4361 4365.output

* GB784768 (A)
Description: GB784768 (A)
No title available
Description of GB784768 (A)
COMPLETE SPECIFICATION
Improvements in or relating to the Balancing of Dynamically Unbalanced
Bodies.
We, GENERAL MOTORS CORPORATION, a Company incorporated under the laws
of the
State of Delaware in the United-States of
America, of Grand Boulevard in the City of
Detroit, State of Michigan, in the United
States of America (Assignees of JOSEPH F.
LAsN) - -do hereby declare the invention for which we pray that a
patent may be granted to us and the method by which it is to be
performed, to be particularly described in and by the following
statement:-
This invention relates to the balancing of dynamically unbalanced
bodies such as crank-shafts.
From one aspect the invention is an apparatus for automatically
determining the magnitude and angular location of unbalance in a
dynamically unbalanced body and from another aspect the invention is
an apparatus for automatically determining the magnitude and angular
location of the unbalance in a dynamically unbalanced body,
in-association with means for automatically correcting such unbalance.
The invention is particularly suitable for use in engine assembly or
finish balancing installations in which the crankshaft is
automaticalfy checked for unbalance when installed in an engine and
any unbalance in the shaft, as well as such unbalance as may be
contributed thereto by the other components of the engine associated
with the shaft, is automatically corrected in the assembled condition
of the engine.
The invention has among its general objects to provide such apparatus
in accordance with the above which is characterised by extreme

simplicity of construction and of operation and, yet, is possessed of
sufficient sensitivity and accuracy required for high production
balancing installations.
A dynamic unbalance determination apparatus according to the invention
enables automatic determination of both the magnitude and the angular
location of unbalance to be made without requiring an operator to
adjust dials, read instruments and interpret readings.
The scope of the invention is indicated by the appended claims; and
how it can be performed is hereinafter particularly described with
reference to the accompanying drawing which shows diagrammatically an
automatic dynamic unbalance determination apparatus and associated
balance correction apparatus in accordance with the present invention.
In the drawing, 10 is an engine which has a crankshaft 12 and is
mounted with the sump cover removed in an oscillatable engine cradle
14. 16 is a constant speed electric drive motor, the shaft 18 of which
carries a wheel 20 and is suitably coupled to the engine crankshaft 12
to rotate the latter in the cradle or stand. 22 and 24 are vibration
pickups each of which is associated with an unbalance magnitude and
location determination apparatus and an element of an unbalance mag-
nitude correction device in accordance with the present invention,
only one set of the unbalance determination apparatus and the element
of anunbalance magnitude correction device for one of the pickups
being shown in the drawing.
The engine stand or cradle 14 is of a kind employed in conventional
balancer installations and is mounted on resilient or oscillatable
supports while permit movement of the cradle and engine due to
unbalance effects in either end of the crankshaft in an axial plane of
the shaft and the vibration pickups. In accordance with conventional
balancing practice, the crankshaft is coupled to the shaft 18 of the
drive motor through a coupling arrangement such as the pair of spaced
universal joints shown at 30.
The vibration pickups 22 and 24 are mounted transversely to the axis
of the crankshaft and at axially spaced points along the length of the
cradle 14 corresponding to the mechanical nodal points of the
unbalance forces at the respective ends of the crankshaft The pickups
22, 24 are conventional electromagiieetic devices each of which
generates an alternating current signal and, by reason of said nodal
point mounting, are unaffected by the unbalance influence of the
opposite end of the crankshaft. The alternating current signal from
each of the pickup devices 22, 24 has a frequency equal to the
rotational speed at which the crankshaft is driven and an amplitude
proportional to the total unbalance effect produced by the end
of the crankshaft adjacent the pickup. Each pickup signal further
includes a phase displacement characteristic related to the angular

location of the total unbalance from a fixed reference point on the
surface of the shaft and
contained in a transaxial correction plane extending through an end
counterweight of
the crankshaft, there being two such correc
tion planes, one at each end of the shaft.
Pickup 22, together with the apparatus
associated therewith, is adapted, therefore, to
sense the characteristics of unbalance at the
left end of the shaft and has its output ampli
fied in an amplifier 34 the output of which is
applied through conductors 36, 38 to a first
chopper or unbalance angle relay contactor
device 40 which includes a transformer 42
having a primary winding 44 connected to
conductors 36, 38 and a centre-tapped
secondary winding 46 associated with a relay
48 having a pair of stationary contacts 50, 52
and a movable switch arm 54 operable be
tween said contacts by an energisable relay
coil 56.
Relay coil 56 is connected for energisation
in a circuit which is alternately completed and
interrupted by one of a pair of circuit
interrupting switches S-l and S-2 of a contact
mechanism which is indicated generally at 64
and comprises a pair of rotatable axially
spaced cam elements 66, 68 oriented 90
degrees in space relative to one another and
mounted on a shaft 69 coupled to the drive
motor 16 and driven in synchronism with the
crankshaft 12. Each cam 66, 68 has asso
ciated therewith a pair of circuit contacts 70,
72 and 74, 76 which are stationary relative to
the cams and are alternately closed and
opened during each revolution of the shaft
69. Suitable ganged means 78 associated with
the cams 66, 68 and including a control knob
80 is provided for angular displacing the
cams relative to their contacts so as to alter
the commencement of the half period during
which the contacts 70, 72 and 74, 76 are closed
and opened relative to the fixed reference
point on the crankshaft.

The energising circuit for relay coil 56 in
cludes conductor 82, a source of power such
as battery 84, conductor 86, contacts 70, 72
and conductor 88. The movable switch arm
54 of the relay 48 is thus alternately moved
between its contacts 50, 52 to provide a
reversing or commutating action of the ampli
fied pickup signal. This commutated signal
appears in the output of the unbalance angle relay contactor device 40
between conductors
90 and 92, which are connected to switch arm
54 and the centre tap of the transformer
secondary winding, respectively, and may be
displayed on a zero centre D,C. milliameter
94 connected between conductors 90 and 92.
Rotation of the control knob 80 to adjust the
position of the cams 66 and 68 with respect to
the crankshaft 12 will cause the amplitude of
the full wave rectified signal displayed on
meter 94 to vary from zero to maximum. The
control knob 80 is provided with angular
graduations thereon so that its angular dis
placement relative to a reference pointer 96
on a stationary panel or the frame 98 of the
contact mechanism 64 may be read for a zero
or null reading of meter 94 as an indication of
the angular location of the unbalance in the
- left end of the crankshaft. While the knob
80 may be adjusted by an operator to effect
a null reading of the meter as in an open loop
step sequence system, it is preferred to employ
automatic positioning of the contact mech
anism, as will be described.
The amplitude or magnitude of the total
unbalance at the left end of the shaft is
determined by applying the amplified pickup
signal appearing at the output of amplifier 34
to a second chopper or unbalance amplitude
relay contactor device 100 which is similar to
chopper 40 and includes a transformer 102
having a primary winding 104 and a centre)
tapped secondary winding 106 and a relay
108 with a switch arm 110 movable between
a pair of stationary contacts 112 and 114 by an

energisable actuator coil 116. Actuator coil
116 is contacted in an energisable circuit :
which includes conductor 118, battery 120,
conductor 122, contacts 74, 76 of contact
mechanism 64 and conductor 124.
The commutated output of the second
chopper 100 is taken from the centre tapped]
winding 106 and switch arm 110 and applied
as a full wave rectified signal through conduc
tors 130, 132 to a closed loop servo controlled
amplitude comparison circuit which auto
matically indicates the magnitude of the un-i
balance quantity and positions an adjustable
drill stop setting element 134 of a balance
correction drilling apparatus associated with
the unbalance determination apparatus to
effect exact compensation for the amount of :
the unbalance at the left end of the shaft. The
amplitude comparison and drill stop position
ing apparatus includes a conventional servo
amplifier 136 and its associated two-phase
servo positioning motor 138 and a poten-:
tiometer arrangement comprising the ad
justable resistor 140 connected across a fixed.
known reference source of balance voltage.
shown as battery 142. The output of the
second chopper 100 is connected in series with the input of the servo
amplifier and the portion of the output of the.potentiometer appearing
between conductor 132 and the adjustable arm 144 of the potentiometer
resistor 140, which is mechanically coupled to the shaft 146 of the
servo motor 138.
One of the phase windings of the servo motor 138 is connected for
energisation from a local alternating current source of supply and the
other quadrature phase winding thereof is connected for energisation
by a control signal, which appears at the output of the servo
amplifier 136 and corresponds to the amplitude difference between the
output of the chopper 100 and the potentiometer. The resulting
differential control signal is of such magnitude and polarity as to
tend to rotate the- unbalance servo motor 138 in a direction and by an
amount such as to reduce the error or control signal to zero, -at
which point the amplitude comparison system will be balanced and the
motor or translating device will cease moving.
An indicator in the form of-a graduated indicator dial, which may be
provided on, say; the stator casing of the servo motor 138, and a

