USRE22041E - Multicylinder pressing machine - Google Patents

Description

Feb. 24, 1942. J. F. RAYNOLDS Re. 22,041

MULTICYLINDER PRESSING MACHINE Original Filed Dec. 13, 1939 5 Sheets-Sheet l [VVE/VTOE JOHN F. EA YNOL D:

Feb. 24, 1942. J F, RAYNQLDS Re. 22,041

MULTICYLINDER PRESSING MACHINE Original Filed Dec. 13, 1939 5 Sheets-Sheet. :5

' [NVENTOE H6.-3 J-OHN E EA YNOL 0s pl! V Q? M Feb. 24, 1942. J"F RAYNQLDS I Re. 22,041

MULTICYLINDER PRESS INC MACHINE Original Filed Dec. 13, 1939 5 Sheets-Sheet 4 ACTUATING l 1-6 POSITION PRESJ ACTUATING I34 I PILOT CYL INDER LEFT HAND RIGHT HAND ACTUAT/NG L/CTUAT/NG CONTR PRESS 4951.515 E POSITION :3 P76. 7

- PRESS REL 5/155 14 CTUAT/NG CON TROL [NVENTOE JOHN F. EAYNOLDS flrrozrvsvar SMALL- CYL/NDEQ Feb. 24, 1942.

J. F. RAYNOLDS MULTICYLINDER PRESSING MACHINE Original Filed Dec. 13, 1939 5 Sheets-Sheet 5 Reissued Feb. 24, 1942 22,041 MULTICYLINDER PRESSING MACHINE John F. Raynolds, Minneapolis, Minn, assignor to The Unipress Company,

Incorporated, Minneapolis, Minn, a corporation of Minnesota Original N0. 2,242,481, dated May 20, 1941, Serial 6 Claims.

The present invention relates to garment or laundry presses of the'multi-cylinder type and has for an object, the provision of a simple mechanical construction by which such presses may rapidly be moved toward closed position and thereafter squeezed under heavy pressure 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, automatically compensate for compression of the buck pad and variation of thickness of garments being pressed.

According to previous methods of operating multi-cylinder machines, it has been customary to close the presser head into or nearly into contact with the buck by means of a primary motor and then to apply power to a secondary motor which effects final closure and squeezing of the pressing head upon the buck. In such pressing machines, the application of power to the secondary motor has been accomplished by means of apparatus controlled by the operation of the press, that is to say, the application of power to the secondary motor has been carried out at a predetermined time after the press closing is initiated or at a predetermined position of the presser head with respect to the stationary buck. Such pressing machines have been subject to various objections.

According to the present invention the application of power in such a multi-cylinder press is made simultaneously to the primary motor and to the secondary motor, but the secondary motor is mechanically prevented from operating until the pressing head reaches a predetermined position near the buck, at which time the secondary motor is permitted to work and to move the presser head into final pressing engagement with the buck.

It is, accordingly, an object of the invention to provide an improved multi-cylinder pressing machine in which power is simultaneously applied to the primary and secondary motors.

It is a further object of the invention to provide an improved .multi-cylinder pressing machine in which the secondary or squeezing motor is mechanically prevented from actuating until the press has been closed to a predetermined safe intermediate position by means of the primary motor notwithstanding the fact that power is simultaneously applied to both motors when the press closure is initiated.

December 13, 1939. Application for reissue October 10, 1941, Serial No.

It is a further object of the invention to provide an improved structural arrangement of parts which is simple and economical to manufacture and which may be assembled expeditiously.

It is a further ob'ect of the invention to provide an improved multi-motor pressing machine having a greatly reduced number of parts and having simplified, unified parts.

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.

Other objects of the invention are those inherent in the invention herein illustrated, described and claimed. These and other objects of the invention will become apparent in the description.

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

Figure 1 is a side elevational view, partly in section, of the pressing machine embodying the features and mechanisms of the present invention and showing the pressing machine in pressopen position.

Figure 2 is a side elevation partly in section illustrating the features and mechanisms of the present invention and in full lines showing the press just as it is at the beginning of the squeezing operation.

Figure 3 is a kinematic diagram showing the various pressing elements in a plurality of positions between the open position and the several closed positions.

