US2924869A - Brake and braking system - Google Patents

Description

Feb. 16, 1960 N. E. KLEIN ETAL 2,924,869

BRAKE AND BRAKING SYSTEM Filed March 1, 1954 4 Sheets-Sheet l i: v I.

INVENTOR.

NORMAN E. KLEIN CHARLES D. LUCAS GEORGE A. MOBLEY ATTORNEY WM KM Feb. 16, 1960 Filed March 1 1954 N. E. KLEIN ETAL BRAKE AND BRAKING SYSTEM 4 Sheets-Sheet 2 FIG-2- PUMP IN V EN TOR.

NORMAN E. KLEIN CHARLES o. LUCAS GEORGE A MOBLEY BY WKZM M ATTORNEY N. E. KLEIN ET AL BRAKE AND BRAKING SYSTEM Feb. 16, 1960 v 4 Sheets-Sheet 3 Filed March 1, 1954 INVENTOR. NORMAN E. KLEIN BY EORGE A. uloaLEv ATTORNEY Feb. 16,1960

Filed March 1, 1954 N. E. KLE lN E L BRAKE AND BRAKING SYSTEM as 6 0 62 63 5s 59 50 4 Sheets-Sheet 4 INVENTOR.

NORMAN E.KLEIN CHARL a. was esoas .MOBLEY wlzaiw ATTORNEY fl dstates Patent 2,924,869. BRAKE AND BRAKING SYS'IEM search Corporation. near Peudleton', S.C .,a corporation qf e a ar ApplicatiouMareh 1, 1954, Serial No. 413,132

I to. 2

This: invention relates to brakes and braking systems and: more particularly to fluid braking systems suitable for usewith textile beaming or slashing apparatus and a new type of fluid activated brake suitable for use in such}. a braking system. In beaming and slashing. operations it is common practice toload a creel with a number of-section beams each of which has been previously wound with a multitude of warp threadsor ends. The endsfrom all of the section. beams are combined to form a warp. which is, at least in slashing operations, then treated with a liquid size dried and wound on a warp beam. In all such beaming operations it is necessary that the section beams be braked in order to provide the. proper tension in the warp and to,prevent t he warp from overrunning during such times as the apparatus is being brought to a stop. At present, braking action for the. section beams is customarily provided by placing a weighted rope'or band around one or both heads of each of the section beams in peripheral grooves provided for the purpose. In spite of mnnerous suggestions over a period of many years for replacing such brakes with a more precise system, rope bralges continue as the choieeof most of the industry.

The disadvantages of weighted rope brakes are'well recognized in the art. The brakes require constant attention since asthe diameter of the yarn supply on each of the section beams decreases, it is necessary to decrease the braking action to ,maintan a constant tension in the warp and this. means that an operator must be continually removing weights from the rope brakes on each of the section beams throughout the beaming operation, A second well recognized disadvantage of rope brak isthat the braking action is not decreased uni- ,fo as thefweights are removed, and one obtains a step wise reduction of braking action. A further serious disadvantage of the weighted rope brakes is that the ropes soon become frayed so that the braking action on various section beams is not uniform and, as a result, some section beams run out of yarn much soone an oth r -j A e rn remaining a t n be is, out cannot readily be employed in the preparaum Qff arp. s, e ults n ha s. n n h r d s t w te, a

In spite of the fact that the disadvantages of rope brakes for beaming apparatus have'been recognized for 'rnany years and many efforts have been made to replace the r pe brakes, none of these efforts have met with any degree ofcommercial success. A primary reason that these efforts have not been successful is that conventio al mechanical brakes in all instances possess measu able operating friction in the control system i which results: in objectional hysteresischaracteristics. In other words. the amount of braking torque obtained with the applicatiou of a given force to the'brake activating varies vWith conventional m ychanical brakes derenfiii e rm Whether. th se ted. al i app from a smaller value or from alarger value. "'-'Afurther ice reason why these efforts have been largely unsuccessful is that conventional brakes ordinarily do not have a linear response so, that the amount of braking torque resultingfrom the application of'the brake is not necessarily proportional to the amount of force applied to the brake activating means. A still further reason why these efforts have generally met with failure is that there has not been available a braking system capable of evenly compensating for the different brakingtorques required as the diameter of the section beams is decreased.