pointer carried by the shaft 146 may be employed to indicate the
magnitude of the unbalance. The shaft 146 of the unbalance servo motor
138 is directly coupled to the drill depth control element 134 of a
balance correction drilling apparatus or equivalent balance correction
apparatus which is mounted under the engine assembly, and adjusts the
drill depth setting element automatically in accordance with the
determination af the magnitude of unbalance. It will be noted that
both the unbalance magnitude determination and the setting of the
drill control element 134 are performed automatically without human
intervention.
To provide for automatic adjustment of the knob 80 of the contact
mechanism 64, the output of the first or unbalance angle relay 40 is
applied to the input of a servo amplifier 177 of a servo positioning
system, thereby dispensing with this previously manually performed
operation. The output of the servo amplifier 177 is connected by
conductors 179 and 181 to the variably energised phase windings of an
angle positioning servo motor 183 whose rotor shaft 185 is geared to
the rotatable knob 80 of the contact mechanism 64.
The apparatus may further include still another servo positioning
arrangement for angularly positioning the handwheel 20 upon conclusion
of the unbalance determination operation to correspond to the extent
of rotation of the unbalance angle servo motor 183 when the relay
contactor 40 was adjusted to balance, and thereby to locate the
crankshaft 12 in proper relation to the balance correction apparatus.
This last-mentioned crankshaft positioning arrangementmay include a
synchro transmitter device 187, the rotor shaft 189 of wliich is
coupled to the shaft 185 of the servo motor 183; a synchro receiver
device 191 the three-phase stator winding of which is electrically
connected to the three-phase stator winding of the transmitter device
187 by conductors 193, 195, 197; a servo-amplifier 199 the input
terminals of which are connected to the rotor winding of the receiver
synchro device 191 by conductors 201 and 203; -and a two-phase power
servo positioning motor 205 the control phase winding of which is
connected to the output of the servo amplifier 199 by conductors 207
and 209. The other winding of the servo motor 205 is energised from a
local alternating current power -source. The rotor shaft 211 of this
servo positioning -motor is coupled through gearing-213 to the wheel
20 or to the crankshaft 12 itself and through gearing 217 to the shaft
of the synchro receiver in the manner of synchro-controlled servo
positioning arrangements. A switch 215 may be provided in one of the
A.C. source conductors of the position transmitter device 187 and is
adapted to be closed to energise this data transmission system-at the
conclusion of the unbalance determining cycle when the drive motor 16
stops rotating, at which time the control phase winding of the servo

motor 205 will be energised to servo position the wheel 20 in
accordance with the determined angle of unbalance location for the
left end of the shaft.
The two cams 66 and 68 of the contact mechanism 64 both move as the
servo motor 183 automatically adjusts the control knob 80 of the
contact mechanism 64 for zero or null reading on the D.C. meter 94.
The output of chopper 40 associated with the unbalance location or
angle determination portion of the apparatus is then zero while that
of chopper 100 associated with the quadrature related cam 68 of the
unbalance magnitude determining portion of the apparatus will be a
maximum. The unbalance servo motor 138 controlled from the unbalance
magnitude relay contactor 100 adjusts the drill depth control element
134, and after the drive motor has been stopped, the synchro data
transfer system 187, 191 is energised to con trol servo motor 205
which adjusts the hand wheel 20 to position the exposed counterweight
of the crankshaft, where one of the balance corrections is to be
performed, over the drill bit of the drilling apparatus mounted below
the engine stand and thereafter energises the drill motor and
transmission apparatus thereof to remove an amount of metal
corresponding to the setting of the automatically adjusted drill depth
control element 134 from the counterweight in the left end correction
plane. The operation is repeated for the right end of the shaft with
similar apparatus associated with pickup 24.
The use of the chopper integrator apparatus for the unbalance
magnitude and angle determination apparatus simplifies difficult
filtering problems that otherwise would be presented and assures that
the unbalance signal obtained from the outputs of the choppers 40,
100will be unaffected by and independent of all frequencies other than
the fundamental frequency determined by the speed of shaft 69. In
short, the choppers 40, 100 act as very narrow band pass filters.
Pickup 24 is adapted to sense unbalance effects in the right end of
the crankshaft and will have its output applied to an unbalance
determination and drill depth control apparatus including a second
contact mechanism and a second set of angle location and unbalance
magnitude choppers and associated positioning apparatus identical with
that associated with pickup 22, the illustration of which has been
omitted for simplicity of the drawing.
While the present invention has been shown and described herein as
applied to the unbalance detection and correction ofunbalance in two-
arbitrarily selected transaxial planes of correction in elongated
bodies such as crankshafts, it is apparent that the principles and
apparatus of the present invention are equally applicable to the
automatic detection and correction of unbalance in bodies in which the
unbalance is located in but a single transaxial plane.

What we claim is:
1. Apparatus for automatically determining the unbalance of a
dynamically unbalanced body, comprising a device for supporting the
body for rotation about its axis, drive mechanism including a
rotatable shaft coupled to said body for rotating it on its axis,
vibration pickup means responsive to vibrations induced by unbalance
in said body and developing a periodically varying electrical signal
having a phase and amplitude related to the angular location and
magnitude of unbalance in said body, a commutator chopper device
having an input circuit connected to said vibration pickup means and
an output circuit, a variable contact mechanism controlling the output
from said chopper device and including a cam driven by said drive
means in synchronism with said body, a pair of switch contacts adapted
to be actuated by said cam and adjustable means for changing the
position in space of said switch contacts relative to said cam, said
switch contacts being connected in circuit controlling relation with
said chopper device, and servo positioning means connected to the
output of said chopper device for automatically adjusting said
adjustable means of said variable contact mechanism.
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* 5.8.23.4; 93p
* GB784769 (A)
Description: GB784769 (A) ? 1957-10-16
Improvements in bead wrapping machine
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US2855976 (A)

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The EPO does not accept any responsibility for the accuracy of data
and information originating from other authorities than the EPO; in
particular, the EPO does not guarantee that they are complete,
up-to-date or fit for specific purposes.
PATENT SPECIFICATION
784,769 Date of Application and filing Complete Specification: Nov 28,
1955.
No 33981155.
Application made in United States of America on Dec 13, 1954.
Complete Specification Published: Oct 16, 1957.
Index at Acceptance:-Class 144 ( 1), B 4 E.
International Classification:-B 62 g.
Improvements in Bead Wrapping Machine.
We, UNITED STATES RUBBER COMPANY, of Rockefeller Center, 1230 Avenue
of the Americas, New York, State of New York, United States of
America, a corporation organized and existing under the laws of the
State of New' Jersey, United States of America do hereby declare the
invention, for which we pray that a patent may be granted to us, and
the method by which it is to be performed, to be particularly
described in and by the following statement:-
This invention relates to a machine intended for use in applying
rubberized tape to a bead wire bundle such as used in the manufacture
of pneumatic tires, but suitable for applying tacky tape to other
annular shaped articles.
Among the objects of the invention is to provide such a machine that
will automatically accommodate bead wire bundles of varying radial
thicknesses without the necessity of manual adjustment; which will
automatically measure and sever the tape to desired lengths; which
will automatically feed the tape to the point of application thereof
to the bead wire bundles; and which will automatically eject the bead
wire bundles from the machine upon the completion of the wrapping
thereof.
Other objects and advantages of the invention will become apparent
from the following description when read in conjunction with the
accompanying drawings wherein:
Fig 1 is a side elevational view of the machine of the invention; Fig