Figure 4 is a diagrammatic view showing certain of the parts in section or partly in section. The large or secondary motor of the pressing machine, together with a pneumatically operated relay valve for controlling the same, (shown in the upper part of Figure 4) are a fragmentary view partly in section along the line 4-4 of Figure 1, while the pipe circuits, operating valves (which are shown in section) and a fragmentary section of the small or primary motor of the assembly are exposed in diagrammatic relationship.

Figure 5 is asectional view along line 5-5 of Figure 4.

Figure 6 is a sectional view along the line 6-6 of Figure 5 and illustrates the control valve of the secondary motor in the press-closed position.

Figure '7 is a sectional view along the line or Figure 5 and illustrates the control valveof the secondary motor in the press-opened position.

Figure 8 is a fragmentary View of the control buttons for operating the press.

Figure 9 is a vertical view partly in section of a modified press embodying the present inven-- THE Hmvv DUTY Press This embodiment of the present invention includes a main frame, preferably fabricated from structural shapes. The frame includes a bed frame member I upon which are mounted columns 2 and 3 and top frame member 4. Mounted upon the top frame 4 adjacent column 3 is a pedestal 5 which serves to carry stationary pressing buck 6 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 of the present invention, it should be borne in mind that a buck pad as presently used, frequently consists of material which is loose and thick when fresh, but which material gradually becomes matted and takes a permanent set as it is used. This results in a gradually receding surface 8 upon which the cooperative movable "pressing, member 9 seats. The buck 1 may be heated by steam or electricity if desired.

The movable pressing element 9 is heated in any desired manner, such as by steam under pressure, or electrically, and is carried by a pressing arm I which is pivoted at point H at the upper end of column 2.

The operating mechanism of the press includes primary and secondary pneumatic motors generally designated l2 and [3 respectively. Primary motor l2 consists of a cylindrical shell I4 in which piston I5 and piston rod l6 move when air under pressure is admitted thereto. The low-- er end of primary motor [2 is pivoted to column 2 at point l1 and the piston rod is connected by means of clevis lfia at its upper end to pivot point I8 on presser arm It) (as shown in Figures 1 and 2). It will be observed that in this construction, piston rod I6 acts directly upon the movable presser arm ID to change its position from the open position shown in Figure 1 to the nearly closed position shown in the full lines of Figure 2.

The primary motor l2 moves the press from open position to a safe intermediate position which is nearly but not quite closed. In order to complete closure of the press and to apply heavy ironing pressure, there is provided a large sec ondary motor I3. The large secondary motor,

generally designated l3, completes closure of the press and applies heavy pressure to the buck after the head 9 has been brought into close proximity to the buck through the action of primary motor I2.

preliminary Secondary motor channel 24.

I as to slide against the side faces I 3 consists of cylindrical member I9 which is held between cylinder heads 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 The latter is in turn carried by front columns 3 of the press. Piston rod 25 carries piston 26 in cylinder [9 and is provided at its outer end with a bifurcated member 21 which is the threaded portion 28 a cam trackway having an arcuate section 39 and a cam wedge section 3|. A roller 32 is mounted by means of an anti- It will be noted also that the ends of bifurcated member 21 are widened so 34 of the trackway thereby to add stability to ber with a similar bifurcated member 35. 31 is adjustably attached to bifurcated member 35 by means of screw 36 so that the three members form a solid inextensible link, which may, however, be adjusted in length. No adjustment of the link is ordinarily necessary after the machine is initially assembled, and it is therefore considered as an inextensible link. The upper end 31 is pivoted to arm ID at the point 31a.

The bracket 29, in which cam track 3| is formed, is mounted in fixed relationship with respect to the lower horizontal member I of the The details of the cam track construction are illustrated in Figures 1, 2 and 3 which show the operation linkages in four illustrative as its center the pivot pin 20 of cylinder I9 is fixed to The surface 3| is a curved wedge having a gradually decreasing rad1us which results in an upturned end. It is to be understood, of course, that the portion 3| need not be exactly circular, but may be of any gradually rising curve.

buck pad 1 with heavy pressure.

