BE482966A - - Google Patents

Description

       

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  Press for ironing articles of textile materials.



   This invention relates to presses and more particularly to a new practical press for ironing and the like for pressing clothes, garments, suits and fabrics. The press is more especially employed in laundries for ironing laundered articles and cleaned clothes and is also required in garment factories, where high pressure is required for ironing. edges, and seams.



   This invention is illustrated by showing a new and improved scissor type ironing press, thus

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 called out because of the upwardly circular arcuate movement of its upper ironing head articulated on a shaft placed behind and close to the pressure plane of the cooperating ironing elements or jaws of well-known shapes, generally called head and bock . Although one or more preferable examples of a movable top head and padded bottom cup type machine are shown herein, the invention can be used with other types of jaw presses.



   The general object of the invention is a press motor mechanism comprising a motor with uniformly constant power and movement transmitting means actuated by this motor by which the static inertia of the press head, when it is open, is easily defeated, and the head set in motion without rebounding or shock and moved rapidly in most of its closing movement to around its closed position, by a set of high-ratio, fast-acting levers, and in the last part of its stroke by a set of levers at low ratio, by a uniform action of the primary motor, or during the transformation of the opening and closing movements, or during the passage from the large lever ratio to the low ratio during closing, all without shock,

   rebound 'nor violence.



   More specifically, it relates to a press in which the head closes by an arched downward and forward motion, with a final closing motion over a small vertical portion of the arc of motion, practically at right angles. with the pressing plane or face of the lower pressing element or bock, the upper motor lever having successively a downward movement and a vertical pulling movement due to the constant force of the motor, in turn-

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 first around an axis near the lower end of the lever, so that the movement of the lever is transmitted to the press head by the long lever arm, then when the press closes , by rotating around an axis located at its upper end, thus putting into action the low lever arm ratio,

   which forces or pulls the control lever essentially vertically downwards, thus gripping the press head, practically linearly, in the vertical portion of its arcuate movement, to a final high pressure position, so as to always provide pressure maximum and to compensate or follow certain variations such as the differences in thickness of the workpieces, the differences in thickness or compression of the padding of the bock, and the cedage of the padding.



   It further relates to a control mechanism or a mechanism for transmitting movement between the motor and the head to maintain the fulcrum of the lever against any appreciable rocking movement during the part of the movement of the head towards the head. down and forward, and means actuated by the lever during its rocking motion about an axis near its upper end to move the lever downward, such as a pull rod simply, when the head passes through the vertical portion of its arc of motion.



   It further relates to a motor mechanism or movement transmitting mechanism between the motor and the head comprising a broken lever which performs the final closing by the set of levers at low ratio, and means for keeping the broken lever folded or turned up during the preliminary closing of the press to a point prior to the application of the final pressure, and to tension this lever during the final rocking movement of the lever by the motor, thus applying pressure by the broken lever strained while the lever acts as a pull rod.

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   It further relates to an arrangement of the control mechanism by which the head-holder lever and the control lever of the latter are housed and profiled or by which one of them is received inside. on the other when the press is open or closed, particularly their upper portions above the press table, behind the bock, and also by which the control lever and the head-carrying lever do not move not, during the opening or closing movement, behind a plane, vertical tangent to the extreme rear surface of the upper part of the lever, this fact being advantageous for the economy of space, the safety of persons near the machine in motion and the appearance of the machine.



   Other purposes will appear from the specification.



   In the invention, the variable force lever mechanically connected between a constant power motor and a press head subjected to constantly varying forces re-establishes the balance, that is to say compensates for the absence of common operating characteristics between the motor and the head and supplies from the motor to the head a constant current of energy compensating for the opposing factors such as starting the head from its stop position, the increase in resistance of the opposing springs being energized, the need to keep the driving force until the end, the requirement not to knock or hammer the padding of the bock, exceeding the rapidly increasing elastic resistance of the padding as soon as the final pressure of the jaws begins,

   by accomplishing these steps without transferring any load or strain to the bearing surface of the cams or journals, which is a favorable method used herein for controlling the movement of the lever at high pressure.

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 laughing at this invention. It has been found by tests that a motor element of a given size exerts on the part and the upholstery, with this new textile press, a compression of the jaws five times greater than that obtained with a press of known form.



   With the foregoing and other objects in view, the accompanying drawings illustrate some examples of the invention, particularly three main forms of levers, in which certain modifications of shape, size and mode of action can be made without depart from the principles and advantages explained in this description, and in which:
Figures 1 to 7 show a first form of the invention in two of its simplest constructions.



  A mechanism consisting of low-force levers first closes the movable head to an initial position, i.e. in slight contact with the padding of the bock, after which a high-power lever mechanism and strong pressure, having a higher efficiency than the normal broken lever mechanism, gives the strong compression of the jaws to the workpiece on the bock; the movement is continuous from start to finish, thus avoiding the two-stage action of known presses, especially two-roll presses.