2 is a partial front elevational view of the machine looking in the
direction of the arrows II-II of Fig 1; Fig 3 is a top plan view of
the machine; Fig 4 is a sectional view taken on the line IV-IV of Fig
2 showing the details of the main bead driving and wrapping wheel of
the machine; Figs 5-9 are partial sectional views of portions of the
machine illustrating the sequential lPrice 3 s 6 d l operations of the
machine in wrapping a bead wire bundle; Fig 5 showing the wrapping of
three sides of the bead wire bundle; Fig 6 showing the folding of one
edge of the tape over the remaining side; Fig 7 showing the 50
stitching of the first turned edge; Fig 8 showing the folding over of
the remaining edge of the tape; and Fig 9 showing the stitching of the
second turned edge of the tape; and 55 Fig 10 is a diagram of the
fluid and electrical control system for the machine.
Referring to the drawings and in particular to Figs 1 and 2, the
intended function of the machine is to wrap a length of tacky rub 60
berized tape T (Figs 1 and 2) around a bead wire bundle or coil B (Fig
2).
BEAD WRAPPING MECHANISM The portion of the machine which performs the
wrapping of the bead B includes a bead 65 driving and wrapping wheel
10 comprising axially spaced radial flanges 10 a and 10 b between
which the bead wire bundle B is pressed in the wrapping of the tape T
therearound The wheel 10 is secured to the end 70 of a shaft 11 which
extends from the front of the machine and is journaled, as best shown
in Fig 3, in suitable bearings 12 and 13 secured respectively to
vertically extending framework plates 14 and 15 forming a part 75 of
the supporting framework for the machine.
As best shown in Figs 2 and 3, the shaft 11 and the wheel 10 secured
thereto are rotated in the direction of the arrow in Fig 2 by means of
an electric motor 16 (Fig 3) through 80 a drive including a speed
reducer 17, a pulley 18 secured to the output shaft of the speed
reducer 17, a pulley 19 secured to the shaft 11 and a belt 20
interconnecting the pulleys 18 and 19 85 As best shown in Fig 4, the
flange 10 a of the wheel 10 is secured to the end of the shaft 11 by
means of a tapered, split bushing 21 and set screws 22 The flange 10 b
has an axially projecting externally screw-threaded hub por 90 tion 23
which screws into an internally screwthreaded annular portion 23 a of
the flange l Oa This arrangement permits variation in the axial
spacing between the opposed outer peripheral surfaces of the flanges I
Oa and l Ob by rotation of flange l Ob with respect to flange la, so
that bead wire bundles B of various widths may be accommodated
therebetween The flanges 10 a and l Ob may be locked in any desired
relative rotative position by means of a pin 24 which is adapted to
extend through any of a plurality of circumferentially spaced openings
25 through the flange l Ob and an opening 26 through the flange 10 a.

An annular plate 27 having an outer peripheral axial flange 27 a is
resiliently mounted in the space between the flanges l Oa and l Ob
with the flange 27 a thereof forming a cylindrical surface against
which a bead wire bundle B positioned in the space between the outer
peripheries of the flanges l Oa and l Ob may bear as the tape T is
applied thereto.
The annular plate 27 is resiliently mounted in the space between the
flanges l Oa and l Ob by a resilient rubber ring 28, one side of which
is bonded, by the usual conventional process of bonding rubber to
metal to the plate 27 and the opposite side of which is bonded to an
annular plate 29 secured to flange l Oa by screws 29 a This resilient
mounting of the annular plate 27 permits radial displacement thereof
upon the application of a localized force to the flange 27 a thereof
by the bead wire bundle B in the application of the tape thereto so
that the bead wire bundles B of a variety of radial thicknesses can be
automatically accommodated completely within the space between the
flanges l Oa and lob, to thereby ensure proper wrapping thereof.
In the application of the tape T to the bead wire bundle B, the bead
wire bundle B, which is of a larger diameter than the wheel 10, is
placed around the wheel 10 as shown in Fig.
2 The tape T is fed onto the peripheral surface of the wheel 10 and
pressed thereagainst by a feed roller 30, as shown in Figs 2 and 4.
As the wheel 10 rotates it carries the tape T therewith and the bead
wire bundle B is pressed against a medial portion of the tape T into
the space between the flanges i O a and l Ob by a pressure roller 3 1
to wrap the tape T around three sides of the bead wire bundle B as
shown in Fig 5 The resilient mounting of the annular plate 27 permits
the complete accommodation of a segment of the bead wire bundle B in
the space between the flanges l Oa and l Ob thereby ensuring that the
bead wire bundle is completely wrapped on three sides Thereafter, as
the bead wire bundle B is rotated by the wheel 10, one edge of the
tape T is folded over the other side of the bead wire bundle by a plow
32, as shown in Fig 6, and stitched down by a stitching roller 33 as
shown in Fig 7 The other edge of the tape is then folded over by a
plow 34 as shown in Fig 8 and stitched down by a stitching roller as
shown in Fig 9.
The pressure roller 31, plow 32, stitching 70 roller 33, plow 34, and
stitching roller 35 are secured in spaced relationship to an arcuate
plate 36 (Fig 2) which in turn is secured to a slide 37 to permit
retraction thereof from the operative position as shown in Fig 2 to a
75 retracted position as shown in Fig 3 to allow loading and unloading
of the bead wire bundle from the wheel 10 The slide 37 is slidably
mounted in parallel ways 38 and 39 which are secured to framework
plate 14 and 80 is actuated by fluid actuated cylinder 40 secured to

the opposite side of the plate 14 'as shown in Fig 3 The piston rod 40
a of the cylinder 40 is secured to a plate 41 which is in turn secured
to the end of the slide 37 85 TAPE FEEDING MECHANISM The tape T for
wrapping a bead wire bundle B is supplied from a roll thereof which is
supported on a roller 42 journaled at one end in and extending from a
side framework 90 plate 14 a adjacent the base thereof as best shown
in Fig 1 The tape T is normally wrapped with a length of liner fabric
L interposed between adjacent turns of the tape to prevent sticking
together thereof A liner 95 take-up roll 43 journaled in the end of an
arm 44 pivotally suspended from a pivot pin 45 secured to the
framework plate 14 a, frictionally engages the periphery of the roll
of tape T so that as the tape is withdrawn from 100 the roll thereof,
the liner take-up roll 43 is automatically rotated to take up the
liner fabric L.
The tape T withdrawn from the roll thereof is directed around spaced
guide rollers 46, 47 105 and guide plate 49, all secured to the plate
14 a, and through a clamping and perforating mechanism 50, which as
will be described in detail hereafter, serves in severing the tape to
the proper length From the clamping and 110 perforating mechanism 50,
the tape is directed over a guide roller 51, and then around a guide
roller 52 mounted on an adjustable slide 53 mounted in ways 54 and 55
secured to the side plate 14 a and adapted to be locked 115 in
adjusted position by a lock nut 56 From the guide roller 52, the tape
is directed around a pulley 57 secured to the input shaft of a
variable speed drive 58, and around a guide roller 59, a guide plate
60, a guide roller 61, a 120 guide roller 63, a guide plate 64 (best
shown in Fig 2) and under the feed roller 30.
Adjustment of roller 52 permits varying the length of the tape between
the clamping and perforating mechanism 50 and the feed roller 125 in
accordance with the circumference of the bead wire bundles B being
wrapped The variable speed drive 58 serves as a measuring and control
device A switch actuating cam (Fig 3) is secured to the output shaft
of 130 784,769 to continue to rotate A spring press brake finger 95
engages the tape T as it passes over the guide plate 64, and prevents
the tape from retracting due to the tension therein when the feed
roller is raised and the tape severed 70 as will be hereinafter
described The finger is journaled on a pin 96 which is secured to an
extention of plate 71 While the initial feeding of the tape T is
performed by the rotation of the wheel 10 when the tape T is 75
pressed thereagainst by the feed roller 30, the tape, because of its
tackiness, is sometimes difficult to pull from the roll thereof and a_
pulley 97 (Fig 1), driven by an electric motor 98, which frictionally
engages the tape T 80 between the roll thereof and the guide roller 46
is provided to assist in pulling the tape T from the roll The electric

motor 98 is secured to the inner side of framework plate 14 a It will
be appreciated that the frictional 85 force between the pulley 97 and
the tape T and therefore the force which the pulley 97 exerts on the
tape T is dependent upon the tension in the tape T and that therefore
pulley 97 assists in pulling the tape from the 90 roll thereof only as
necessary to maintain a minimum predetermined tension G in the tape.
TAPE SEVERING MECHANISM The clamping and perforating mechanism 95 50,
best shown in Fig 1, which serves to sever the tape after the desired
length of tape has been applied to a bead wire bundle, is secured to
side plate 14 a and includes a stationary jaw 99 and a moveable
clamping 100 jaw 100 which is spring mounted by means of springs l O
Oa and l O Ob on the lower face of a moveable platen 101 which is in
turn actuated by a fluid actuated cylinder 102 The platen 101 also
carries a perforating tool 103 which 105 is adapted to move through an
opening through the floating or spring mounted jaw to perforate the
tape T across the full width thereof to thereby weaken, without
severing, the tape, at a predetermined point 110 The spring mounting
of the jaw 100 permits the clamping of the tape prior to the
perforation thereof The clamping of the tape between the jaws 99 and
100 acts as a brake on the tape to thereby tension the tape a suffi
115 cient amount to cause the tape to break or fail along a previously
perforated point thereof upon the completion of the wrapping of a bead
wire bundle The roller 52 and the variable speed drive 58 are so
adjusted that 120 the length of tape T passing through the clamping
and perforating mechanism 50 between actuations thereof is equal to
the length of tape necessary to wrap a particular bead wire bundle
Thus, the clamping of the 125 tape causes the tape to break or fail
along a previously perforated line at a point between the feed roller
30 and the pressure roller 31 whereby another bead wire bundle can be
wrapped without re-threading the tape 130 the variable speed drive 58
and serves to actuate a control switch forming a part of the control
circuit for the clamping and perforating mechanism 50 after a
predetermined length of tape has passed around the pulley 57 As best
shown in Fig 3, the pulley 57 is secured to a shaft 66 which is
journaled in bearings 67 and 68 secured to a bracket 69.
The shaft 66 is coupled to the input shaft of the variable speed drive
58 by a flexible coupling 70 By varying the speed ratio of the
variable speed drive 58, variations in the length of tape passing
around the pulley 57 between actuations of the control switch by the
cam 65 can be obtained.
Guide roller 61, guide roller 63 and guide plate 64 are secured to a
plate 71 which in turn is secured to a slide 72 (Figs I and 3).
Slide 72 is slidably mounted on a plate bracket 73 by bolts 74 which
extend -through slots in the slide 72 Adjustment of the slide 72 is

