US2242480A - Multicylinder pressing machine - Google Patents

Description

y .2 1941- J. F. RAYNOLDS v2,242,480

MULTI'C'YLIVNDER PRESSING MACHINE Filed Dec. 30,1937 5 Sheets-Sheet 1 JbfiA/EEA YNOL 0s flr'rneNErs i [nverzior Z Ma 20, 1941. J. F. RAYNOLDS MULTICYLINDER PRESSING momma Filed Dec. 30, 19:57 5 Sheets-Sheet s 95 FIG. 4-

P255; OPE/v v MUFFLER AuroMAT/c 77 76 4- 1R SUPPLY 55 RELEASE Ar-ronA/EYJ Patented May 20, 1941 MULTICYLINDEB PRESSING mcnmr:

John F; Raynolds, Minneapolis, Minn, assignor to The Unipreas Company, Inc.,

Minneapolis,

Minn, a corporation Minnesota Application December 30, 1937. Serial No. 182,452

Claims. (Cl. 38-41) The present invention relates'to garment or laundry presses oi. the multicylinder type and has for an object, the provision of a simple mechanical construction by which the press may be closed preliminarily under light pressure and a heavy pressure thereafter developed to.complete the pressing operation.

It is a further object to provide a mechanism which will be economical in the use of compressed air.

It is a further object of the invention to provide a mechanism which will during usage automaticaily compensate for compression of the buck ad and variation of thickness of garments being pressed.

It is a further object of the invention to provide a multicylinder machine in which one of the cylinders acts alternatively as motor cylinder and as a buffer cylinder, whereby the opening of the press is timed and cushioned.

. It is a further object of the invention to provide a system of controls whereby it is impossible for the operator of the press to become injured while operating the press.

These and other objects of the invention will become apparent in the description.

In the description hereinafter given reference is had to the accompanying drawings in which like characters represent corresponding parts in all views.

Figure 1 is a side elevation of the pressing machine showing the parts disposed when the press is in open position. H

Figure 2 is also a side elevation of the press, partly in section and with some of the elements removed, showing the mechanisms disposed as they are when the press is in partly closed, and closed positions.

Figure 3 is a fragmentary front view of the press, showin the controls.

Figure 4 is a diagrammatical view showing certain of the operating elements of the press, together with the control valves and the connecting lines as they are positioned when the press is in the open position.

Figure 5 is also a diagrammatical view showing certain elements of the press, control valves and connecting lines as they are positioned when the press is in closed position.

Figure 6 is a kinematic diagram showing the various pressing elements in a plurality of positions between the open position and the several closed positions.

The pressing machine of the present invention comprises a main frame which may, if desired,

be fabricated-from structural shapes. It comprises bed frame I upon which are mounted columns 2 and 3, and top frame 4. Mounted upon the top frame 4 adjacent column 3 is a pedestal 5 which serves to carry stationary pressing buck I which is covered with a conventional buck pad i. This pad may be of any desired construction such as a cotton-filled, cloth-covered pad, or a pad containing a large number of small springs, or other resilient elements. While the details of the pad construction form no part or the present invention it should be borne in mind that buck pads as presently used frequently consist of material which is loose and thick when fresh, but which becomes matted and takes a permanent set as it is used. This results in it gradually receding surface 8 upon which the cooperating movable pressing member 9 seats. The movable prmsin: element 9 is heated in any desired manner, such as by steam under pressure, or.electrically, and is carried by a pressing arm II which is pivoted at point H at the upper end of column 2.

The operating mechanism of the press includes two pneumatic motors l2 and i3. Motor i2 consists oi' a cylindrical shell il in which piston i5 and piston rod l6 move when air under pressure is admitted thereto. The lower end of motor i2 is pivoted to column 2 at point I! and the piston rod is connected by means of clevis l6a at its upper end to pivot point ll on presser arm ill (as shownin Figs. 1 and 2). It will be observed that in this construction piston rod it acts directly upon the movable presser arm I. to change its position from the open position shown in Figure 1 to the position shown in the full lines of Figure 2.

