US2242481A

US2242481A - Multicylinder pressing machine

Info

Publication number: US2242481A
Application number: US309016A
Authority: US
Inventors: John F Raynolds
Original assignee: Unipress Co Inc
Current assignee: Unipress Co Inc
Priority date: 1939-12-13
Filing date: 1939-12-13
Publication date: 1941-05-20
Anticipated expiration: 1958-05-20

Description

May 20, .1941.`

J. F. RAYNOLDS MULTI CYLINDER PRES S ING MACHINE Filed Dec. 13, 1959 5 Sheets-Sheet 2 v KQ@ '9 @L (46 [NVE/VTM 7o/1N EEA wvoz.- DJ

$7 Wwf, @shim ATTORNEYS May 20, 1941. J. F. RAYNoLDs MULTICYLINDER PRESSING MACHINE Filed Dec. 13, 1939 5 Sheets-Sheet .'5

' fNvENTo/e H6. 3 JOHN E ,QA YNOLDS Q3 Waal,

ATTORNEY;

May 20, 1941- J. F. RAYNoLDs MULTICYLINDER PRESSING' MACHINE Filed Dec. 13, 1939 v5 Sheets-Shea?l 4 PRES REL EA SE PILOT RIGHT HAND CTU/ITING CONTRGL l LEFT HAND AcTuAT/NG coNTRoz.)

Jj F. RAYNoLps 2,242,481

MULTICYLINDER PRESSING MACHINE Filed Dee. 13, 1939 sheets-sheet s ZIO May zo, 1941.

258. /VENTo/e lam.

Wwfwfs.

(zal

ArrozNEYr-r tion near the buck,

Patented May zo, 1941 2,242,481 mm'riorLrNnEn Panssmc MAcnmE Minneapolis, Minn., assignor to John F. Reynolds,

The Unipress Company, A apolis, Minn., a corporation of Minnesota Relssutn y FEB 24 1942 Incorporated, Minne- Application December 13, 1939, Serial No. 309,016

` s 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 heavypressure to complete the pressing operation.

It is a further object to providera 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 nal closure and Ysqueezing 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 b'een 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 posiat which time the secondary to work and to move the engagement with motor is permitted presser head into nal pressing 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.

press just as it is at4 the beginning ing operation.

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 object of the invention to provide an improved multi-motor pressing machine having a greatly reduced number of parts and having simplified, unied 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 iniured 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 of the squeezkinematic diagram showing the elements in a plurality of posiposition and. the several Figure 31s a various pressing tionsl between the open closed positions. l y

Figure 4 is a diagrammatic view showing certain of the parts in section or partly in section. The large or secondary motorv 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 l, 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 a sectional view along line 5 5 of Figure 4.

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

Figure 7 is a sectional vie-.af along vthe line 1- 1 of Figure 5 and illustrateslthe control valve lof the secondary motor in the press-closed position.`

j`|3'consists of cylindrical j held between

cylinder heads

20 and 2| by means Figure 8 is a fragmentary view of the control buttons for operating the press.

Figure9 is a. vertical view partly in section of a modified press embodying the present invention. 'I'hroughout the drawing identical parts are designated by corresponding numerals.

The present invention is capable of being carried out in a variety of pressing machines, two of which are herein illustrated. Figures 1 through 3 show a. heavy duty press capable of ironing large areas of material, whereas Figure 9 illustrates a light duty press, which is useful for various finishing operations. Figures 4 through 8 relate to detalls of the control mechanisms which are found alike in both presses.-

The heavy 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 1. This pad may be of any desired construction such as a cotton-filled, cloth-covered pad, or a pad containing a large large number of small springs or other resilient elements. While the details of the pad con.. struction 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. Thebuck 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 at the upper end of column 2. Y

The operating mechanism of the press includes primary and secondary pneumatic motors generally designated I2 and I3 respectively. Primary motor I2 consists of a cylindrical shell I4 in which piston I5 and piston rod I6 move when air under pressure is admitted thereto. The lower end of primary motor I2 is pivoted to column 2 at point I1 and the piston rod is connected by means of clevis |6a at its upper end to pivot point I8 on presser arm I0 (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 I0 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 I2 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 ls provided a large secondary motor I3. The large secondary motor, generally designated I3, 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 preliminary action of primary motor'I2. Secondary motor member I9 which is of throughl bolts.22.v The cylinder head 20 is wedge section 3|.

constructed so thatit can be pivoted'at point 33 upon bracket 23 which is in turn mountedvupon channel 24. The latter is in turn carried by front columns 3 of the press. Piston rod 25 carries piston 25 in cylinder I9 and is provided at its outer end with a bifurcated member 21 which is adjustably 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 an arcuate section 30 and a cam A roller 32 is mounted by means of an antifriction bearing 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 Ill-3|. It will be noted also that the ends of bifurcated member 21 are widened so the side faces 34 of the trackway thereby to add stability to the mechanism.