provided by means of a screw-threaded shaft 75 journaled in a plate 76
secured to bracket 73 and screwed into a block 77 secured to the slide
72 Adjustment of slide 72 by rotation of shaft 75 by means of a hand
wheel 78 secured thereto permits proper alignment of guide plate 64,
guide roller 63, and guide roller 61 with wheel 10 The guide plate 64
is provided with an adjustable fence 64 a providing for accommodation
of tapes of various widths.
The tape feed roller 30 previously referred to, which presses the tape
against the periphery of the flanges 1 Oa and l Ob of the wheel 10, is
journaled, as best shown in Fig 4, on the end of a shaft 79 Shaft 79
in turn is secured to the end of a lever arm 80 (Fig 4).
Lever arm 80 is secured to a shaft 81 which is journaled in a bearing
82 secured to framework plate 14 A lever arm 83 is secured to the
shaft 81 A screw-threaded actuator rod 84 pivotally secured to a core
85 of a solenoid 86 extends through an opening through the end of the
lever arm 83 and springs 87 and 88 encompassing the actuator rod 84
and interposed between adjustment nuts 89 and 90 (Fig 4) and the lever
arm 83 provide a resilient connection between lever arm 83 and
actuator rod 84 A tension spring 91 secured at one end to shaft 79 and
at the other end to a pin 92 secured to a bracket 93 attached to side
plate 14, serves to move the feed roller away from the wheel 10 when
the solenoid 86 is de-energized A stud 94 screwed through bracket 93
serves as an adjustable stop to limit upward movement under the action
of spring 91, of the lever 80 and the feed roller 30 carried thereby
De-energization of solenoid 86, permitting upward movement of the feed
roller 30 away from the periphery of the wheel 10, relieves the
frictional contact of the tape T with the wheel 10 so that feeding of
the tape will stop when the tape is severed, while allowing the wheel
10 784,769 BEAD WIRE EJECTING MECHANISM A hook-like element 104 is
adjustably secured to an extension 105 of the bracket 71 by means of
screws and wing nuts 106 The hook-like element 104 serves as guide for
the bead wire bundle when placed on the wheel The lower circumference
of the bead wire bundle is held in alignment with the wheel 10 by
engagement with plates 107 and 108 attached to pins 109 and 110,
respectively, adjacent the periphery of the wheel 10 Pins 109 and 110
are secured to and extend from framework plate 14.
When the slide 37 is in operative position, the pressure roller, 31
plows 32, 34 and stitching wheels 33, 35, distort a portion of the
bead wire bundle B engaged thereby to a slightly smaller radius of
curvature When the slide 37 is retracted upon completion of the
wrapping of the bead wire bundle, the bead wire bundle springs back to
its normal radius due to the inherent resiliency thereof and thereby
becomes disengaged from between the flanges 10 a and 10 b of the wheel
10 so that it is suspended only from a pin 111 which is pivotally

secured to the plate 14 The pin extends through a block 112 a bolted
to the end of an arm 112 forming a part of the ejecting mechanism The
arm 112 is pivotally mounted on a vertically extending pivot pin 113
Pivot pin 113 is secured to a bracket 114 secured to plate 14 The arm
112 is normally urged toward the plate 14 as shown in full lines in
Fig 3 by a tension spring 115 The tension spring 115 is connected at
one end to the arm 112 and at the other end to plate 14.
The arm 112 has a dog 117 (Fig 2) secured thereto The slide 37 has a
bracket 118 secured thereto and a cam block 119 is secured to the end
of the bracket 118 When the slide 37 is retracted upon completion of
the wrapping of the bead wire bundle, the dog 117 on the arm 112 is
engaged by a tapered surface 119 a on the cam block 119 and the arm
112 pivoted to the dashed line position shown in Fig 3 so that the
wrapped bead is pushed off the pin 111 and thereby ejected from the
wheel 10 into a suitable container or rack (not shown).
When the' slide 37 is again moved toward the wheel 10 to wrap another
bead wire bundle, the dog 117 is engaged by a tapered surface 119 b on
the top of cam 119 and the arm 112 lifted to the dashed line position
as shown in Fig 2 thereby permitting movement of the cam 119 past the
dog 117 without imparting any ejection movement to the arm 112 as in
the case where the slide 37 is retracted.
A compression spring 120 around the pivot pin 113, and interposed
between the arm 112 and a head 113 a of the pin 113 serves to return
the arm to the full line position of Fig 2 after the cam 119 passes
the dog 117.
CONTROL SYSTEM AND CYCLE OF OPERATION The control system, both fluid
and electrical, is diagrammatically shown in Fig 10.
The electrical circuit includes a two wire 110 volt control circuit
Li, L 2, and a three wire 440 volt power circuit, L 3, L 4 and L 5 The
70 two wire circuit Ll, L 2 derives its electrical energy from the
three wire power circuit L 3, L 4 and L 5 by means of a transformer
200.
In the diagram all switches are shown in their non-actuated position
and all solenoids 75 in a non-energized condition: On initial
operation of the machine there is no bead wire bundle in the machine,
the feed roller 30 is in its raised position with the end of the tape
under the feed roller 30, and the slide 47 80 in its retracted
position.
The motors 16 and 98 which serve to rotate the wheel 10 and the pulley
97 respectively, once started are intended to run continuously during
the wrapping of a plurality 85 of bead wire bundles The motors 16 and
98 are started by pressing push switch 201 to close the contacts
thereof The closin'g of contacts of this push switch 201 completes a
circuit to energize the solenoid of a motor 90 control relay 202 to

close contacts 202 a, 202 b, 202 c, 202 d and 202 e thereof The
closing of contacts 202 c, 202 d and 202 e completes a circuit to
start operation of motors 16 and 98.
Closing of contacts 202 a completes a holding 95 circuit around the
contacts of push switch 201 so that the solenoid of relay 202 remains
energized when switch 201 is released The continuous operation of the
motor 98 and the pulley 97 secured thereto, affects no feeding 100 of
the tape during the time between the wrapping of one bead wire bundle
and the next because there is essentially no tension on the tape
during this period.
To wrap a bead wire bundle B assuming 105 that the motors 16 and 98
are in operation and the necessary adjustments made for the particular
size bead wire bundle, the operator places a bead wire bundle B over
the pin 111.
around the wheel 10, into the hook shaped 110 guide element 104 The
wrapping of the bead wire bundle so positioned in the machine is
initiated by pressing a push switch 203 to close the contacts thereof.
Closing of the contacts of push switch 203 115completes a circuit
through previously closed contacts 202 b of control relay 202,
normally closed contacts 204 a of a relay 204, normally closed
contacts 205 a of a time delay relay 205 to energize the solenoid of a
control relay 120 206 Energization of the solenoid of relay 206 closes
normally open contacts 206 a and 206 b and opens normally closed
contacts 206 c and 206 d thereof Closing of contacts 206 a completes a
holding circuit around push 125 switch 203 and the contacts 204 a of
the relay 204 so that the solenoid of relay 206 remains energized when
push switch 203 is released and the contacts 204 a of relay 204 are
opened The closing of contacts 206 b com 130 784,769 i 1 Lamber, speed
drive 58 which forms part of the measuring device The limit switch 210
is secured to the bracket 69 adjacent the cam 65.
Actuation of limit switch 210 to close the contacts thereof completes
a circuit through 70 the normally closed contacts 206 c, and the
previously closed contacts 204 d of relay 204, to energize the
solenoid of a relay 211 to close the normally open contacts 211 a and
211 b thereof Closing of contacts 21 Ia provides a 75 holding circuit
around limit switch 210 so that the solenoid of relay 211 remains
energized upon release of the limit switch 210.
The closing of contacts 211 b completes a circuit to solenoid 209 b of
valve 209 to shift 80 the valve thereof to admit pressure to the
cylinder 102 to clamp the tape between the jaws 199 of the clamping
and perforating mechanism 50 to put sufficient load on the tape to
cause the tape to break or fail along 85 the previously perforated
point between the feed roller 30 and the pressure roller 31 upon the
completion of the wrapping of the bead wire bundle B At the same time