According to this invention thereis provided a brake suitable foruse on section beams wherein two disk shaped braking surfaces are engaged in frictional contact by theexpansion of a bellows due to internal fluid pressure and there is also provided a fluid braking system suitable for use. with the new brake in beaming operations. The new system evenly and adequately compensates for the change in diameter of the yarn supply on the section beams and results in the warp being maintained under a substantially constant tension at all times.

It is .a feature of the new brakes of this invention that they display substantially no hysteresis effect and the amount of braking torque exerted by the brake with a given fluid pressure in the bellows is substantially the same irrespective of whether the selected pressure is approached from a lower value or from a higher value. This advantage is made possible only by a brake design which eliminates any part, necessary for the actual activation of the brake, moving frictionally against another except,of course, the braking surfaces." In fact, substantially the only operating friction in the new brakes of this invention is that resulting from the flow of the braking fluid and as this friction is completely dynamic in nature, the brakes are responsive to practically infinitesimal changes 'in the pressure of the activating fluid.

It is a further feature of the new brakes of this invention that they exhibit a near perfect linear response or in other words the braking torque is directly proportional to the pressure in the fluid system. In fact, not only does each individual brake display an almost perfect linear response, but each of a number of brakes of the same design generally gives substantially the same braking torque with a given fluid pressure even though the brakes have been subjected to different amounts of wear. As can be seen, this more readily permits the new brakes to be employed in a system using automatic control where it is desired that the same braking torque be applied to a plurality of rotating members.

Further features of the new brakes of this invention are that the brakes possess an absolute minimum of moving parts, are simple in design and have a large braking area compared to the size of the brake. These features result -braking torque on all of the section beams is substantially the same thereby insuring that the beams will run out at substantially the same'time with the elimination of soft waste.

It is a further advantage of the new braking system when applied to beaming apparatus that the tension in the warp is maintained substantially constant at all times irrespective of the diameter of the yarn supply on the section beams thereby insuring that the warp will be wound on the warp beam at a constant tension.

Still another feature of the new braking system is that it provides means responsive to the diameter of the yarn supply and means responsive to the tension in the Patented Feb. 16,1960

v 3 I warp which are adapted to be employed in combination or individually to control the braking torque applied to the section beams.

, A preferred embodiment of the invention will now be described with reference to the accompanying drawings in which:

Figure l is a fragmentary perspective view, showing principal parts in location, of a sizing apparatus employing the new brakes and braking system.

Figure 2 is a schematic diagram illustrating the new braking system.

Figure 3 is a view in perspective of the new brake as applied to a section beam.

.Figure 4 is a sectional view of the new brake taken substantially along the line 4, 4 in Figure 5.

Figure 5 is a sectional view of the new brake looking substantially along the line 5, 5' in Figure '4.

Referring to the drawings in greater detail, there is illustrated in Figure 1 a conventional rayon slashing apparatus modified to employ the new brakes and braking system of this invention. Certain elements of the rayon slashing apparatus such as the creel and warp beam are not illustrated as they are conventional indesign and form no part of the present invention.

A pluralityof section beams each of which has been previously wound with a multitude of yarn ends, are arranged in two tiers and feed yarn ends to a comb- 11. After passing through the comb 11, yarn ends from all of the section beams 10 are combined into a warp 12 which is drawn over a roller 13 and into a size box 14' where it is coated with a suitable sizing solution. The warp 12 is subsequently passed over drying rollers 15 and is eventually collected on a warp beam, not illustrated. 7

Each of the section beams 10 has a barrel section 16 on which the warp ends are wound and a head or flange 17 at each end of the barrel portion. Extending centrally from each of the heads 17. is a journal or gudgeon 18 on which the section beams are adapted to be journaled for rotation. Mounted around the gudgeon 18 on one end of each of the section beams 10 is a fluid activatable brake, generally indicated by the reference numeral 19, to be more specifically described in subsequent paragraphs. I p

