* 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

Description of GB784769 (A)

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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.

COMPLETE SPECIFICATION

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

Description of GB784770 (A)

A high quality text as facsimile in your desired language may be available

amongst the following family members:

DE1074420 (B) US2797958 (A)

DE1074420 (B) US2797958 (A) less

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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

784,770 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.

COMPLETE SPECIFICATION

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

performed, to be particularly described in and by the following

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

Description of GB784771 (A)

PATENT SPECIFICATION

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.

COMPLETE SPECIFICATION

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

performed, to be particularly described in and by the following

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

Description of GB784772 (A)

A high quality text as facsimile in your desired language may be available

amongst the following family members:

BE546511 (A) CH333843 (A) DE1032485 (B) FR1148685 (A)

BE546511 (A) CH333843 (A) DE1032485 (B) FR1148685 (A) less

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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

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.

COMPLETE SPECIFICATION

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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