   Figure 1 is a side elevation of the press in the wide open position, with the pedestal frame in section to show the operating mechanism, i.e. the lever system hidden therein.



   Sheet 2 comprising Figures 2, 3, 4 and 5 is a study of movement showing successive positions of the press from the beginning to the end of its closing movement performed in a continuous movement without stopping.

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   Figure 2 shows the press in the fully open position, Figure 3 in the half-closed position, and Figure 4 shows it initially closed, when the head is just against the padded bock, but without exerting pressure on the press. him. If we note that the head has slipped along its long arc, and that it has reached its initial closed position in Figure 4, we see that only part of the stroke of the piston has been used. There therefore remains a long portion of its driving stroke to move the head from its position in FIG. 4 to its position in FIG. 5.



  Figure 5 shows the press in its position under final ironing pressure, and by comparison with Figure 4 it will be seen that the padding of the lower bock is now under maximum pressure.



   The figure. 6 is a side view of the press in one of its most commercial forms, with parts omitted for clarity, and, showing a novel system of cranked counter springs for opening the press, and Figure 7 is a rear view of the latter, made more particularly in section along line 7 - 7.



  These two views are a development of the previous views, and, for simplicity, they can be considered as part of the first form of construction.



   Figure 8 is a side view of one form of construction in which the same set of low force closing levers are employed as before, but the set of high pressure, high force levers is a cam. acting on a guide for a moving fulcrum on which the system of low-effort levers is supported.



   Figure 9 is a top fragmentary view and

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 rear showing the assembly of the ironing head with its arm and a lever forming part of the compound lever system.



   Figure 10 is a plan view of the head carrier lever (also called the yoke), looking downward at Figure 9.



  Note the long single support pin passing through the antennas of the bifurcated arm as well as a set of two short twin support pins on the outside of the antenna arms, one axially aligned with the support holes in which they must enter. .



   Figures 9 and 10 should be considered with the other views of the drawings, as all of the forms of the invention shown herein employ the same system of lever assemblies with the ironer head. This assembly provides a means of taking up play between the arm and the lever; it provides safety because a careless person behind the press does not know how to insert the hand into the mechanism, and it improves the appearance of simple straight lines of the press.



   Figure 11 is a schematic of the pneumatic circuit including a compressed air motor with two hand control to illustrate the construction of the press. The elements are shown in the press open position.



  Since any suitable pneumatic control can be employed with the invention; no claim is made with respect to this particular engine and control.



   Figures 12 to 16 show the invention in a third form. Its system of compound levers, fully automatic, comprises a few more parts, and its action is characterized by a mode of operation which produces a slightly greater pressure of the jaws and a somewhat greater speed.

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 larger for an engine of given dimensions, than the other two shapes. A movable cam, guiding a movable point of support, in combination with a hydraulic speed regulator makes more efficient use of the available power of a motor of given dimensions.

   This third form, in its new combination, allows the press to work at higher speed than in the previous forms; as a result, press operators can achieve greater ironing output.



   Figure 12 shows the third form of wide press open, and Figure 13 shows it fully closed. The hydraulic speed regulator, by which it is possible to increase the speed of the ironing head, is not shown in these two views, as it is mounted on the far side.



   Figure 14 is a front view of the third form of the invention. The press is closed, and the face of the frame removed to show the parts of the lever system.



  Note the hydraulic speed controller on the right side of the press: it is slightly enlarged for clarity.



  The governor is directly connected by a coupling with a shaft of the lever system and is driven by the latter, and a rod of the broken lever is attached to this shaft. This hydraulic governor includes a double-acting two-cylinder shock absorber and speed controller. By its use, in a new method, it is now possible to close the press head at high speed because the governor maintains the lever system at its pre-adjusted speed and prevents the driving organs from exceeding this speed.



  Likewise, the opening of the press can be done at high speed, in fact at the maximum speed obtainable, and the shock absorber brakes the inertia at the end of the opening stroke.

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 without delaying the rapid opening of the press.



   Figure 15 is a separate view of the hydraulic regulator, looking at the end of the regulator shaft which connects it directly to the press lever system, with parts of the regulator shown in the press open position. .



   Figure 16 is a plan view of the cruise control taken along line 16-16 of Figures 14 and 15, with the cover removed, therefore looking down into the device.



   Reference is now made to the drawings for a more detailed description of the illustrated examples of the invention, but: the description will moreover be given of a press in general, that is to say of the type of press chosen for illustration of the lever system and other features of the invention in its various forms.