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 isadjustably attached to bifurcated member 35 by means of screw 3B 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 The upper end 31 is pivoted to arm |0 at the point I9.

The bracket 29, in which cam track 30-3I is formed, is mounted in fixed relationship with respect to the lower horizontal member I of the frame. The details of the-cam track construction are illustrated in Figures ,1, 2 and 3 which Ishow the operationlinkages in four illustrative positions a, b, c and d. The lower portion 30 of the cam track is an arc of a circle which has as its center the pivot pin 39 by which the base 20 of cylinder I9 is fixed to frame 3.

It is to be understood, of course, that the por. tion 3| need not be exactly circular, but may be of any gradually rising curve.

The surface 3| is a curved wedge having a gradually decreasing radius which results in an upturned end. The' wedge portion may be varied in different presses to accommodate the various compressibilities of buck pads, but in any design the wedge is made of rising conguration such that as roller 32 is forced outwardly on the arcuate wedge 3|, thepressing head 9 will be forced downwardly upon buck pad 1 with heavy pressure.

The two

portions

30 and 3| of the cam slot are joined together by a transition curve 39 of relatively short radius, and the length of the arcuate portion 30 and position of the transition curve 39 are made such that the large cylinderY I3 is prevented from operating until the presser head 9 has reached a safe position sufficiently close to the buck 1 that the operator of the machine is precluded from moving her hands from the controls to any pointl between the presser head 9 and the buck 1. 'I'he 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

30 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 as to slide against as an inextensible link.

`acarrear A.

of-the'arcuate wedge portion 3| of the cam slot. This latter portion 3| continues outwardly to position "d which represents the limit of press movement achieved when the buck pad is worn and matted after long use. y

of curve 39 short and small, the presser head tion b), the press will return to open position the opening springs, notpressure is applied to under the influence of withstanding air under secondary motor I3.

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 4I 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 vary the tension of each of the springs 40.

As explained above, the press from closecl 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 and cushions the opening of the press.

The pilot cylinder |25 is mounted upon the tie rod |45 of cylinder I3 while pilot cylinder |26 is likewise similarly mounted on the opposite side of cylinder I3 Aby means of tie rod. |46.

The pistons of pilot vcylinders |25 and |26 are preferably made of graphite-brass composition so as to be self lubricating. They are machined so 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 (with consequent movement of the piston in the other cylinder) will not compress thefr air in that cylinder for more than a short interval the springs serve to move of time. The slight air leakage around lthe piston of the operating cylinder is inconsequential.

Surface |10 of the valve element -is lapped smooth and operates upon a corresponding lapped surface of the valve body. Elementf-|64 lis pressed inclose engagement of the valve body by means oof a spring |13 which is compressed against the valve element |64 by means of cap |16. Cap |16 is lheld on the valve body by means of a plurality of screws |11, and a gasket |18 is preferably provided so as to make an airtight joint between the valve cap |16 and body I2I.

It will be noted there is a space between the upper surface of the shaft head |65 andkey |62 respectively and the recesses of the valve element |64 into which these portions of the shaft project. I As a. result spring I 13 is free to press the valve element |64 into close engagement into the valve body but at the same time the shaft and element are operatively connected so that as the former is rotated the latter will be likewise rotated.

In the preferred construction, the exhaust muffler is mounted directly upon the pipe |89 which is screwed into the exhaust port |24 of valve |20. l

The manual controls of the press shown in Figure 8 consist of a plurality of manually oper- At the base of the recess |65 ated

buttons

45, 46, and 41 which are slidably mounted in openings 48 in the table panel 49 of the press. Button 45 is the release button and when actuated serves to consummate the opening of the press.

Buttons

46 and 41 are identical with button 45 and are respectively the right hand and the left hand operating controls. The

buttons

46 and 41 are arranged vso that each controls an air supply valve and as explained below the valves are coupled in series so that each of the

buttons

46 and 41 must be in oper ated position in order to initiate closing of the press.