Each of the brakes 19 is operatively connected to a header 20 which, as best shown in Figure 2, is connected to a pump 21 through a conduit 22 containing a check valve 23, a filter 24 to remove any suspended matter from the fluid, a valve 25, a controllable pressure regulator 26, a constriction such as needle valve 27, anda two-way selector valve 28. An air reservoir 29 is operatively connected to conduit 22 between the check valve 23 and the filter 24 and serves thepurpose of smoothing out fiuctuations in pressure introduced bythe operation of the pump 21 and also serves, in combination with the check valve 23, as a fail safe mechanism so that in the .event preceding the connection 31 by means of a conduit 33 and a valve 34. A safety valve 35 is'connected into conduit 22 at a point intermediate the selector valve 28 and the header 20 as a precautionary measure to prevent the pressure being applied to the brakes from rising above a safe value.

A by-pass 36 containing a pressure regulator 37 is connected to conduit 2.2 eta ppipt intermediate the filter '24 and valve 25 and to the two-way selector valve 28.

A pressure indicator 38 is provided for measuring the pressure of fluid in by-pass 36 between the pressure regulator 37 and the two-way selector valve 28. A second by-pass 39 containing valve 40 is operatively connected at one end to conduit 22 at a point intermediate the filter 24 and valve 25 and at the other end to a connection 41 immediately following the valve 27.

The pressure regmlating means 26 is operated by a feeler arm 42 pivoted atone end from a suitable support 43 and having at the other end a contact for the yarn supply on beam 10 such as a small roller indicatedfby the reference numeral 44. The roller 44 is preferably made of a light weight material such as cork and is adapted to be held against the surface of the yarn supply on a selected one of the beams 10 by the tension spring in the regulator 26. As the diameter of the yarn supply on the section beam 10 decreases, a corresponding movement of the roller 44 and arm 42 allows pressure regulator 26 to close and decrease the pressure being supplied to brakes 19 by conduit 22.

After the warp 12 passes through comb 11 it is passed over a stationary rod 45 and then under a rod 46 which is resiliently mounted by virtue of leaf springs 47 only one of which is shown. The warp is then passed upwardly over roller 13 so that the rod member 46 is displaced upwardly as a result of the tension in the warp and as will be apparent to those skilled in the'art, the degree of displacement of the rod 46 will be dependent on the tension in the warp 12. The nozzle 32 is'positioned immediately below the spring member 47 so that the spring member acts as a variable closure for the nozzle.

In operation, the slashing apparatus is p'rovided'with full section beams, pump 21 is started to build up suitable operating pressure, and the selector valve 28 is positioned to open by-pass 36. Pressure regulator 37 is opened sufiiciently to give approximately the correct brakingpressure and the slasher is placed in operation, Pressure regulator 37 is then adjusted to give exactly the desired braking actionas determined visually. The reading of pressure indicator.38 is noted and with the selectoryalve 28 still in the position to open by-pass 36, and with needle valve 27 wide open and valve 34 closed, pressureregulator 26 is adjusted to give a reading on pressure 'indicator 30 slightly in excess of that on pressure indicator 38. Valve 34 is. then opened and no'zzle32 positioned with respect to the spring member '47 so that' the escape of fluid from nozzle 32 is appreciable but not excessive. As pressure regulator 26 will be trying dili- 'of fiuid from nozzle 32'.is thenagain'checked to make certain it is satisfactory in volume and'if necessary readjustment of nozzle-32 and needle valve 27 is made.

vWhen the escape of fluid from nozzle 32 is satisfactory and the reading of pressure indicator 30 is identic'al to that of pressure indicator 38, selector valve 28 is operated to close by-pass 36 and open conduit 22.