the tape is perforated across the width thereof by the 90 perforating
tool 103.
The closing of contacts 21 lb also completes a circuit through closed
contacts 206 d of relay 206 and the contacts 212 a of a relay 212 to
energize the solenoid 207 b of the valve 207 95 to shift the slide
thereof to admit pressure to cylinder 40 to retract the slide 37 and
the pressure roll 31, plows 32 and 34 and stitching wheels 33 and 35
from the wheel 10 As the slide 37 is retracted, the arm 112 is cammed
100 outwardly, as previously described, to eject the wrapped bead wire
bundle B from the machine In fully retracted position the slide 37
releases limit switch 208 thereby breaking the circuit to the-solenoid
of relay 204 per 105 mitting contacts 204 a thereof to close and
contacts 204 b, 204 c and 204 d to open, thereby preparing the circuit
for another cycle of operations Closing of contacts 2111 b also
completes a circuit through closed con 110 tacts 206 d to energize the
solenoid of a relay 2-121 to open the normally closed contacts 212 a
thereof after a short time delay occasioned by a dash-pot 212 b or
similar time delay device.
-Opening of contacts 212 a breaks the circuit 115 to solenoid 207 b of
valve 207 thereby preparing the valve 207 to be shifted on
energization of the solenoid 207 a of the next cycle of operation The
time delay ensures that the slide of valve 207 is completely shifted
by the 120 solenoid 207 b before the latter is deenergized.
This completes the cycle of operations of the machine and a new cycle
is initiated by again pressing the push switch 203.
From the above description, it can be seen 125 that there is provided
an improved machine for wrapping bead wire bundles or similar articles
with a length of tape The machine is substantially automatic in its
operation and requires a minimum of adjustments For 130 pletes -a
circuit to energize a solenoid 207 a to operate a solenoid actuated
valve 207 to admit pressure to the cylinder 40 to move the slide 37
and the pressure roller 31, plows 32 and 34, and stitchirig wheels 33
and 35 into operative, bead wrapping position.
As the slide 37 moves to operative position, it actuates a limit
switch 208 As best shown in Fig 2, the limit switch 208 is secured to
the framework plate 14 and is actuated by a cam block 208 a which
is-secured to the slide 37.
Actuation of limit switch 208 to close the contacts thereof completes
a circuit to energize the solenoid of the relay 204 to open normally
closed contacts 204 a thereof and close normally open contacts 204 b,
204 c and 204 d thereof Closing of contacts 204 c completes a circuit,
via 206 b to energize a solenoid 209 a of a solenoid actuated valve
200 to shift the slide thereof, to admit pressure to cylinder 102 to
raise the clamping jaw 100 and the perforating tool 103 Closing of

contacts 204 b completes a circuit through previously closed contacts
206 b of relay 206 to energize solenoid 86, which as previously
described presses the feed roller 30, toward the periphery of the
wheel 10 to thereby press the tape against the periphery of the wheel
10 and cause the tape to feed therewith At this time the wrapping of
the bead wire bundle B begins.
Closing of contacts 204 h also completes a circuit to energize a
solenoid of a relay 205.
Energization of the solenoid of relay 205 opens contacts 205 a thereof
after a short time delay occasioned by the dash-pot 205 b or similar
time delay device The opening of contacts 205 a breaks the circuit to
the solenoid of relay 206 thereby allowing previously closed contacts
206 a and 206 b to open and allowing previously opened contacts 206 c
and 206 d to close Opening of contacts 206 a breaks the holding
circuit around push switch 203 and contacts 204 a of relay 204.
Opening of contacts 206 b breaks the circuit to solenoid 207 a of
valve 207, thereby preparing, valve 207 to be shifted on subsequent'
energization of the solenoid 207 b, and also breaks the circuit to
solenoid 209 a to permit subsequent operation of the valve 209 -by
solenoid 209 b Opening of contacts 206 b also breaks the circuit to
solenoid 86 thereby allowing the feed roller 30 to rise under the
influence of the spring 91 (Fig 4) The time delay in the opening of
contacts 205 a is provided to permit the roller 30 to feed the tape
until it becomes engaged with the bead wire bundle being wrapped
Thereafter the tape continues to feed by reason of the attachment
thereof to the bead wire bundle being wrapped.
Upon completion of the wrapping of the bead wire bundle B, a limit
switch 210 s actuated by the rotating cam 65 (Fig 3) secured to the
output shaft of the variable 784,769 this reason, the machine may be
used by comparatively unskilled operators to effectively and
efficiently wrap bead wire bundles.
The novel construction of the main bead wrapping and driving wheel 10
provides for automatic accommodation of bead wire bundles of various
radial thicknesses and for bead wire bundles of non-uniform radial
thicknesses, thereby ensuring proper wrapping of such bead wire
bundles The novel feeding mechanism and the novel perforating and
clamping mechanism eliminates a number of manual operations necessary
in wrapping bead wires on machines heretofore proposed.
While a preferred form of the invention has been described it is to-be
understood that this is for the purpose of illustration only and that
variations therein may be made without departing from the scope of the
invention as claimed in the appended claims.
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* GB784770 (A)
Description: GB784770 (A) ? 1957-10-16
Improvements relating to the door-sealing of four-door saloon motor cars
DE1074420 (B) US2797958 (A)
DE1074420 (B) US2797958 (A) less
784,770 Date of Application and filing Complete Specification:
t'| @ January 10, 1956.
No 814/56.
Application made in United States of America on January 17, 1955.
Complete Specification Published: October 16, 1957.
Index zt ac 20 p)nnce:-Cszs 3), D( 2: 5), J(I: 2 D).
Intemalonzl Ca Sifknti On:-E@ 4 f.
Impjrovemenis re Rating to he doer-sealing of Four-door Saoon Motor

Cars We, GENERAL MOTORS CORPORATION, a Company incorporated under the
laws of the State of Delaware in the United States of America, of
Grand Boulevard in the City of Detroit, State of Michigan, in the
United States of America (Assignees of EDWARD G.
PODOLAN) do hereby declare the invention, for which we pray that a
patent may be granted to us, and the method by which it is to be
statement:-
This invention relates to the door-sealing of four-door saloon motor
cars.
The scope of the monopoly is indicated by the appended claims; and how
the invention can be carried into effect is hereinafter particularly
described with reference to the accompanying drawings, in which:Fig 1
is a side elevation of a four-door saloon motor car; Fig 2 is a cross
section on line 2 2 of Fig 1 showing one embodiment of doorseal; Fig 3
is a cross section on line 2 2 of Fig 1 showing another embodiment of
doorseal; and Fig 4 is a section on line 4 4 of Fig.
3.
Referring now to Fig 1 of the drawings, a vehicle body 2 includes a
front door 4 hinged at its forward edge to the body and latched at its
rearward edge to a centre pillar 6, and a rear door 8 hinged at its
forward edge to the centre pillar 6 and latched at its rearward edge
10 to the vehicle body.
The centre pillar 6 extends only from the floor of the vehicle to the
body waist-line, which is the top edge of the front and rear doors
panelling A front window 12 fixed within a window frame 24, 24 A is
supported within door 4 by a suitable window regulator for vertical
sliding movement between open and closed positions The frame of window
12 seals against the roof rail 14 in closed position and also against
the rear member 16 B of a ventilator window frame 16, 16 A, 16 B
extending upwardly at the forward portion of door 4 to the roof rail
and pivotally supporting a ventilator window 18.
The frame 16, 16 A, 16 B is rigid with the 50 door The rear window 20,
fixed within a window frame 22, 26 is supported within deor 8 by a
suitable window regulator for vertical sliding movement The frame 22
of window 20, in closed position, seals against 55 the roof rail 14
and overlaps the centre pillar 6 In the closed position of the doors
and the windows, the rear window frame member 24 of the front window
12 and the forward frame member 26 of the rear window 60 22 are close
together, and they locally form the door edges Since the centre pillar
6 does not extend above the waist line, a weather seal is provided
between window frame members 24 and 26 65 Referring now to Fig 2 of
the drawings, a first embodiment of the seal will be described The
window frame members 26 defines a channel 28 extending the length of