The operating connection between the

buttons

45, 46 and.41 and their

corresponding valves

55, 56 and 10 are identical and the description of button 41 and its connection to left hand control valve 10 will thus be representative of all of the controls used. As shown in Figure 1, .button 41 is of comparatively large diameter and is slidably mounted in opening 48 in the table 49. At the lower end of button 41 there is a stem 50 which Ais pivotally connected to the rocker arm 5| mounted on the underside of table 49. The rocker arm is provided with an adjustment screw 52 which abuts against the stem of the left hand control valve 10.

In Figure 4 the control operating circuits and 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 is containedin a separate casing and is operated by the left hand control button 41.

The combined release and right hand control valve casing has an antrum chamber 51, which 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 52 having a head 65, the entire valve being biased to the closed position by means of valve spring 66. The right hand control valve is similar and has a stem. 53. This valve is likewise biased to the closed position by spring 66. AThe combined release and right hand control valve casing is provided with a cover plate for antrum chamber 51 to which there is connected an air pressure supply line III which serves to maintain air under pressure at all times in the antrum chamber 51.

Adjoining valve port 58, there is a secondary chamber 60 which is connected by tube 6I to pilot cylinder |25 previously described. Adjacent the valve port 59 of the right hand valve there isa chamber 62 which is connected with tube 64 to the chamber 63 of the left hand control valve.

The left hand control valve is provided with 'a casing having valve port 68 that is normally closed by a valve 54. Like

valves

52 and 53, valve 54 is biased to the closed position by spring 66. The valve port v68 communicates with chamber 69 which is connected with tube II1 to the pilot cylinder |26 of valve |20. The tube II1 has a branch H8 which is connected directly to the primary motor I2.

It will be noted that a portion of the valve stems 53 and 54 adjoining heads of thevvalves is of reduced diameter and the junctions between the large and small portions of valve stems 53 and 54 form valves which serve to open and close small exhaust ports 61 and 1I respectively having a purpose to be described.

. port 68 Operation of heavy duty press Under normalconditions the press is in the open position shown 'in Figure 1 at which time the operating head 9 is heldin an elevated position due to the action of springs 4l. Under normal open press condition, the valve |20'is in the position shown in Figure .7; v.Air under pressure is supplied to chamber 51 of the combined release and right hand valves and is also supplied to the portion of valve A|20 above the valve blade |54 by means of tube |80.

In order to close the press, the operator operates the right hand control button 46 and the left hand control button". When this occurs, valve stems 53 and 54 are pressed inwardly against the action of their springs 66 and serve to open the passageway from the air pressure supply in antrum chamber 51 through valve port 59 to antrum chamber 62 of the right hand valve and thence through pipe 64 to the chamber 63 ofthe left hand valve. Since the left hand valve is also open at this time, air ows through valve and chamber 69 to pipe II1 and thence through pipe I I8 to the primary motor I2. At the same time, air is supplied to the pilot cylinder |26 of valve |20 which is therefore simultaneously operated with the result that valve |20 is moved to the operating position shown in Figure 7 and air is supplied to secondary motor I3 even before the press has had an opportunity to close under the inuence of primary motor I2. Air under pressure at pipe accordingly flows through port |61 in valve element |64 and through port I 53 to pipe |50 and thence to the secondary motor I3. Hence, upon actuation of the right and left hand valves, air is simultaneously supplied to both the cylinder of primary motor .I2 and to the cylinder of secondary motor I3. It is obvious that in the actio'n of supplying air to the primary and secondary cylinders I2 and I3, there is no attempt to time qr delay the ilow of air to high pressure cylinder I3, but on the contrary, the application of air is made simultaneously to both cylinders. Pilot cylinder I 26 and valve |20 are rapidly operated, and air is in fact introduced into cylinder I3 simultaneously with the introduction into cylinder I2. Action of secondary motor I2 is however prevented because the arcuate section 30 of the cam slot precludes movement of the piston 28 in secondary motor I3 until the press head has moved to a safe position close to the buck.

Hence, when the

buttons

46 and 41 are pressed, piston rod I6 of the primary motor is thrust outwardly but piston rod 25 of the secondary motor is held from moving.