As has been previously explained, it is necessary that the braking action be decreased as the. diameter of the yarn supplyon the section beams decreases in order that the tension in the warp be maintained constant. It will be apparent from the above description that'this is accomplished by pressure regulator 26 providing a decreased pressure on; the fluid 'being supplied to brakes 19 by reason of 'the movement of arm 42 with decreasing yarn supply diameter. Pressure regulator 26 is, therefore, the primary pressure regulating means and the purpose of .the escape nozzle 32 in ordinary operation is that of a econdary pressure regulating means re ponsive to, arp

' warp -12 increase above the desired value,

6 sure indicator close .by pass 36 p I the brakes. through by-pass39, conduit 22 and header slightly, the-rod-46sis l oyveredlasa resultof the tension ing spring rrten bersz 47, thereby decrea fn'g the volume of fll idescaping'throughlthe nozzle 32 so that the'fluid pres- .sure being supplied to brakes 19 isequal to-the pressure in conduit 22;:between pressure regulator 26 and needle valve 27.; ;On;the other hand should the tension in red 46 "and spring; niembers 47 ateraised yer'tically thereby, allowing I an increasedescape of fluidlfromnoz'zle 32. Due to the constriction: in conduit -2j2 furnished by valve 27, this resuli in a reduced fluid pre ssure being applied to the fluid st vatab e b kes. lhsothat the nsion,. in th p i I 1' T. i i .l .-It is a feature of the present braking system that it be operated with either .nozzle132. or. pressure regu- .lator26.servi ng .as the sole pressure regulating. meansfand this is advantageous in rrumerous instances; I f for 'example pump 21 becomes defectiveso that it is incapable of furnishing suflicient'fluid to operate the system when escape nozzle. 32 is li;n operation, it' may be desirable to operate thebrakingnsystem solely 'byimeans of pressure regulator 26.. on thelotherhandgit the'ipressure regulator 26qshould becomedeiectiye in I acition, one mightdesire to operate.the systernfwith escape nozzle 32 as the sole pressure regulating means.

To operate the braking system with regulator 26 as .the sole regulatingrneansa correct operating pressure is de e min as exp aincda e y.- b -P ss, 6am P es- ;sure indicator 38. With valve 34 elosed and valve 27 regulator 2,6.is' then adjusted so thatpr'es- 3.0; gives a' reading identical to that of Theselector valve 28" is then operated to ope p s e close. by.-pas s .36 {and open conduit 22. i

braking system with escape nozzle 32 To operate the as the sole'pr'essure regulating means, acorrect operating pressureisdetermined by. means of. by-pass 36.as .above an ith, v lva ficl e -{and a es M nd p n nozzle 32 is positipnedtogivea' pressure reading on indicator equaljto that on indicator 38. If the escape of fluid from nozzle is excessive; valve 40 should be partially clo'sedyand' nozzle 32 again. adjusted to give a correct pressure reading on indicator 30. When the escape of fluid'fron'i nozzle 32 issatisfactory and the reading of pressure 'indicator"30'.i s identica tdthat of essure indicator 38, selectorvalve 28 is operated to so that fluid pressure is then supplied to i t t l Reference will now'be titadeto Figures 3, 4=and5 of ."the drawings"wherem the new fluid activatable brake is illustrated in greater detail. T he'reference'nurneralSt) designates a tubular sleeve adaptedto be placed over a gudgeon 18 extending centrally from the head 17 of a section beam. As gudgeons of various section beams vary slightly in diameter, an adapter sleeve 51 is provided to eliminateneedless play. Sleeve is provided with an annular flange 52 near one end and attached to the flange 52 by any suitable means such as by bolts 53 is a centrally apertured, disk shaped member 54 having a wide peripheral annular flange 55. Secured to the flange member 55 for instance by welding is a lug member 56 adapted to engage any one of a number of ribs 57, with which the heads of section beams are conventionally provided, and thereby secure the'disk member 54 and sleeve 50 for rotation with section beam 10.