The two portions to and 3| of the cam slot are joined together by a transition curve 39 of relatively short radius, and the length of the arouate portion 38 and position of the transition curve 39 are made such that the large cylinder I3 is prevented from operating until the presser head 9 has reached a safe position sufliciently close to the buck 7 that the operator of the machine is precluded from moving her hands from the controls to any point between the presser head 9 and the buck l. The transition curve 39 preferably has a comparatively short radius and the roller 32 is likewise made of comparatively small diameter in order that the transition between curves 3% and 3| may be comparatively abrupt.

The open press position is designated a in Figure 3, while the beginning of transition curve 39 is designated b. The transition curve extends to'position c which is also the beginning of the arcuate wedge, portion 3.I of the cam slot. This latter portion 3| continuesoutwardlyto position 7 d ,which' representsjthe limit of press movement achievedwhen the buck padis worn and, matted after-longusa.

By making the radius of curve 35 short and the diameterof roller 32 small, the presser head may be maintained under the exclusive control of the primary motor-from position 11 until the press has closed to position b, at which position, head 9 is a very short or .safe distance from the buck 1. Accordingly should the operator release the controls prior to the time that roller 32 reaches transition curve 39 (position b) the press will return to open position under the influence of the opening springs, notwithstanding air under pressure is applied to secondary motor I3. 7

The press is provided with a pair of springs 40, one on each side of link 35. The springs 40 are pivotally attached to a bracket 4| mounted in the base and are pivotally attached to a through rod 42 which is mounted upon the link 35. If desired, an adjustment screw. 43 may be provided so as to varythe tension of each of the spr As explained above the springs serve to move the press from closed to open position and to return the press to open position from any intermediate position. A rubber or leather pad 44 is provided upon the top part of cam frame 29. Pad 44 provides a seat for spring attachment pivot 42 v and cushions the opening of the press.

A pilot valve generally designated I is mounted upon cylinder I3 and consists of a valve outlet port I23 and an exhaust port I24. The valve body has a transverse bore I which receives an operating shaft I3I. To the outwardly extending end I32 of operating shaft I3I, there is' attached an operating lever I33 having arms I34 and I36. The valve operating arm I34 is connected to a piston rod I35 of pilot cylinder I25 by means of a clevis I38 which may be adjusted with reference to the piston rod I35 by I36 is connected to the piston rod I31 of pilot cylinder I26 by means of a clevis I40 and is likewise adjustable by means of lock nuts MI.

The valve I20 is preferably mounted directly I50, which thus not only serves to connect the port I23 of the valve I20 to cylinder I3, but also mechanically to support the valve I20.

The pilot cylinder I25 is mounted upon the tie likewise similarly mounted on the opposite side of cylinder I3 by means of tie rod I46.

piston rod I31 will be thrust outwardly and will move the arm I36 upwardly in the direction of arrow I44 (Figure 4) and when air is admitted to the pilot cylinder I25, the arm I35 will be moved upwardly in the direction of arrow I45. The pistons of pilot cylinders I25 and I26 are as to provide a clearance of about .010 inch and there is accordingly a slight air leakage around them so that when either cylinder is operated other cylinder) will not compress the air in that cylinder for more than a short interval of time. The slight air leakage around the piston of the operating cylinder is inconsequential.

, The valve body I2'I is provided with a passagebody I2I having an air inlet port I22 and an air means of lock nuts I39. The valve operating arm upon cylinder I3 by means of a short pipe nipple v} rod I45 ofcylinder I3 while pilot cylinder I26 is When air is admitted to the pilot cylinder I25,

preferably made of graphite-brass composition so as to be selflubricating. They are machined so (with consequent movement of the piston in the way. I5Lwhich connects the exhaust, port I24 to a port 154 in the face 'of .the valve body andis provided :with another lpassageway: I 52 which terminates in the secondport I53in the face of 1 the valve body. As will be explained below, port I24 is an exhaust port and port I23 is the outlet.

The operating shaft I3I of valve I20 is provided withvan inner circular head I which seats within acircular recess, I6I inthe. right hand side of the valve body as shown in Figure 5-. Thevcircular head I60 is provided with a transverse key I62 which fits in a keyway I63 of a valve element generally designated I64. The valve element I64 has a configuration such as that shown in Figures 5, 6 and 1 and is provided with circular recess I65 into which the head I60 of the operating shaft fits. At the base of the recess I65 there is formed the keyway I63 previously mentioned. Element I64 is provided with a through passageway I61 and with a cutout portion I60 on the under side thereof.