The primar-y motor I 2, however, is free to actuate and accordingly moves the pressure arm I0 towards the closed press position against the opemng influence of springs 40. Due to the action of primary motor I2 and piston rod I 6 the pressing arm I 0 moves from open press position a through the safe position b, at which time the presser head 9 is very close to the buck 1, and then through position c. Throughout this motion, the roller 32' is held in tight contact with the arcuate portion 30 of the slot in bracket 29 due to the pressure being applied by secondary motor I3. As the roller 32 reaches the transition curve 39 (position b) piston 26 and piston rod 25 are operate and as they rides upwardly on 3| and accordingly pivotal connection permitted for the rst time to move outwardly the roller 32 the arcuate wedging lsurface lifts link 35 which, due to its force exerted by springs 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 3| of the cam trackway is deter, mined by the air pressure in the cylinder I9, the 40 and the resisting pressure of the buck pad 1.' When the pad is fresh and thick, or when al heavy garment is in the press, theroller will cease movement at a position such as pos'tion C in Figure 3. In this position the presser pad at level C. As the pad 1 is compressed during use, the surface is gradually lowered from C through intermediate stopping positions to the limiting position D. Thus the limiting vpositions of roller 32 will gradually shift from position C of Figure 3, which is the position when the pad is fresh, through intermediate positions, and then to position D, which is the position when the pad has been fully compressed in use and ready for replacement. Adjustment of the press to achead is in contact with the.

commodate for the compression during the life of the pad is thereby rendered unnecessary, and by proper selection of the curve 3|, 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 and on link 35--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 40 and by the rising curvature of portion 3| 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 notedthat 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 21, piston rod 25, and secondary motor I3 simply oscillates upwardly without being extended, until the roller reaches the transition curve 39 of the trackway, even though there is heavy pressurebetween 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 in the cylinder of primary motor I2 is accordingly exhausted via pipe IIS, pipe ||1, chamber 63 of valve 10, port 68 of 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 through chamber 1| 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 59, through port 68, tube 64, chamber 62 and port 61, which at this time is uncovered due to the movement of valve stem to the released position.

The press will remain closed under the iniiuence of the heavy pressure of secondary motor I3 until release valve 55 is operated by pressure upon resistance is therefore small, even` though the button 45. from chamber 51 through ber 60 and thence cylinder |25 which serves to move the valve |20 to the position shown in Figure 1. When this oc curs a passageway is completed from the cylinder I9 of secondary motor I3 through pipe |50 to port |53 and thence through arcuate section |68 in the under side of valve element |64 to port |54 and thence through passageway |5I Ato the' exhaust port |24, exhaust -pipe |89 and exhaust muiiier |90. The air within cylinder I9 accordingly rushes outwardly through the exhaust mufer. As this occurs, spring 40 quickly move the roller 32 downwardly along the arcuate wedge portion 3| of the slot 30 in bracket 29 and thence around the transition tion 30 of this open press position.

In the event the

buttons

46 and 41 are operated, (with consequent substantially instaneous operation of valve |20 which applies air to cylinder I9 of secondary motor I3) and are then released before the roller 32 has moved to the transition curve, the press will open 1. 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 valve port 58 to champressure 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 which may be of any approved type, preferably a variable resistance type. The hydraulic shock absorber |95 is provided with a lever arm |96 which is connected by means of links |91 to pivot I9 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 'I'he 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 ilnishforming a piece of relatively heavygauge 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 204 serve to carry the pivot 2 |I upon which the presser arm 2|0 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 2'06 is married upon a pedestal, 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 bedl plate 20| by welding.

'I'he Work table 249 is 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 ref- When this occurs, air is admittedy through pipe 6| to pilot release v curve 39 to the arcuate porerence to the heavy duty press, is gradually compressed during use.

Within the open back'channel 202-203, there is positionedthe primary or press closing motor generally designated 2|2, which is pivotally connected at 2|1 to the front portion 203 of the Press frame channel. ary motor 2|2 is provided With a piston and piston rod 2|6, which is pivotally connected by means of pivot pin 2|8 to the rearwardly extending portion of the presser arm 2|0. Adjacent the pivot 2|8 is the Second pivot 2| 9, 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 24| and is attached to the inextensible link235 by means of a pivot connection 242. As in the heavy duty press, the inextensible link .235 is composed of a downwardly extending bifurcated member, which is connected by means of an adjustment screw 236 to an upper bifuncatedA 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 there is pivotally mounted at 238 a secondary motor generally designated 2|3, 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. The roller 232 is preferably mounted upon anti-friction bearings such as needle roller bearings and is arranged to operate in a cam slot of bracket 229.