the window frame member, with the sides 70 of the channel being
oblique to the base of the channel An elongated sealing strip member
32 of frusto-conical cross section fits within channel 28 and extends
forwardly of the vehicle body from window frame 75 member 26 The edge
portion of sealing strip member 32 includes two rounded lips 36 and 37
defining between them a groove 34 The sealing strip member is rigid,
and may be made of a non-metallic material, 80 such as hard rubber,
vinyl resin, nylon, or poly-tetrafluor-ethylene resin, the two latter
being preferred because of their low coefficients of friction.
The window frame member 24 defines a 85 T-slot 38 extending the length
of the window frame member having an opening 40 narrower than slot 38
to define shoulders 42 A metal sealing strip member 44 having flanges
46 fits within channel 38 and is biased rear 90 784,770 wardly of the
vehicle body from window frame member 24 by a number of coil
compression springs 48 fitting within vertically spaced bores 50 in
the sealing strip member.
Flanges 46 abut against shoulders 42 in the extreme rearward position
of the sealing strip member to provide a positive stop The edge of the
sealing strip member is founded by oblique surfaces 52 and 53
terminating in a V-shaped rib having a rounded nose 54 which fits
within groove 34 in the strip 32, in the closed position of the doors
as shown in Fig 2.
The operation of the seal will now be described as either or both
doors are opened and closed.
Assuming now that the front door 4 is swung outwardly of the vehicle
body to open position, the surface 52 of sealing member 44 will
initially slide along lip 37 of sealing member 32 and cam sealing
member 44 within slot 38 of window frame member 34 against the action
of springs 48 to withdraw nose 54 from sealing engagement within crcov
34 After nose 54 slides around lip 37, springs 48 will bias sealing
member 44 to its extreme rearward position When the front door is
closed surface 53 will initially slide along lip 37 and cam sealing
member 44 within slot 38 against the action of springs 48 This allows
nose 54 to slide around lip 37 into sealing engagement within groove
34 Springs 48 continuously resist movement of sealing member 44 within
slot 38 so that oblique surfaces 52 and 53 and nose 54 are always in
wiping or sliding contact with lip 37 as the front door is initially
opened or finally closed.
When the rear door 8 is swung outwardly of the body to open position,
rounded lip 36 slides outwardly of the vehicle body along surface 53
to cam sealing member 44 within slot 38 against the action of springs
48 and withdraws nose 54 from sealing engagement within groove 34.
Springs 48 return sealing member 44 to its extreme rearward position
As the door is closed, lip 36 slides inwardly of the vehicle body

along surface 52 to cam sealing member 44 within slot 38 against the
action of springs 48 so that nose 54 can be returned into sealing
engagement within groove 34 by springs 48 If both doors are opened or
closed at the same time, then the action of the sealing members remain
substantially as described, except that the movement of sealing member
44 within slot 38 of window frame members 24 will be somewhat greater
during the initial opening and final closing movements of the doors
The use of the rounded lips 36 and 37 and the blunt nose 54 reduces
the area of sliding contact between the sealing members as the doors
are opened or closed and thus reduces friction and wear, since there
is only tangential contact between the sealing members Depending on
the location of the pivotal axis of the rear door 8 and its
inclination, if any, to the vertical, lip 37 may slide inwardly or
outwardly of the vehicle body as the rear 70 door 8 is opened The seal
strips each have a cross-sectional shape which is symmetrical about a
vertical plane passing centrally through the rib and the groove
similar to the plane 4-4 shown in Fig 3 75 Referring now to Figs 3 and
4 of the drawings, another embodiment of this invention will be
described Window frame member 26 is provided with an undercut channel
56 extending the length of the win 80 dow frame member and an
elongated sealing member S having a base portion of cross section
similar to the cross section of channel 56 is mounted within the
channel A substantially rigid web 60 extends forwardly 85 irc, N the
base portion of sealing member 58 and terminates in a rib 62 Sealing
member 58 may be mrade of the same materials as sealing member 32.
The window frame member 24 is provided 90 wth a slot 64 extending the
length of the wndow frame member and having an opening 65 of smaller
width than the slot to define a pair of opposite shoulders 66 A metal
sealing strip member 68 having flanges 95 fits within slot 64 and is
biased rearwardly by a number of vertically spaced curved leaf springs
72 having curved ends 73 bearing against the base of slot 64, as can
be seen in Fig 4 These flat springs fit 100 within a channel 74
extending the length of the sealing member, with projections 76
extending inw vardly from tle walils of the channel to retain the
springs in position Flanges engage shoulders 66 in the extreme rear
105 ward position of sealing member 68 to provide a positive stop The
terminal portion of sealing member 68 defines oblique surfaces 78 and
80 and a groove 82 of semicircular cross section having rounded lips
110 84 and 86 extending the length of the sealing member Groove 82
receives bead 62 of sealing member 58 in the closed position of the
doors as shown in Fig 3.
When the front door 4 is opened, sealing 115 member 68 is cammed
within slot 64 of window frame member 24 against the action of springs
72 as groove 82 and lip 86 slide around bead 62 to disengage the

sealing members The rounded lip 86 prevents cut 120 ting of bead 62
When door 4 is closed, oblique surface 78 of sealing member 68 slides
over bead portion 62 and cams sealing member 68 within slot 64 against
the action of springs 72 until lip 86 slides over the 125 bead and the
bead enters groove 82, with springs 72 urging the sealing members into
sealing engagement.
When the rear door 8 is opened, bead 62 cams sealing member 68 within
slot 64 130 784,770 against the action of springs 72 as it slides out
of channel 82 and over lip 84 to disengage the sealing members Springs
72 return sealing member 68 to its extreme rearward position As the
door is closed, bead 62 slides along surface 80 to cam sealing member
68 within slot 64 against the action of springs 72 and then slides
over lip 84 into groove 82, with springs 72 urging the sealing members
into sealing engagement.
When both doors are opened or closed the action of the sealing members
remains substantially the same as described, except that sealing
member 68 is moved a somewhat greater distance within slot 64 as the
doors are initially opened or finally closed Depending on the location
of the pivotal axis of the rear door 8 and its inclination, if any, to
the vertical, bead 62 may slide inwardly or outwardly of the vehicle
body as the rear door 8 is opened.
Although the seal embodiments have been illustrated and described in
conjunction with a four-door saloon having a centre pillar extending
to the waist line, it should also be noted that both embodiments of
this seal may be used with equal success on pillarless vehicles
wherein the front door is hingel at its forward edge to the vehicle
body and the rear door is hinged at its rearward edge to the vehicle
body, with the window frame members in the same relationship as herein
described The operation of the seal will be somewhat different, but
since it is symmetrical it will work equally well in either type of
vehicle.
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* GB784771 (A)

Description: GB784771 (A) ? 1957-10-16
Improvements in or connected with stands for shaving brushes
f i Date of application and filing Complete Specification: Feb 9,
1956.
No 4035156.
(Patent of Addition to No 762,039 dated May 19, 1955).
Complete Specification Published: Oct 16, 1957.
Index at acceptance:-Class 131, D 3.
International Classification:-A 45 d.
Improvements in or Connected with Stands for Shaving Brushes I, ERIC
LEOPOLD HUGO COSBY, of 24, Old Bond Street, London, W 1, a British
Subject, do hereby declare the invention, for which I pray that a
patent may be granted to me, and the method by which it is to be
statement:-
This invention relates to a stand in which a shaving brush can be
supported as set forth in the specification of Patent No 762,039.
According to this invention, a stand for a shaving brush comprises a
base for resting on a flat surface and two half-circular or Ushaped
portions at a distance apart arranged at an angle to the vertical and
supported at a suitable distance above the base, the halfcircular or
U-shaped portions being constructed of bendable material, such as wire
or other material, so that the brush can be positioned in the
half-circular or U-shaped portions with the bristles projecting
downwards at an angle at a distance above the base and whereby the
half circular or U shaped portions can be closed in or opened out to
suit the size of the brush.
The invention will be clearly understood from the following
description aided by the accompanying drawings, in which: Figure 1 is
a perspective view showing one example of carrying the invention into
eflect, and Figure 2 is a side view of same.
The stand or support is made of a length of wire or other bendable
material which is curved on itself into a half-circular or Ushaped
portion 1, the portions la of the material continuing in a straight
line at right angles to the portion 1 and bent downwards at right

angles to the portion la and curved to meat and form a second
half-circular or J-shaped portion lb.
The portions lb are bent downwards at a forwards angle and outwards to
form legs lc and then bent inwards with a curve or angle to form a
base Id, the ends of the portions hi being brought together and
secured at le by welding or otherwise, so that when the base is
resting on a flat surface the half-circular or U-shaped portions 1, lb
are at an angle to the vertical to form a cradle in which a shaving
brush 2 can be positioned 50 with the bristles 3 projecting downwards
at an angle at a distance above the base portion id.
Instead of forming the base integral with the legs lc the legs lc
could be secured in a 55 separate base.
The half-circular or U-shaped portions may be closed in or opened out
to suit the size of the brush.
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* GB784772 (A)
Description: GB784772 (A) ? 1957-10-16
Molds for bending glass
BE546511 (A) CH333843 (A) DE1032485 (B) FR1148685 (A)
BE546511 (A) CH333843 (A) DE1032485 (B) FR1148685 (A) less