Surface I10 of the valve element is lapped smooth and operates upon a corresponding lapped surface of the valve body. Element I64 is pressed in close engagement of the valve body by means of a spring I13 which is compressed against the valve element I64 by means of cap I16, Cap I16 is held on the valve body by means of a pluralityof screws I11, and a gasket I10 is preferably provided so as to make an airtight joint between the valve capI16 and body I2I.

' It' will be noted there is a space between the upper surface of the shaft head I65 and key I62 respectively and the recesses of the valve ele- 1 ment I64 into which these portions of the shaft that as the former is rotated the latter will be likewise rotated.

The valve I20 has sufficient internal friction that it remains in the position into which it is actuated by means of the lever arms I34 and I36, and their cooperating pilot cylinders I25 and I26.

When the valve I20 is in the position shown in Figures 5 and 6, as occurs when press actuating pilot cylinder I25 is or has been actuated,

. the valve element I64 is moved to a position such that port I61 of the valve element is in alignment with port I53 of the valve body. As a consequence, airunder pressure is admitted through supply pipe I and travels in the direction of arrow I8I through passageway I61 of the valve element I64, and passageway I53 of the valve body I2I to pipe nipple I50 and thence to the interior of the large cylinder l3.

When the valve is in the position shown in t Figure 7 as occurs when the release pilot cylinder I26 is or has been operated, the arcuate recess I60of the valve element I64 is positioned such that a communicating channel is afforded from port I53 through the arcuate under slot I68 and thence into port I54 and through passageway I5I. Passageway I5I terminates at exhaust port In the preferred construction, the exhaust muffler I is mounted directly upon the pipe I I89 which is screwed into the exhaust port I24 of valve I20.

The manual controls of the press shown in Figure 8 consist of a plurality of manually operated buttons 45, 46 and 41 which are slidably -mounted in openin s 48 in the table panel 49 of the press. Button 45 is the release button Operation of heavy duty, press and when actuated serves to consummate the Under normal condition-s the press is in the opening of the press Buttons 46 and 41 are en osition shown in Figure 1 at which time identical with button 45 and are respectively the 5 migrating head 9 is held in an elevated posi right hand and the left hand operating conth n s rm 5 40' Under trols. The buttons 46 and 41 are arranged so Ion due to 6 ac 10 of p g explained below the valves are coupled in series Sure is supplied to chamber of the combined release and right hand valves and is also supoperated posmon m order to Inmate closmg 1O plied to the portion of valve I20 above the valve of the Presselement I64 by means of tube I80.

The operating connection between the buttons In Order to close the press, the Operator 46 and 47 m correspondmg valves erates the right hand control button 45 and the 56 and 10 are identical and the description of 1 f t 1 b M n 41 en urs button 41 and its connection to left hand control e t hand con m u o Wh 1 the lower end of button 41 there is a stem 50 whlcht 1s plvotiny connected to 5 i q ig g of the left hand valve. Since the left hand valve $2 2; i g l ggggs g 3 z i is also open at this time, air flows through valve screw 52 which abuts against the stem of the left hand control valve 10. through plpe to th In Figure 4 the control operating circuits and der '25 of valve '20 the interior construction of the control valves are diagrammatically illustrated. Release button 45 operates release valve 55 which is contained in the same casing at the right hand control valve 56 (which is operated by button 46). The left hand control valve 10 is contained 32 33 3 31? is; gi s fig gi g gi ggg ggggfi a is operated by the left I80 accordingly flows through port I61 in valve The combined release and right hand control 35 element and through port to plpe Valve casing has an antrum chamber which and thence to the secondary motor I3. Hence, is provided with valve port 58 of release valve 55 and valve port 59 of the right hand control valve 56. The release valve has stem 55a having a head 65, and the entire valve is biased to the 40 secondary motor It is Obvious that in the action of supplying air to the primary and secondary cylinders I2 and I3, there is no attempt nght hand 9 01 va lve and has a to time or delay the flow of air to high pressure stem 53. This valve 1s likewise biased to the cylinder H, but on the contrary, the application closed position by spring 66. The combmed of air is made simultaneously to both cylinders.

