Thus the apertures 334 for the 15-slot armature are
located by an angle equal to 360.degree. divided by 15, or
24.degree., from the imaginary line x--x, there being 24.degree.
between each slot of a 15-slot armature. The remaining apertures
are spaced from the imaginary line x--x by greater angles because,
as the number of armature slots decreases, the angles between slots
increase. There are two clusters of slots 332 and 334 on opposite
sides of the imaginary line x--x to accommodate both the forward
and the reverse patterns of wind. It will be noted in FIG. 16 that
the mounting ring 326 is locked in a position for winding an 8-slot
armature with a reverse pattern.
Associated with the tang selector cam 290 are a pair of stop dogs,
a first tang selector dog 342 and a second tang selector dog 344.
The dogs 342 and 344 are connected to air actuators 346 and 348,
respectively. The first tang selector stop dog 342 is pivotally
mounted upon a bracket 350 and its actuator 346 pivotally mounted
on a bracket 352, both of which are fixed relative to a second
fixed mounting plate 354 mounted on the support plate 316. A
rotatable mounting ring 356 is held by a pair of retaining plates
358 in an annular recess in the mounting plate 354. The air
actuator 348 and its associated stop dog 344 are mounted by pivot
pins 360 and 362, respectively, to the mounting ring 356. Both stop
dogs 342 and 344 can stop against the relatively wide stop surface
290a. Accordingly, adjustment of the stop dog 344 relative to the
stop dog 342 is the same as that described above in connection with
the stop dogs 306 and 308, the mounting ring 356 being held in an
adjustably fixed position on the mounting plate 354 by a pin 364
which extends through a selected hole (not shown) into one of two
apertures (not shown) in the mounting ring 356 and the mounting
plate 354.
The positions of the holes (not shown) that receive the pin 364 are
determined in the same way as the positions of the apertures 332
and 334 except that the holes for the pin 364 will be more closely
spaced since there are twice as many tangs as there are slots in an
armature wound with two coils per slot, these apertures being more
closely spaced for the same reason that the apertures 208 of the
second tang selector cam of FIG. 6 are more closely spaced than the
apertures for the second slot selector or index cam 170 of FIG.
2.
The setup of the device of FIGS. 15 - 17 would proceed
substantially as described above, the tang selector cam 290 being
adjusted with respect to the slot selector cam 288 upon removal of
the nut 294. An armature to be wound would be manually rotated as
previously described to a position for receiving the first pair of
commutator lead wires. With the armature held in this position the
cam 290 would be adjustably moved so that its stop surface 290a
would engage the first tang selector dog 342. This is the position
of the cam 290 shown in FIG. 17. The stop dogs 308 and 344 can be
adjusted by rotation of their mounting rings 326 and 356 either
before or after adjustment of the tang selector cam 290. Of course,
it will be apparent that, when the mechanism of FIGS. 15 - 17 is
set up for winding an armature to have only one coil per slot, it
will only be necessary to relatively adjust the positions of the
two cams 288 and 290 and then to adjust the mounting ring 326
relative to the cam 288 to cause the armature to be indexed through
the desired angle after each coil is wound. When winding an
armature having only one coil per slot, the stop dogs 306 and 342
would not be used.
Another embodiment of a winding machine, generally designated 400,
in accordance with this invention, is illustrated in FIGS. 18 - 20.
The machine 400 includes a drive shaft 402 which in this case is
axially aligned with a driven shaft or spindle 404. Both shafts 402
and 404 are hollow to receive a collet operator shaft 406 extending
the entire combined lengths thereof. The shafts 402, 404 and 406
are mounted in axial alignment by a forward support stanchion 408,
an intermediate support stanchion 410 and a rear support stanchion
412. It will be understood that the support stanchions 408, 410 and
412 are mounted in fixed relation upon the bed of the machine (not
shown), and that the shafts 402, 404 and 406 are journalled in
bearings (not shown) therein.