7839772 t F, Date of Application and filing Complete Specification
February 24, 19-56.
No 5778/56.
Application made in United States of America on March 29, 1955.
Complete Specification Published: October 16, 1957.
hndex at -ccepae-v C^ S 6, Mr 73.
International Cassiieation:-f 6 3 h.
Holds for Bending Class We, PITTSBURGH PLATE GLASS COMPANY, a
corporation organised under the laws of the State of Pennsylvania,
United States of America, of One Gateway Center, Pittsburgh 22, State
of Pennsylvania, United States of America, do hereby declare the
invention, for which we pray that a patent may be granted to us, and
the method by which it is to be performed, to be particularly
described in and by the following statement:-
The present invention relates to improved molds for bending glass.
At present, the autcroctive industry requires that glass sheets for
windshields and backlights be bent into highly complex curvatures
wherein the radius of curvature of the glass varies considerably along
any axis.
The prior art is replete with examples of molds for curving glass
sheets Among the most successful bending molds are those of the female
skeleton type These molds comprise a number of relatively movable
molding members having upper rails.
The most efficient type of female skeleton bending mold comprises a
fixed center mold member and counterweighted outboard mold members The
latter members rotate relative to the center mold member to form a
substantially continuous outline conforming in elevation and outline
to the contour desired for the bent glass The outboard moldina members
also rotate in the opposite direction relative to the center molding
member to increase the mold length to accommodate flat glass sheets
mounted thereon for bending These outboard molding members are
preferably counterweighted so that when the open mo'd and the flat
glass are subjected to glass softening temperature, the glass
commences to sag toward the rails and the outboard molding members are
rotated to form the continuous skeleton outline mentioned above, The
facility by which the outboard molding members rotate in response to

the softening of the glass determines the effici(Price 3 s 6 d) ency
of the bending operation.
Unfortuately, prior art molds have their outboard molding members
mounted on axles which rotate on bearings that are prone to bind
during use This binding may re 50 sult from the oxidation of the
bearing surfaces of the axles and axle housings, the uneven wear
resulting from roughness in handling during use or inaccuracy of
alignment of the mold parts Such binding prevents 55 the efficient
operation of a bending mold of this type, especially when one outboard
moldir'e member rotates and the other sticks.
Various attempts have been made to synchronize the movement of the
outboard 60 molding members However, such synchronization of movement
does not insure that the outboard members rotate in synchronism with
the sagging of the glass, because the sticking of any one bearing,
including those 65 required for the linkages synchronizing the
rotation of the outboard molding members, prevents movement of the
mold from its open to its closed position Hence, it is quite possible
that the glass sheet will be 70 reversely kinked due to the delay that
occurs in closing the mold relative to the softening of the glass
Also, in extreme cases, the heat softened glass may fall off the mold
when the latter fails to rotate in response 75 to the sagging of the
glass.
An object of the present invention is to improve the efficiency of
operation of such glass bending molds by minimizing the rotational
friction of the bearings forming part 80 of the mold, while avoiding
the requirement for mechanical linkages between the outboard molding
members.
In accordance with the invention a glass bending mold is provided
comprising at 85 least two mold members pivotally mounted with respect
to each other by means of a pair of laterally spaced pivots, in which
said pivots comprise male and female bearing components carried by
said respective 90 784,772 mold members, said male and female bearing
components being adjustable relative to each other so as to adjust the
bearing contact between said mold members.
When a flat glass sheet, mounted for shaping on the improved molds of
the present invention, softens due to its exposure to heat, the
outboard molding members be-in to rotate immediately to provide a
mechanical assist to the gravitational forces tending to sag the heat
softened glass sheet to the contour formed by the upper surfaces of
the molding members as the lattter assume the closed mold position
Hence, both outboard members begin to rotate at the same instant,
bends are effected more rapidly than previously, and difficulties
inherent with prior art bending molds, due either to uniform lagging
or non-uniform rotation of the outboard members, are avoided.

The substitution of male and female bearing components for
conventional bearing rods in hinged glass bending molds as taught by
the present invention has resulted in a considerable saving of power
expenditure, because the rotatable outboard molding members, by virtue
of their facile, uniform rotation, furnish a greater proportion of the
glass bending, even when the mass of the counterweights are reduced
Outboard members of earlier molds with larger rotational friction at
the bearings than our structures, rotated in steps whenever the
moments were sufficient to overcome the standing friction of the
bearings Larger counterweights were required to minimize these steps
However, the greater the size of the counterweights, the more lehr
heat was required for the useless purpose of heating the
counterweights.
The present invention, by lessening the requirement for the minimum
rotational moment needed for the glass bending operation, provides a
more efficient utilization of the heat of the lehr.
The improved molds of the present invention are susceptible of easy
maintenance by virtue of the replaceability of the outboard molding
members, since the latter are more susceptible to damage from
mishandling than the cther mold constituents Thus our molds frequently
require replacement of an outboard member only to enable their use in
the bending line, whereas previously, the entire mold had to be
removed from the production line for a long period of repair.
The movable bearing components of each pair of bearing components
preferably are adapted for simultaneous movement along substantially
parallel axes to align the inboard extremities of an outboard molding
member to the adjacent outboard extremities of the central molding
member in the closed mold position.
In order that the invention may be fully understood it will now be
described with reference to the accompanying drawings, in which:
Figure 1 is a plan view of a typical glass bending mold in its closed
position, modified in accordance with the present inven 70 tion;
Figure 2 is an end elevational view of the mold seen in Figure 1 with
certain portions of the mold shown in open position in phantom; 75
Figure 3 is a fragmentary top plan view showing the details of a
bearing suitable for incorporation in the improved bending molds
forming part of the present invention, Figure 4 is a side elevational
view of the 80 element shown in Figure 3 taken along the lines IV IV
of Figure 3; Figure 5 is a sectional view along the lines V V of
Figure 4; Figure 6 is a view identical to Figure 85 3, showing an
alternate embodiment of the present invention; Figure 7 is a side
elevational view taken along the lines VII VII of Figure 6; Figure 8
is a sectional view along the 90 lines VIII VIII of Figure 7.
Reerring to Figures 1 through 5, a preferred embodirnent of bending

mold according to the present invention comprises a central molding
meinber 10 including a 95 number of bracing rods 11 interconnected
across a pair of spaced, arcuate rails 12 which extend longitudinally
and substantially parallel to the longitudinal center line of the mold
Adjacent each outboard extremity 100 14 of each of the spaced rails 12
are cross rods 16 Cross rods 16 support the central molding member 10
on a carriage 50 Outboard moldin Q members 18 reinforced with bracing
rods 19 combine with molding mem 105 ber 10 to constitute a glass
forming mold.
A Divot socket 20 is attached to the outer surface of the central
molding member 10.
This socket comprises a shaft 22 welded to the outside surface of the
center mold mem 110 ber 10 and a conically countersunk socket mcnber
24 fixed to the outboard extremity ef the shaft Socket member 24 has a
conical recess 25.
Outboard molding members 18 are gener 115 ally C-shape in contour and
have upper shaping surfaces 26, which in the closed position of the
mold, combine with the upper surface 28 of the central molding member
rails 12 to provide a continuous shaping sur 120 face conforming in
elevation and outline to the contour desired for a bent glass sheet.
An extension arm 30 extends inwardly longitudinally of the mold from
its point of attachment to the periphery of each out 125 board molding
member 18 These extension arms are provided with counterweights 32
which normally urge the outboard molding members to rotate to the
closed position shown in Figure 2 130 784,772 Each extension arm 30 is
provided with an internally threaded aperture 34 into which is meshed
an externally threaded screw 36.
Screw 36 is externally threaded and comprises a hexagonal head 38 at
one extremity and a conical point 40 at its other extremity.
An important aspect of the present invention resides in the fact that
the apical angle at the point 40 of the screw 36 is less than the
apical angle formed by conical recess of the countersunk socket member
24 which receives the point of the screw 36.
Bearings 41 formed by the engagement of the point 40 with the conical
recess 25 at each lateral extremity of the mold define an axis of
rotation for each outboard molding member 18 Lock nuts 42 are threaded
on the screw 36 on either side of the apertured arm 30 to fix the
location of each point 40 relative to its associated recess 25.
Metal straps 46 extend downwardly from the bottom of the side rails of
the central molding member Their bottom extremities are connected to
cross rod 16 The carriage 50 comprising longitudinal side bars 48 and
interconnecting end bars 49 supports the mold since cross rods 16 rest
upon the side bars 48 The carriage 50 is carried through a bending
lehr by means of a conveyor, the glass laden mold being carried above