lease and right hand control valve casing is pr Pilot cylinder I25 and valve I20 are rapidly opunder pressure at all tim in th antr m however prevented because the arcuate section ch mb 51 30 of the cam slot precludes movement of the Adjoining valve port 58, there is a secondary Piston 28 in Secondary O until the press chamber 50 which is Connected by tube 6| to head has moved to a safe position close to the pilot cylinder I26 previously described. Adjabuckcent the valve port 59 of the right hand valve when the buttons 45 and 7 are pressed,

there is a chamber 52 which is connected with piston rod I6 of the primary motor is thrust outwardly but piston rod 25 of the secondary motor gigevigvtgo the chamber 63 of the left hand con is held from moving.

The left hand control valve is provided with a tuate an a c rdi casing having valve port 68 that is normally d C 0 ngly moves Dresser arm closed by a Valve Lil!e Valves and opening influence of springs 40. Due to the acvalve 54 is biased to the closed position by spring on f primary motor m and piston rod 3 t 66 The valve port 68 communicates with champressing arm I 0 moves from open press posiber 69 which is connected with tube I I I to the tion a through the safe position b, at which time p o Cylinder I 25 of valve I20. The tube II1 the presser head 9 is very close to the buck I,

has a branch II8 which is connected directly and then through position 0. Throughout this to the primary motor I2. motion, the roller 32 is held in tight contact It will be noted that a portion of the valve with the arcuate p0 accordingly lifts link 35 which, due to its pivotal connection to the presser arm, exerts a heavy pressure between the presser head 9 and the buck 1.

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 the resisting pressure of the buck pad 1. When the pad is fresh and thick, or when a heavy garment is in the press, the roller will cease movement at a position such as position in Figure 3. In this position the presser head is in contact with the pad at level 0. As the pad 1 is compressed during use, the surface is gradually lowered from 0 through intermediate stopping positions to the limiting position (1. Thus the limiting positions of roller 32 will gradually shift from position 0 of Figure 3, which is the position when the pad is fresh, through intermediate positions, and then to position (1, which is the position when the pad has been fully compressed in use and ready for replacement. Adjustment of the press to accommodate for the compression during the life of the pad is thereby rendered unnecessary, and by proper selection of the curve 3I, the pressure of head 9 upon buck 1 is substantially the same through the range of compressions of the buck pad, and the same regardless of the thickness of the work being pressed.

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 35--36 need not be varied after the machine is assembled and balanced. The upward force exerted by link 3536 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 40 and by the rising curvature of portion 3I of the slot. This results in a substantially constant pressure being exerted upon the' pad whether it is new and thick, or compressed as after severe usage.

It will be noted that piston 26 is not moved in cylinder I9 of the secondary motor during the time the press is being opened or closed under the influence of the compressed air in 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 oscillates upwardly without being extended, until the roller reaches the transition curve 39 of the trackway, even though there is heavy pressure between roller 32 and portion 30 of the slot in bracket 29.

When operating buttons 46 and 41 are released after the press is closed, the air inthe cylinder of primary motor I2 is accordingly exhausted via pipes III! and pipe II1, chamber 69 and port 1|, which at this time is uncovered due to the movement of valve stem 54 to the release position, and thence to atmosphere. In the event the left hand button should be held down while the right hand button is released, the air from primary motor I2 is nevertheless exhausted from chamber 69, through port 68, tube 64, chamber 62 and port 61, which at thi time is uncovered due 21, piston rod 25, and secondary motor I3 simply to the movement of valve stem to the released position.

The press will remain closed under the influence of the heavy pressure of secondary motor I3 until release valve 55 is operated by pressure upon button 45. Whenthis occurs, air is admitted from chamber 51 through valve port 59 to chamber 60 and thence through pipe 6| to pilot release cylinder I26, which serves to move the valve I20 to the position shown in Figure 7. When this occurs a passageway is completed from the cylinder I9 of secondary motor I3 through pipe I50 to port I53 and thence through arcuatesection I68 in the under side of valve element I64 to port I54 and thence through passageway I5I to the exhaust port I24, exhaust pipe I89 and exhaust muffler I90. Theair within cylinder I9 accordingly rushes outwardly through the exhaust muffler. As this occurs, spring 40 quickly moves the roller 32 downwardly along the arcuate wedge portion 3I in bracket 29 and thence around the transition curve 39 to the arcuate portion 30 to the open press position.