The second motor I3 is preferably of larger diameter than the first motor I 2 and isior the purpose of applying heavy pressure to the buck after the head 9 has been'brought into engagement with the buck through the preliminary action of motor l2. Motor It consists of a cylindrical member is which is held between cylinder heads 20 and 2| by means of through bolts 22. The cylinder head 20 is constructed so that it can be pivoted at point 38 upon bracket 23 which is in turn mounted upon channel 24 and column 3. Piston rod 25 carries piston 2| in cylinder l9 and is provided at its outer end with a bifurcated member 21 which is adiustably mounted upon the threaded portion 28 of the rod. The bifurcated member 21 is shaped so as to. straddle an upright bracket 29 which is shaped so as to form a cam trackway having arouate sections and 3|. A roller 32 is mounted upon journal pin 33 in the end of bifurcated member 21 and is of a size such that it neatly fits between the opposed surfaces of the trackway 30-3l.

Itwill be noted also that the ends of bifurcated member 21 are widened so as to slide against the side faces 34 of the trackway.

Pin 33 extends beyond the outer surfaces of bifurcated member 21 and serves to join that member with a similar bifurcated member 35.

Clevis 31 is adjustably attached to bifurcated respect to the lower horizontal member I of the The details oi the cam track construcframe. tion are illustrated in Figure 6 which shows the operating linkages in six illustrative positions a, b, c, d, e and f. The lower'portion 33 of the cam track is an arc of a circle which has as its center the pivot pin. 33 by which the base 23 of cylinder i3 is afllxed to frame 3. The upper 'portion 3| of the cam track is also an arc of a circle butin this case the center is point 0 which is below and toward the pivot point I I from a reference point (1 which represents one position of pivot l3 as the presser head 3 approaches the free position Dofthe buck 3. It will be observed that the radius 0A of the arc AC is somewhat less than the length oflink33. This fact and the chosen position of point 0 combine to givea rising characteristic to the arc AC with the result that as roller 32' is iorcedoutwardlyalong the arc AC the link will be given an upward thrust. In the diagram Figure 6 the are 130 is a portion of a circle of radius, equal to the length of link 3! (taken to the outer surface of roller 32) about position d. as a center; and as such represents the curve along which roller 32 might move freely without giving link'35 any upward component of movement. The solid angle 0: between the intersecting arcs AC and BC thus represents a curved wedge surface by which the'outward movement of extensible link 23-41 is given a small .upward component at greatly increased force so that the presser head 3, is moved home upon buck pad I. It will be noted that the two arcuate sections 30 and 3| are smoothly joined by a third are 33 which is preferably of relatively short radius.

Itis to be understood that the location of point 0 is not critical and may be varied within limits. In some instances it is desirable to decrease slightly the radius of the outermost section of the are 3, as for instance the section be tween position'e and f of roller 32.

The press is provided with a pair of springs 43 which are pivotally attached as at point 93, one at each side of and at the upper end of presser arm l0, and at their lower ends to brackets 4| on the base. The press is also provided with a pair of springs 42 which are. adjustably attached at their upper ends to boss 43 on the bifurcated member 35, and at their lower ends are attached to brackets 44 on thelbase of-the" machine.

Only the spring in the near side of the machine is visible in Figures 1 and 2. Each draw rod 43a telescopes into its spring 20 as to bring it into action ashort distance before the roller 32 reaches curved section 39 of the cam track. This retards the rapid downward motion left-hand control valve 13.

of the presser head and prevents any shock of the head against the padded buck. Springs 42 also have the added function of assisting the rapid opening of the press by freeing the air out of cylinder l3. All of the springs are adjusted so as to open the press and to maintain it in the normal position shown in Figure 1.

The controls of the press consist of a plurality of manually'operable buttons 45, 43 and 41 which are slidably mounted in openings 43 in the table panel 49 of the press. The stems 53 are pivoted to rocker arms 5| as shown in Figure 1 which serve to communicate the downward movement of an operated button to the stems 32, 33, and 54 of the control valves.