The cam bracket 229 is attached to the frame channel of the press by means of bolts and is provided with a cam slot composed of an arcuate section 230, which is formed about the pivot point 238 as a center, smoothly joined at curve 239 to a curved wedge portion 23|. In Figure 9 the open press position is illustrated in full lines and the closed press position by dotted lines.

The movement of the press during opening and closing is preferably controlled, as `in the heavy duty press, by means of a hydraulic shock absorber generally designated |25, which may be of any approved type, preferably of a variable resistance type. 'I'he hydraulic shock absorber |25 also in the light duty press is mounted upon one of the side plat 202, and is provided with a lever arm |96, which is positioned within the channel formed plate 203 of the pressing frame. The lever arm |96 is connected by means of a link |91 to pivot 2|9 of the presser arm 2|'0.

The operating controls of the light duty press illustrated in Figure 9 are identical with those of the heavy duty press illustrated in Figures 1, 2 and 3, the controls being the same as those shown in detail in Figures 4, 5, 6 and 7. In the light duty press of Figure 9, however, the rotary valve generally designated |20, is mounted upon the front portion 203 of the frame channel rather than directly upon the large operating cylinder as in the heavy duty press. As in the heavy duty press the rotary valve |20 of the light duty press is arranged to be operated by a pair of pilot cylinders, one of which is illustrated at |26. The pilot cylinders are mounted upon by the side plates and front vthe air supply line of the pins 245, whichv are attached to the frame channel 203 of the press. l

Above the rotary valve |20 there ls mounted an exhaust mumer anda ilexible hose connection 250 is provided between the rotary valve and the large operating cylinder 2|3.

Operation of the light duty press As in the heavy duty press, the pilot cylinders |26 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. vThe 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 through the actuated

valves

56 and 10 to light ||1 which causes the simultaneous actuation of the press actuating pilot cylinders |26 and the small press closing cylinder 2|2. Thus (as in the heavy duty press) the actuation of the right and left

hand control valves

56 and 10 causes the simultaneous introduction of air into the` cylinder of the primary motor 2|2 and into the cylinder of the secondary motor 2|3. 'I'he latter, however, is not permitted to operate due to the fact that roller 232 is in engagement with the arcuate portion 230 of the cam slot.

Asthe 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 rst time permitted to operate. Due to the pressure in motor 2|3, piston rod 228 is extended longitudinally with the result that roller 232 is forced outwardly upon the curved wedging surface 23| and as a result the pressing head 209 is forced tightly into engagement 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 |25. When this occurs, valve |20 is moved to the posi tion shown in Figure 7, and the air then under pressure in the cylinder of secondary motor 2| 3 is 'exhausted to atmosphere through muiller |90. The press accordingly opens under the inuence of spring 240.

In both the light and heavy duty presses, it is `sometimes desirable to provide a throttle valve in secondary motor. 'I'hus a throttling valve or orifice may be provided in pipe 250 or line |50 of the light and heavy duty presses respectively. 'Ihe throttling valve or orice does not inhibit the rapid building up of pressure in the secondary motor at the instant the press closure is initiated (since the volume of the cylinder space is then small), but over rapid movement 4of the secondary motor piston during iinal closure is inhibited.

'Ihis application is a continuation-impart of my application Serial Number 182,452 filed December 30, 1937.

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

What I claim is:

1. In a garment or laundry press, a frame, a presser arm pivoted intermediate its ends for oscillationv 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 of the arm on the frame, and a longitudinally extensible motor, pivot means for connecting one t tensible 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, 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 motor means to initiate closing action of the press and fluid pressure to the uid motor to effect movement of said pivotal junction point along the cam to cause nal 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 to said p whereby the cylinder and piston rod will be moved about the cylinder pivot as a I 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 cylinderv 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 rst motor and then apply nal ironing pressure by action of the second motor.

'3. A garment or frame, a presser arm 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 iirst longitudinally extensible nuid motor coupled between the frame and presser arm for actuating the latter, a second longitudinally exl arm for actuating end of said second motor to the frame, an inextensible link having one of its ends/pivotally conguide' means for causing nal 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 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, operator controlled means for controlling ilow of air to the second motor, a relay valve means having an air introducing position and an air exhaust position for controlling the iiow of air to and from the second motor, a rst relay fluid motor for moving the relay valve to the position for introducing air into the second motor,

said rst relay uid motor being connected to the operator controlled means for operation simultaneously with the first fluid motor, a second relay iluid motor and operator controlled means for supplying air thereto for moving the relay valve