The driven shaft 404 is driven in unison with the drive shaft 402
in the aforedescribed "forward" direction by means of a coupling,
generally designated 414, including a coupling sleeve 416 shown
connected by screw 418 to the drive shaft 402. The coupling sleeve
416 has a hollow, enlarged forward end receiving the rearward end
of the driven shaft 404 and a one-way sprag clutch 420 which causes
the driven shaft 404 to be rotated in the forward direction when
the sleeve 416 is rotated in the forward direction. The coupling
414 further includes a clutch plate 422 slidably but non-rotatably
connected to the driven shaft 404 by a key 424 and having a rear
face abutting a clutch disc 426 sandwiched between the clutch plate
422 and the forward face of the coupling sleeve 416. The clutch
plate 422 is urged to the rear by a spring 428 coiled about the
driven shaft 404 and located between the front stanchion 408 and
the clutch plate 422. As apparent from the foregoing description,
the clutch plate 422 and the clutch disc 426 provide a slip clutch
causing the driven shaft 404 to be rotated in the reverse direction
when the one-way clutch 420 is ineffective for this purpose. As
mentioned above, the reverse drive of the driven shaft 404 is only
through limited angles until the armature being wound is
appropriately stopped by the pawl 58 (FIG. 3D).
The drive shaft 402 may be driven about its axis by any suitable
means such as a rotary fluid motor and timing belt. In FIG. 18 the
drive is shown to be a rack 430 actuated by an air drive actuator
432 engaged with teeth 434 cut along an intermediate portion of the
drive shaft 402. It will be noted that the forward direction of
rotation of the drive shaft 402 is the same as the forward
direction of rotation of the armature. Because the drive shaft 402
and the driven shaft 404 are coupled for rotation in the same
direction, the forward direction of rotation of the drive shaft 402
is opposite from the direction of rotation of the drive shaft 134
described above. Thus, in FIG. 18 the "forward direction" of
rotation of the drive shaft 402 is "top-going."
Mounted on the forward end of the driven shaft 404 is a chuck
assembly, generally designated 436, which is essentially the same
as the chuck assembly 40 described above. Thus, the chuck assembly
436 includes a collet 438 engaged by a collet actuator 440
operating in a collet retainer 442 pinned to the driven spindle
404. Surrounding the chuck assembly 436 is a notched inner shield
444 held adjustably fixed to the forward stanchion 408 by rod 446
and an outer shield 448 driven by air actuator 450. Also shown in
FIG. 18 is a switch operator 452 connected to a bracket 454
connecting the actuator 450 to the outer shield 448. The switch
operator 452 cooperates with a sensing switch arm 456 for detecting
movement of the outer shield 448.
The collet operator shaft 406 is shown driven by a collet air
actuator 458 mounted on a stanchion 460 that is also fixed to the
bed of the machine. The actuator 458 is coupled to the collet
operator shaft 406 by a coupling, generally designated 462,
including a coupling sleeve 464 threaded on the threaded forward
end of a piston rod 466 of the actuator 458. The sleeve 464 is held
in a fixed position by a lock nut 468. Confined within the coupling
sleeve 464 between the forward end of the piston rod 466 and the
rear end of the collet operator shaft 406 is a thrust bearing 470
which permits the collet operator shaft 406 to rotate with the
armature chucked thereto. When an armature is to be chucked by the
collet 438, the piston rod 466 is extended causing the thrust
bearing 470 to urge the collet operator shaft 406 forwardly, i.e.
to the left in FIG. 18. When it is desired to unchuck an armature,
the piston rod 466 is retracted whereupon an internal shoulder
portion 472 of the sleeve 464 engages a washer 474 fixed on the
rear end of the collet operator shaft 406. The engagement of the
shoulder 472 with the washer 474 causes the collet operator shaft
406 to be moved rearwardly.