J ournaled'about sleeve 50 and free to rotate with respect thereto by virtue of low frictionrbearings 58 and 59 is a cylindrical housing 60. The housing 60 is secured against lateral movement by a grease retainer ring 62 rib 57 0f the section beam head 17, the section beam is :effectively braked. As will be apparent, the magnitude of the braking torqueis dependent on the internal prestional creel standard 86.

member 54.

rotate because of its attachment to bellows 67'and housgames and locl; nuts 63: and 64 threaded onto sleeve- 50. The housing 60 is provided with a pair 0t opposed arcuate flanges65 to which an end member 66 of a toroid shaped bellows 67 is. attached-by any Suitable means suchas by' bolts 68. The opposite end'member 69 of the toroid shaped bellows 67 serves as a brake shoe to which'there is attached a section of brake lining material-70 by any suitable means such as by screws 71 having their heads recessed within the brake lining material. 'The braking surface of brake shoe member 69 is adapted to frictiona'lly engage the inner surface ofthe diskmember 54 which, of course, is machined to a high degree of smoothness to present a suitable braking surface and to eliminate unnecessary abrasion of the brake lining 70. The braking surfaces as well as the flexible part of bellows 67 are protected from external dirt and lint by means 55 whichserves as a protective cover. Mounted through the brake shoe 69 in spacedrelationship to the housing 60 is an inertia ring member 72 having anfannular flan'ge73. The inner peripheral edge of brake lining 70 is provided-with a-nannular recess 74 to'receiveth flange 73 which; is maintained-in sliding frictional contact with the brake lining 70 by means of a number of clip springs 75 The springs 75 are mounted in suitable recesses 76 in the brake lining material and aresecured to the brake drum member 69 by screws 77. The end member 66 of the bellows 67 is provided with an orifice 78 into which. a suitable-fitting 79 is threaded. The fitting 79 is' connected by a suitable conduit 80 to header 20 '(Figure 1) for the supply of a fluid under pressure.

The housing 60 1s provided with a-pair of trunnions '81 suitable for supporting the same in a trunnion box 82 quite similar to that with which creels are conventionally equipped. The trunion box 82 is pivotally secured to a slide, not illustrated, but conventional in construction,

which in turn is mounted in a housing 83 and is movable laterally in a conventional manner by rotation of the wheel 84. The housing '83 is in turn rigidly attached by any suitable means such as a bolt 85 to a conven- In operation, the bellows 67 is expanded lengthwise by internal pressure above atmospheric by means of a fluid being admitted through conduit 80 andfitting 79. Onexpansionof the bellows 67, the brake lining material 70f'rictionally engages the smooth surface of rotating disk .Sincethebrake lining 70 is not free to ing 60, a braking torque is exerted on disk member 54 and since disk member 54 is secured for rotation with the section beam 10 by means of lug 56 bearing against sure in bellows 67 which can be etfectively varied by changing the pressure on the fluid being supplied through conduit 80. w f

-The brake lining 70- is secured against rotation only. by

virtue of its attachment to the free end of bellows 67 and since bellows 67 is not completely torsionally rigid, this'introduces the likelihood of high frequency vibration of the brake shoe member 69. The inertia ring member 72 provides means for effectively damping the high frequency vibration which may possibly result because of this arrangement. While the inertia ring 72 does not prevent rotation of the brake shoe member 69, it momentarily discourages transient actions because of the inertia of the ring and the sliding frictional contact of the flange 73 with the brake lining 70 so that the brake shoe member 69 is eflectively prevented from oscillating in a rotary manner.

Having thus described out invention, what we desire to claim and protect by Letters Patent is:

We claim:

1. A fluid activated brake for applying braking torque tachment to said bellows and thetorsional rigidityof said bellows, and damping means comprisingan inertia' ring mounted in slidingfrictional contact with said brake shoe.

2. In a beaming apparatus, a brake comprising a sleeve adapted to encircle the gudgeon of a beam, a disk shaped brake member carried by said sleeve, means adapted to secure said disk member for rotation-with the beam, a

cylindrical housing journaled about said sleeve, a toroid shaped bellows circumscribing said housing, said bellows being secured at one end'to said housing, a disk shaped brakeshoe carried by the free end of said bellows for engaging said disk member on expansion of said bellows, saiddisc-shaped brake shoe being restrained from rotation only by attachment to said bellows and the torsional rigidity of said bellows, an inertia ring carried by the free vend of said bellows to damp high frequency vibration of said brake shoe, and means on said cylindrical housing for supporting the housing in a creel'and securing the same against rotation. I