, Button actuates the release valve 55 of the press, whereas buttons 46 and", respectively. actuate the right-hand control valve 53 and I The release valve 55, and the right-hand control valve 53 are'embodied in one casing which has an air supply chamber 51 and a plurality of valve ports I3 and 53.' Valve port 53 communicates with antrum chamber 63 which in turn is connected to release cylinder Hill by connecting line 6|. Valve port 53 communicates with antrum' 62 which in turn is connected to supply section 63 of the left-hand control valve ill by way of line 64. The release valve casing is provided with a poppet-type valve having head portion 35 which serves to close port 53 when the valve is moved under the influence of spring 63. The right-hand control valve 56 is provided with a similar poppet valve. It will be noted that the junction between the small and large portions of stem 33 of the valve serve as a valve to open and close port 61, the purpose of which will be explained subsequently.

The left-hand control valve 13 is similar to the right-hand control valve and consists of a supply chamber 33, valve port 33, and antrum 33 which is connected with operating cylinder l2 by means of line ill. The casing of the left-hand valve I3 is provided with a port H which is closed when the valve port 33 is opened, and is open when the valve port 33 is closed; due tothe construction of the valve stem. This port is connected through metering orifice 12 which has an adjustment screw '13 by which the flow 01 air through the orifice can be regulated.

The press is also provided with an automatic valve 15 which is mounted upon column 2. This valve consists of a casing having four sections i3, i1, i3 and 13. Section 16 communicates with section 11 by means of valve port "which may be closed by the head 3i of valve 32. Section 'Il is at all times in communication with section 19 by means of passageway 33. Section II communicates with section 13 by means of valve port 34 which may be closed by the head 33 on valve 36. Valves 32 and 33 are provided with springs 31 and 33 which normally tend to seat the valves against their valve ports. The two valves 32 and aiarelopelfat i by rocker arm 33 which is pro vided with adjustment screws 33 and 33 which serve to operate valves 32 and 36, respectively. The-rocker arm 33 is also provided with an arm 3| which extends to the right, as shown in Figure 2, and is normally biased upwardly by spring 92. The upper end of the rocker arm 33 is curved to the left, as shown in the drawings, and is provided with a roller 33 which is positioned so as to be engaged by cam surface 34 on cam rod v I The cam rod 35 consists of a slotted lower section '96, a cam surface 94, and an upper link 9! which is pivotally attached to presser arm I at point 98. The cam rod normally hangs freely but is drawn to the right by means of the release mechanism generally designated I00. This mechanism is shown in detail in Figure and consists of a cylinder IOI in which piston I02 and piston rod I03 operate. The rod I03 carries a clevis I04 at its outer end which carries roller I05 in the slot in the lower section 96 of cam arm 95. Clevis I04 is provided with a cross-bar I06 which is normally biased to the right by means of springs I01, as shown in Figures 1 and 2. A spring I08 is provided within cylinder MI and serves to cushion piston I02 when it is moved to the left (see Figure 5).

Operation The press is normally in the position shown in Figure 1, at which time the release valve 55, the right-hand control valve 56, the left-hand control valve 10, and valve 82 of the automatic control valve I5 are in seating engagement against their respective valve ports. In order to operate the press, buttons 46 and 4'! are depressed. This serves to open the right-hand control valve 56 and the left-hand control valve 10, thereby providing' a free passage for the air from supply line IIO through line III to air supply section 51 of release valve and right-hand control valve.

.in the position shown in Figure 2, with the result that as the press closes, cam section 94 forces roller 93 to the right, as shown in Figures 2 and 5, so as to close valve port 84 and open valve port 80 of the automatic valve 15. The valves are then in the condition shown in the full lines in Figure 5 and air accordingly flows from supply line I I0 through I I2 to section 16 of the automatic valve I5 and thence through open port 80 to section TI through passage 83 to section 19. It will be noted that valve 85 covers valve port '84 and thus prevents the passage of air to section I8. Air under pressure is accordingly driven through line II3 to heavy pressure motor I3 and the piston 26 and piston rod are extended and a heavy pressure produced between the movable pressing head 9 and the pad 1 cr me buck 6.