In the event the buttons 46 and 41 are operated, (with consequent substantially instantaneous operation of valve I20 which applies air to cylinder I9 of secondary motor I3)' and are then released before the roller 32 has moved to the transition curve 39, the press will open under influence of springs 40 notwithstanding there is a heavy pressure exerted by secondary motor I3 between roller 32 and slot 30. The roller 32 is preferably journaled on needle roller bearings and the rolling resistance is therefore small, even though the pressure is heavy. Should the buttons 46 and 41 again be operated, the press will close quickly and smoothly even with the full force of roller 32 exerted upon arcuate portion 30 of the slot.

The movement of the press during opening and closing is preferably controlled by hydraulic shock absorber, generally designated I which may be of any approved type, preferably a variable resistance type- The hydraulic shock absorber I95 is provided with a lever arm I96-which is connected by means of links I91 to pivot 31a of the presser arm I0. In some instances, however, a second shock absorber may be coupled directly upon member 28.

Construction of light duty press The press illustrated in Figure 9 is relatively small as compared to the press illustrated in Figures 1, 2 and 3, and is intended for the finishing of relatively small areas of garments and for the ironing of small pieces.

The frame of the light duty press consists of a bed plate 20I, upon which there is mounted in vertical position an open back channel having a front portion 203 and side portions 202. The open back channel is preferably formed by bending a piece of relatively heavy gauge sheet metal into the desired channel shape. Near the upper portion of each of the side members 202 there is an upwardly and backwardly extending arm 204. The arms 2'04 serve to carry the pivot 2 upon which the presser arm 2I0 is mounted, and the presser arm carries a movable pressing head 209, which moves into and out of pressing engagement with buck 206. The buck 206 is carried upon a pedestal 205, which is in turn bolted to the upper portion of the channel 202-203 by means of bolts. The channel 202- 203 is preferably attached to the bed plate 20I by welding.

The work table 249 i preferably of sheet metal and is likewise carried in fixed relationship upon the pressing machine, the outer portion of the table being provided with openings for the control buttons such as those shown in Figure 8.

The buck 206 is provided with a buck pad 201 of resilient material which, as explained with reference to the heavy duty press, is gradually compressed during use.

Within the open back channel 202203, there is positioned the primary or press closing motor generally designated 2I2, which is pivotally connected at 2 I 1 to the front portion 203 of the press frame channel. Primary motor 2I2 i provided with a piston and piston rod 2I6, which is pivotally connected by means of pivot pin 2I8 to the rearwardly extending portion of the presser arm 2"). Adjacent the pivot 2I8 is the second pivot 2I9, to which an inextensible link 235 is connected after the manner described for the heavy duty press. A spring 240 is attached to the front portion 203 of the channel by means of an eye bolt 24I and is attached to the inextensible link 235 by means of a pivot connection 242. A in the heavy duty press, the inextensible link 235 is composed of a downwardly extending bifur cated member, which is connected by means of an adjustment screw 236 to an upper bifurcated member 231. The adjustment screw is locked in adjusted position by means of locking nuts thereon and ordinarily is not adjusted after the assembly of the apparatus has been completed.

Upon the bed plate 20I, there is pivotally mounted at 238 a secondary motor generally designated 2I3, which is provided with a piston and piston rod 228. The piston rod has connected thereto a bifurcated member 221, which is pivotally connected at 233 to the bifurcated member 235 of the inextensible link. The pivot 233 consists of a through pin, which carries a roller 232 between the forks of bifurcated member 235.

and is arranged to operate in a cam slot of bracket 229.

closed press position by dotted lines.