3. ha beaming apparatus, a'braking system compris ,ing a sleeve adapted to incase the gudgeon of abeam,

a, disk shaped brake member carried by said sleeve, a lug member on said brake member adapted to engage a rib on a beam head whereby said brake member is secured for rotation with the beam, a cylindrical housing .journaled about said sleeve, a toroid shaped bellows positioned about said housing and secured at oneend to said housing, a centrally apertured, disk shaped brake shoe positioned in spaced relationship about said housing and carried by the free end of said bellows,- said brake shoe having a lined surface for frictionally engaging said disk shaped brake member on expansion of said bellowsfa flanged annular. inertia member positioned through said centrally ap'ertured brake shoe in spaced relationshipto lows as the diameter of the yarn supply on said beam decreases.

brake shoe being restrained against rotation only by at- 1 said housing, a recess in the brake lining to receive the flange ofysaid annular inertia member, a plurality of resilient retaining members secured to said brake shoe to retain the flange of said inertia member in sliding frictlonal contact with said brake lining, a pair of trunnions on said cylindrical housing for supporting said housing in a creel and to secure the same against rotation, and a fluid supply system to-supp'ly a fluid under pressure internally 'to said bellows. 1

4. A braking system as in claim 3 whereinsaid fluid supply system is provided with means for automatically decreasing the pressure of the fluid supplied to said bel- SJj'A fluid activated' jbr ake for applying braking torque to'a rotatable rne'mber'fsaid brakecomprising in'combination a substantiallyflabfaced'braking surface adapted for rotation aboutthe axis of rotation of said rotatable 'memberin fixed" relationship therewithfa torsionally rigid bellows'expandable lengthwise by internal pressure, said bellows being secured at one end to prevent rotation with said rotatable rrien'tber,- a secondsubstantially flat-faced braking surface operatively conrlected-to-and supported .by'said bellows and designed *tofrictio'nally engage said first surface upon'expansion of said bellows and tobe f'r'eelyldisengageable from said first surface upon contraction of said bellows; said second braking surface being restrained from rotatiodonly by the torsional rigidity of said bellows; and an inertial dampinge lement operatively connectedin energy absorbing relationto and movable relative to said second braking surface to inertially absorb energy from and thereby damp vibrationof'said second braking surface. 1 I 1 '6, YA brake arrangement accordin'gto claim 5 wherein said bellows :isjin the shape of 'a, toroidcircu'mscribing the axis of rotation of said rotatable member.

7. A fluid activated brake fonapplying'braking torque to a rotatable member; saidbrakekomprising a first disk shaped"brakin'gsurfacerotatable about the axis of rota- ,tion of said rotatable member in'fixed relationship therewith, a torsiorially rigid bellows expandable lengthwise by internal fluid pressurefsaid bellows being secured at one end to prevent'rotation' with said rotat'able member, a second disk shaped braking surface attached to the free end of said'bellows for frictionally engaging said first braking surfaceupon expansion of said bellows, said second braking surface being' restrain'ed from rotation only byjattachment tos'aid bellows,'and the torsional rigidity of said bellows, and an inertial damping element operatively'conne'ctedin' energy absorbing "relation to'and movable relative to said second disk shaped braking surface to inertially absorb-energ from and thereby'damp high frequency vibration of said second disk shaped braking v n t t v l. l a t. f I '8. Abra'ke arrangementaccording to 'claim 7 wherein Y said bellows 'is' in the shape'ofa toroid'circumscribingthe axis of rotation'ot' said 'rotatable'member.

References Cited inih fileio f-th s P n 1 i H srA'rEs PATENTS-'- 2,098,422 ]Nov. 9. 1937 v 2,2 1,891 1 i H Nov.'4, 1941 2,268,329 Ash Dec. 30, 1941 2,382,570 Aug. 14, 1945 2,518,158 u Aug. 8, 1950 2,752,658. July 3, 1956 1 2,752,659, July 3, 1956

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