The rotation of the drive shaft 402 and, accordingly, the driven
shaft 404 in the forward direction is controlled by a cam assembly,
generally designated 478. For purposes of illustration the cam
assembly 478 is shown to be substantially identical to cam assembly
162 described in connection with FIGS. 4 - 10. Thus, the cam
assembly 478 includes first and second slot selector cams 480 and
482, respectively, first and second tang selector cams 484 and 486,
respectively, and an adjusting sleeve 488 interconnecting the first
slot selector cam 480 and the first tang selector cam 484. As
before, the adjusting sleeve 488 is threadedly connected internally
of an annular flange 490 to the first slot selector cam 480 and
connected by an eccentric 492 to the first tang selector cam 484.
The first slot selector cam 480 is rotatably fixed to the drive
shaft 402 by a key 494. The entire cam assembly 478 is held in
axially fixed position upon the drive shaft 402 between a shoulder
formed by the enlarged intermediate toothed portion 434 thereof and
a nut 496 threaded on an enlarged threaded portion 498 of the drive
shaft 402. Stop dogs 500, 502, 504 and 506 are illustrated in FIG.
18 associated with the cams 480, 482, 484 and 486, respectively.
Because the forward direction of rotation of the cams is opposite
from the cams shown in FIG. 4, the stop dogs 500, 502, 504 and 506
are located on the far side of the cams, as illustrated in FIG. 18,
rather than the near side shown in FIG. 4.
Also because the drive shaft 402 rotates in the same direction as
the driven shaft 404, the cams 480, 482, 484 and 486 are slightly
different from those described above. Referring to FIGS. 19 and 20,
cams 480, 482, 484 and 486 are shown with stop surfaces 480a, 482a,
484a and 486a, respectively, adapted to stop forward rotation
thereof upon engagement with their associated stop dogs. The second
slot selector cam 482 shown in FIG. 19 has a plurality of apertures
508 marked with the number of slots for various armatures to be
wound as well as the forward and reverse pattern of wind. The
apertures 508 are "oppositely" located with respect to the
apertures 210 shown in FIG. 10 because the drive shaft 402 in FIG.
18 rotates in the same direction as the armature. For the same
reason, the second tang selector cam 486 has a plurality of marked
apertures 510 (FIG. 20) located oppositely to the apertures 208 of
the corresponding second tang selector cam 178 shown in FIG. 6. As
before, the second slot selector cam 482 is rotated to an
appropriate position relative to the first slot selector cam 480
and held in the adjusted position by a pin 512 passing through the
desired aperture 508 and threaded into a hole (not shown) in the
first slot selector cam 480. The second tang selector cam 486 may
be identically connected to the first tang selector cam 484 by a
pin 514.
It is believed that the operation of the embodiment shown in FIGS.
18 - 20 is apparent from the 1 - description in connection with
FIGS. 1-17. The embodiment of FIGS. 18 - 20 is preferred because of
the minimal space required for the mechanism which controls the
rotation of the armature being wound and because the one-to-one
gears 118 and 132 described above are omitted.
As mentioned above, the drive shafts can be driven by any suitable
actuator instead of the illustrated racks 140 and 430 driven by the
linear air actuators 142 and 432, respectively. For purposes of
this invention, the actuators need only be capable of
intermittently rotating the drive shafts through angles
sufficiently larger than 360.degree. for correspondingly rotating
the armatures, and then rotating the drive shafts back to their
start positions. When using the described linear air actuators 142
and 432, the reverse rotation thereof can conveniently be
accurately stopped by the "bottoming out" of the actuator pistons
at the end of each return stroke. When using, for example, an air
powered rotary motor, another stop is required for accurately
positioning the drive shaft at the end of its reverse rotation.
Such a stop may comprise a cam fixed to the drive shaft with a stop
surface oppositely directed from the illustrated stop surfaces,
such as those shown in FIGS. 6, 16 and 18, and adapted to be
engaged and thus stopped by an appropriate stop dog.
Although the presently preferred embodiments of the machine have
been described, it will be understood that various changes may be
made within the scope of the appended claims.
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