The stopping position of the roller 32 along arcuate portion 3I of the cam trackway is determined by the air pressure in the cylinder I9,

the force exerted by springs 40 and 42, and the resisting pressure of the buck pad I. When the pad is fresh and thick, or when a heavy garment is in the press, the roller will cease movement at the position d of Figure 7. In this position the presser head is in contact with the pad at level D. As the pad 1 is compressed during use, the surface is gradually lowered from D to position E and then to the limiting position F. Thus the limiting positions of roller 32 will gradually shift from position d of Figure 7, which is the position when the pad is fresh, through to position e, and then to position I, which is the position when the pad has been fully compressed in III use. Adjustment'of the press to accommodate for the compression of the pad is thereby rendered unnecessary.

This automatic adjustment feature also compensates for variations in the thickness of garments being pressed. It should be noted that adjusting screws'on piston rod 25 and on link 36 need not ,be varied after the machine is assembled and balanced. The upward force exerted by link 35-36 increases slightly as the limiting position of roller 32 moves to the left, as shown in Figure 2, due to the fact that link 35-36 becomes nearer the right angle position with respect to presser arm I0, but. this increase is counteracted by the increased tension in springs and 42. This results in a substantially constant pressure being exerted upon the pad whetheritis new and thick, or compressed as after severe usage.

It will be noted that piston 26 is not moved in cylinder I9 during the time the press is being opened or closed under the influence of motor I2 because section 30 of the cam track is the circumference of a circle, the center of which is pivot point 38. Thus as the pressing elements close upon each other, the roller 32, bifurcated member 21, piston rod 25, and cylinder I3 simply oscillate upwardly withoutibeing extended, until the roller. reaches the circular section 39 of the trackway.

The cam track 94 is adjusted with respect to link 91 so that the automatic valve is operated as the roller 32 reaches section 39 of bracket 29, with the result that the heavy pressure cylinder I9 is completely inactive during the initial press closing operation and is then brought into activity only as the press approaches the closed position and pressure is ready to be generated between the opposed pressing elements I and 9.

As the press is moved under the influence of heavy pressure motor I3, piston I5 in cylinder I4 uncovers port II 4, thereby permitting air which is under pressure in the cylinder, to escape. In operation the operator removes pressure from buttons 46 and 41 at about the time the heavy pressure motor I3 takes over the operation of the press. The communicating passage from air supply IIO through chamber 56 of right-hand valve ;valve port 59, chamber 62, line 64, chamher 63 of left-hand valve 10, valve port 68, chamber 69 and line III to cylinder I4 is interrupted by the closure of valve ports 59 and 68. The fluid under pressure in cylinder I4'will continue to exhaust from port II4 until atmospheric pressure is established. The importance of this will be explained subsequently.

The presswill remain closed under the influence of heavypressure motor I3 until the release valve is operated by pressure upon button 45. When this occurs valve stem 52 is depressed and air is admitted from air supply chamber 51 through valve port 58 toantrum chamber 60 and thence by way of line 6I to the cylinder IOI of release mechanism I00 where it forces piston I02, piston rod I03, and roller I05 to the left from the heavy line position to the dotted line position, ,as

shown in Figure 5. The movement of roller I05.

causes cam arm to oscillate to the left and rocker arm 86 is rotated in a counterclockwise di-' rection due to the tension of spring 92. Valve 62 is thereby closed and valve 86 opened; The closure of valve 82 interrupts the air supply from line IIO to heavy pressure motor I3, and at the same time opens valve 86 and thus permits the free passage of the air which is under pressure in cylinder ll of motor l3, through line H3 to chamber I! and thence through valve port I toh chamber I8 and by way of line Ill to muflier Ill. The press immediately begins to open under the influence of springs 40 and 42, and the pistons of both cylinders are forced toward their respective cylinder heads. As the piston in mo- .tor it passes port H4 air is entrained and forced tially constant (as compared with fluids such as oil) because the air is always entrained at atmospheric pressure and because the percentage variation in the absolute temperature of the air throughout the range of operation temperatures, is very small.