the carriage during the glass bending operation.
Stop members 60 are attached to each counterweighted extension arm 30
to prevent overbending of the outboard molding members 18 These stop
members each comprise an ear 62 and an apertured flange 64 extending
perpendicularly from the ear A set screw 66 is adjustably mounted
through the aperture of the flange for engagement with outboard
extremity 14 of the central molding member 10 at its under surface.
An additional stop member 51 comprising a downwardly extending tab 52
attached to the side rail 12 is provided with an apertured flange 54
for receiving a set screw 56 When the outboard mold members 18 have
rotated into closed mold position, the set screws 56 come into
engagement with the counterweighted arms 30 to help stop the rotation
of members 18 and provide additional rigidity for the mold in the
closed mold position.
The closed mold position assumed by the outboard molding members is
stabilized by the addition of stop members 51, each pair of which is
located on the side opposite the rotational axis defined by the
bearings from the location of the pair of stop members 60 on each
extremity 14 of the center molding member Proper adjustment of screws
56 and 66 insure almost simultaneous engagement of all the stop
members with the counterweighted arms 30 and the extremities 14 of
center molding member 10, respectively, thus insuring greater
stability of the closed mold structure.
It may be preferred to back off the set screws 56 a fraction of a turn
to insure that stop members 60 are brought into engagement at the
proper moment in the rotational cycle of the outboard molding members
70 The provision of additional stop members 51 further insures the
almost perfect vertical matching of the upper shaping surface 26 of
the outboard members and the upper shaping surface 28 of the central
molding 75 member, thus enabling the closed mold to form a
substantially continuous outline matching the desired contour of a
glass sheet to be bent in both elevation and outline, even when the
main stop members 60 fail 80 to stop rotation of the outboard members
in time due to operators manipulating the screw 66 of the main stop
60.
Stop members are also provided to insure that the outboard molding
members 18 open 85 suficiently to receive flat giass, out also do not
open beyond this point For this purpose, heat abstractors 80, which
are attached to cross rods 16 by means of bent rods 82, are engaged by
bracing rods 19 of the 90 outboard molding members 18 whenever the
latter have been rotated sufficiently.
Care must be exercised also in mounting the outboard molding members
18 in correct alignment with the central molding member 95 This is
usually accomplished by mating opposing male members 36 with the

opposing female members 25 in such a manner that the inboard
extremities 70 of the outboard molding members 18 are in 100 perfect
lateral alignment with the outboard extremities 14 of the center
molding member Then, if the adjustment of the conical bearing members
is too loose or too tight, it is necessary to loosen or tighten both
male 105 members at opposite lateral extremities of a pair of conical
bearings equally to insure that the perfect lateral alignment is
maintained while the bearing rigidity and friction are adjusted 110
The apex angle of the conical point 40 of the externally threaded
screw 36 is less than that of the countersunk conical recess For
example, an apical angle of 90 for the conical point 40 is nested into
a coni 115 cal recess 25 having an apical angle of 110 ".
This difference in apex angles avoids the necessity for perfect
alignment of the male and female members 40 and 25 to form the low
friction conical bearings 41 120 A single line of contact is provided
between the conical point and the conical recess, thus enabling easy
relative rotation between the outboard molding members, fixed to the
externally threaded screw forming the 125 male member of the conical
bearings, and the central molding member 10 fixed to the conical
recess 25 forming the female member of the conical bearings Such
rotation is effected with minimum friction because 130 784,772 of the
thin line of contact between the relatively movable conical members,
even when there is substantial misalignment of the conical bearing
components 40 and 25 This line of contact becomes a point contact when
the conical bearing members are in perfect alignment.
By rotating screw 36 in one direction, the screw threaded male
component 40 is brought into rigid rotational engagement with the
female component 25 If the male and female components are in too close
engagement so that they bind, this can be remedied by backing off
opposite pairs of male components When the opposing male components
are backed completely out of engagement with their associated female
components, an outboard molding member 18 can be removed from the
central molding member 10 This virtue of having the outboard molding
members removable from the fixed center molding member facilitates
repair, maintenance, and storage problems.
Arother virtue of the above embodiment lies in the fact that most
windshield and backlight patterns required by automobile manufacturers
have substantially equally curved central portions, but vary
considerably in the shapes and curvatures toward their longitudinal
extremities Therefore, the ease by which the outboard molding members
18 can be replaced eases the storage problem, since one set of central
molding -members 10 may be used with many different outboard molding
members to produce different patterns according to different
customers' requirements.

Previously, it has been so difficult to separate the molding members
from each other that the entire mold had to be stored and replaced by
entirely different molds when production was changed from pattern to
pattern While some time is spent in replacing outboard mold members
preparatory to changeovers, the amount of storage space saved by
virtue of storing only the outboard molding members for a family of
patterns is considerable and well worth the time and effort expended
in their replacement.
The spherical bearings can also be incorporated in bending molds in
such a manner that they are adjustable along vertical rather than
horizontal axes Such a structure is shown in Figures 6 through 8,
wherein the central molding member 10 and the weighted extension arm
30 are provided with the same reference numerals as recited in the
discussion of the first embodiment above.
In this alternate embodiment, a bracket 100 having a vertical flange
102 and an apertured horizontal flange 104 is welded to each side of
the central molding member 10 at vertical flange 102 An externally
threaded bolt 106 is screw threaded through the aperture of the
horizontal flange 104 Lock nuts 108 are provided to fix the location
of the bolt 106 relative to the bracket The tip of the bolt 106 is
conically shaped and extends vertically upwardly of the bolt.
At the laterally inboard side of each ex 70 tension arm 30, a pivot
socket bracket 112 is secured by welding its vertical flange 114
thereto The pivot socket bracket also comprises an apertured
horizontal flange 116 through which a pivot socket member 118 75
extends in fixed relation At the bottom of the socket member 118 is a
conically recessed socket 120 Like the previous embodiment, the apex
angle of the recessed socket comprising the female bearing compon 80
ent is greater that that of the tip 110 of the movable bolt 106, which
comprises the male bearing component of the conical bearings formed
when the socket 120 and tips 11 ( O are brought into engagement In a
typ 85 ical mold of this type, the apical angle of the socket is 110 '
and that of the tip 50 .
When the conical bearings comprise vertically adjustable hinges as in
the latter embodiment, there is no lateral thrust main 90 taining the
outboard molding members in fixed, rotational relation to the center
molding mnember Hence, the outboard members, if mishandled or treated
negligently, are liable to fall off the contact points formed 95
between the bearing components 110 and 120.
A unitary molding structure may be formed by drilling enlarged
apertures 130 through each side rail 12 of the center molding mem 100
ber 10 and a portion of flange 102 Locking rods 132 may be inserted
through laterally opposing enlarged apertures 130 to interconnect
laterally opposing socket members 118 by attaching one of the latter

to each 105 extremity of the locking rod Thus, the pivot socket
members 118 may be adjusted vertically within the limits defined by
the difference in diameter between the locking rod 132 and the
aperture 130 110 In order to insure that the locking rods 132 are
centrally disposed through the apertures 130, each pivot socket member
118 may comprise an externally threaded shaft 134 adjustable
vertically through the aper 115 tured flange 116 of the pivot socket
bracket 112 and lock nuts 136 for fixing the vertical location of the
pivot socket member 118 so that the longitudinal extremities of the
outboard and central molding members are in 120 alignment when the
mold is in closed position Of course, the pivot point bolt 106 is
adjusted vertically so that it supports the conically recessed socket
120 of the pivot socket member 118 at the center of the point 125
formed on the outer surface of the bolt 106.
When proper alignment is made, the locking rods 132 are held centrally
of the apertures 130 and each longitudinal extremity thereof is fixed
to a pivot socket member 130 784,772 118 Thus, while laterally
opposing socket members 118 are interconnected by the locking rods,
the latter rotate with the counterweighted outboard mold members in
spaced relation to the fixed central mold member without any bearing
contact except that provided by the conical bearing components 110 and
120.
As the conical bearing components of this latter embodiment wear, an
upward vertical adjustment of the pivot point bolts 106 is all that is
required to realign the upper shaping surfaces of the outboard molding
members relative to the fixed center mold member.
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