The movement of the press of a hydraulic shock absorber generally designated I25, which may be of any approved type, preferably of a variable resistance type, The hydraulic shock absorber 295 than directly upon the large operating cylinder as in the heavy duty press. As in the heavy duty press, the rotary valve I 20 of the light duty press is arranged to be operated by a pair of pilot cylinders, one of which is illustrated at I25. The pilot cylinders are mounted upon pins 245, which are attached to the frame channel 203 of the press.

Above the rotary valve I20, there is mounted an exhaust muffler I90 and a flexible hose connection 250 is provided between the rotary valve and the large operating cylinder 2I3.

Operation 09 the light duty press As in the heavy duty press, the pilot cylinders of which pilot cylinder I25 is visible in Figure 9 are arranged to be operated by a plurality of control buttons 45, 46 and 41, which are arranged to operate valves 55, 56 and 10 respectively. The actuation of the right and left- hand control buttons 46 and 41 respectively causes the actuation of valves 56 and 10 respectively, which in turn provides a flow of air from control line III through the actuated valves 56 and 10 to pipe I I1 which causes the simultaneous actuation of the press actuating pilot cylinder I25 and the small press closing cylinder 2I2. Thus. (as in the the actuation of the right and simultaneous introduction of air into the cylinder tion 230 of the cam slot.

As the press 209 is brought to a position close to the buck 201 the roller 232 reaches the transition curve 239, and at this instant, the secondary motor 2| 3 is for the first time permitted to operate. Due to the pressure in motor 2 I 3, piston ment with the buck 201.

When it is desired to open the press, the release button 45 is actuated which accordingly opens valve 55, and causes the introduction of air into the press release pilot cylinder I 26. When this occurs, valve I20 is moved to the position shown in Figure 7, and the air then under pressure in the cylinder of secondary motor H3 is exhausted to atmosphere through mufiier I90. The press accordingly opens under the influence of spring 240.

of the cylinder space is then small), but over rapid movement of the secondary motor piston during final closure is inhibited.

The patent, of which this application is an is a continuation-in-part of my application Serial Number 182,452, filed December 30, 1937, now Patent Number 2,242,480,

It is obvious that made in the details of the apparatus herein illustrated and described without, departing from the spirit of the invention which is claimed.

valves, 56 and 10 causes the What I claim is:

1. 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 arcuat-e wedge oriented so that mo tion of the junction point along said arcuate wedge moves the press toward closed position, motor means for moving the pivotal junction of said longitudinally extensible motor and said link along said cam surface, and two-hand control means for simultaneously applying power to said motor means to initiate closing action of the press and fluid pressure to the fluid motor to effect movement of said pivotal junction point along the cam to cause final closing of the press.

2. A pressing machine comprising a frame, a presser arm pivotally mounted on said frame, a first motor having a cylinder and piston for moving the presser arm toward press closed position, a second motor having a cylinder and piston, a pivot for mounting the cylinder of the second cylinder motor on the frame and a link directly connected between the presser arm and the second 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, a wedge segment formed to present a progressively increasing deviation towards the presser arm from a radius through the cylinder pivot, and two-hand operator controlled means for substantially simultaneously applying fluid pressure to the cylinders of both motors, to initiate closing of the press by action of the first motor and then apply final ironing pressure by action of the second motor.

3. 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, cam guide means for the pivotal connection between the inextensible link and the second motor, and two-hand operator controlled means for controlling flow of air to the first motor, and relay valve means operated when the two-hand operator controlled cause actuation of the second fluid motor for effecting movement of said pivotal connection along the cam guide means for causing final closing of the press.

4. 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 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, cam guide means for the pivotal connection between the inextensible link and the second motor, operator controlled means for controlling flow of air to the second motor, a relay valve means having an air introducing position and an air ex-' haust position for controlling the flow of air to and from the second motor, a first relay fluid motor for moving the relay valve to the position for introducing air into the second motor, said first relay fluid motor being connected to the operator controlled means for operation simultaneously with the first fluid motor, a second relay fluid motor and operator controlled means for supplying air thereto for moving the relay valve to the position for exhausting air from the second fluid motor.

5. The combination set in the relay valve means 0nd fluid motor.

6. The combination set forth in claim 4 wherein the relay valve means is mounted on the second fluid motor.

forth in claim 3 whereis mounted on the sec- JOHN F. RAYNOLDS.

means is moved to means for connecting one

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