In the event left-hand valve 54 has been held open, the air from.cyllnder I will not be permitted to escape at port H and will be forced through chamber 69, valve port 68, chamber 63, and thence through line 64 to antrum chamber 62. Th right-hand valve 53 is assumed to be in the unoperated position and valve port 69 will be closed and side port 61 open, thereby permitting the escape of air by means of the side port. a

The invention herein described is illustrated in its preferred embodiments but changes and modifications may be made without departing from the scope of the invention as set forth in the appended claims.

What I claim is: 1. A garment or laundry press comprising a frame, a presser arm pivoted intermediate its ends on said frame, a stationary pressing element mounted on the frame, a movable pressing element mounted on said presser arm for cooperating engagement with said stationary pressing element, a first longitudinally extensible fluid motor coupled between the frame and presser arm for actuating the latter, a second longitudinally extensible motor, pivot means for connecting one end of said second motor to the frame, an inextensible link having one of its ends pivotally connected to the presser arm and the other of; its ends pivotally connected to the second motor, and cam guide means for the pivotal connection between the inextensible link and the-second motor. I

2. In a garment or laundry press, a frame for said press; a presser-arm pivoted intermediate 'its ends on said frame; a stationary pressing element; a movabl pressing element mounted on one end of said arm for a cooperating engagement with said stationary pressing element; a first fluid motor capable of extending longitudinally when actuated, coupled between said frame and the other end of said presser arm for moving the movable pressing element into engagement with the stationary pressing element; an actuating mechanism comprising an inextensible link and an extensible link pivotally connected together, said extensible link being a second fluid motor, said actuating mechanism; being connected between said frame and said movable presser arm, and a cam guide for the pivotal connection between said links, whereby heavy pressure maybe applied by the movable'element after it has been moved into preliminary engagement with said stationary element: a manual operable valve means for applying fluid pressure to said first fluid motor to preliminarily close the press, and mechanically operated valve and means operating said valve when said press has reached a predetermined closed position, to apply fluid pressure directly to said second motor; means to exhaust all but a fixed volume of fluid from said first motor when the press is moved to its full operative position by the second fluid motor and to entrain said fluid as the press opens, and means to regulate the escape of the entrained air so as to time the opening of the press.

3. In a garment or laundry press, a frame; a presser arm pivoted intermediate its ends for oscillation with respect to said frame; a pair of cooperating pressing elements, one mounted on the frame and another on the arm; a link pivoted to said arm at a point removed from the pivot point of the arm on the frame, and a longitudinally extensible fluid motor, pivoted at one end to said frame and pivotally connected at the other end to said link; a cam surface for guiding the pivotal junction point of said link and said longitudinally extensible motor, comprising a segment of a circumference smoothly joined to a substantially arcuate wedge oriented so that motion of the junction point along said arcuate wedge moves the press toward closed position:

and motor means for moving the pivotal junction of said longitudinally extensible motor and said link along said cam surface.

4. A pressing machine comprising a frame; a presser arm pivotally mounted on said frame, a cylinder and piston therefor, a pivot for mounting the cylinder on the frame and a link directly connected between the presser arm and piston rod whereby the cylinder and piston rod will be moved about the cylinder pivot as a' center when the presser arm is moved from open press position toward closed press position, and a cam guide including an arcuate segment oriented around the cylinder pivot point as a center for restraining outward movement of the piston rod throughout a portion of said press closing movement, and a wedging segment oriented substantially radially with respect to the cylinder pivot. 5. A pressing machine comprising a frame, a presser arm pivotally mounted on said frame, a cylinder and piston therefor, a pivot for mounting the cylinder on the frame and a link directly connected between the presser arm and piston rod whereby the cylinder and piston rod will be moved about the cylinder pivot as -a center when the presser arm is moved from open press position toward closed press position, and a cam guide including an arcuate segment oriented around the cylinder pivot point as a center for restraining outward movement of the piston rod throughout a portion of said press closing movement, and a wedge segment formed to present a progressively increasing deviation towards the presser arm from a radius through the cylinder pivot.

JOHN F. RAYNOLDB.

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