   The frame is preferably fabricated from sheet steel shaped and welded together to form a rigid pedestal enclosing the mechanical parts. The frame can therefore consist of two spaced side plates 2 with a front plate 3, thus leaving the frame open at the rear as shown. Vertical frame sheets 2-3 can preferably rise from a base with stamped edges
4. The rear upper part of the frame is provided with a pair of spaced parallel horns or consoles 5 to receive the mechanical parts of the movable press head.



   The frame 2, 3 is surmounted by a plate 6 which can also form a table or a table support to suitably support the pieces during ironing or pressing. Usually, a thin metal table (not shown) is placed above the frame cover 6, and this table can be as long or longer than the press jaws, and therefore overhang the faces.

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 frame 2. The frame cover 6, or more particularly the table when placed therein, can also extend forward beyond the faceplate 3 and be folded down so as to form a frontal margina- le collar '7.

   Especially since the table, to finish and cover the frame cover 6, is preferably made of thin sheet metal, the front edge 7 provides rigidity as well as suitable protection for the control valves and their front levers. the press. The frame cover (with its top table not shown) can extend rearward under the press jaws and curve upward in 8 to form a back plate against which the edges of the garments or parts can. rest and be protected during operation.



   A frame support or console 9 is rigidly fixed under the frame cover 6 and hangs from the latter towards the rear central part of the frame 2-3. It is used as a fixed pivot frame to mount the new form of high power, high pressure broken lever having variable stroke or oscillation, as described below. Likewise, on the face of the press, a lug or support bracket 10 for mounting an adjustable pivot frame for the new system of levers is shown. A little lower in the frame, a similar console frame 11 forms a support for the engine.



   12 is
A vertical post or pedestal / placed at the top of the frame plate 6 to support the lower presser jaw or padded bock. This upright 12 sometimes takes the shape of a horizontal U when it is seen from the front of the press (see figure 14) which explains why it is known in the trade under the name of "swan neck", and this is more

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 especially true when the bock is long, because it allows the operator to place the part more easily. An ordinary steam-heated bock 15 is supported on the upper end of the gooseneck 12; bock is covered with a single layer of padding 16.

   The padding 16 usually consists of a tight packing of short coil springs interposed vertically under layers of felt padding to provide a substantial and thick resilient bed upon which the piece can be placed and arranged.



   The movable ironer head 17 has a long up and down movement to achieve a wide opening of the press for the convenience of the operator. A head support arm 19, frequently referred to as the yoke, and its front end conveniently attached to the head 17. Usually, an equalizer is interconnected between the head arm or yoke 19 and the head 17 to allow the ironing surface of the head to compensate for the differences in thickness of the pieces extended on the padded bock, which is partially shown in Figures 13 and 14, without however representing a characteristic claimed here. The head-carrying arm 19 is preferably metallic and hollow for lightness. -it may be in the shape of a channel or an inverted U with its open face facing downwards.

   Thus the top of this rather wide head-carrying arm 19 is smooth and its sides are closed so that it has a good appearance. the head-carrying arm 19 is bifurcated by a groove 20 extending upwards from its rear end towards the head 17, which gives a space intended to receive a control lever described below. This grooved construction provides two spaced arms 21 occupying the major part of the length of the head arm 19. This arm protrudes.

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 runs horizontally backwards and curves down behind the press jaws 15 - 17 then is hinged on two horizontally spaced support pins 22 carried by two spaced vertical console frames 5.

   Each supply pin 22 stops just at the inner face of its arm branch 21 so as not to enter into the groove 20 and not to obstruct it. The groove 20 of the head-carrying arm is left fully open and free for movement up and down around a support axis 22, levers for tilting the press head up and down 17. The spaced consoles frames 5 carry their twin supports 22, which define the pressure plane, that is to say the plane of the head and the bock, the axes 22 being parallel to the longitudinal axis of the pressing jaws 15 - 17.



   The preceding construction allows circular movement of the head 17 about its axis of rotation 22, its action being such that the head tilts up and back from the bock 15, thus exposing the latter so that the The operator can place a piece to be ironed there and smooth it out before pressing. As said previously, this general form of jaw press is sometimes called a scissor press because of this characteristic movement of the head around its rear axis 2. The rear end of the arm 19 carries a rubber-lined stop console 23 placed under the pivot 22.

   This stop 23 resiliently abuts either against the press frame or against the rear plate of the latter, and thus calmly stops and limits the upward stroke of the head 17.



   A specially designed head actuator 25, in the form of a compound motion lever, is mounted back into the press frame and into the groove 20 of the press.

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 head support arm 19. The upper control end 26 of this lever is bent forward in the grooved arm 19 on which it is articulated by a pivot 27. The upper end of the lever 26 has the same contour. than the head support arm or yoke 19, so that when the press is closed a continuous and neat appearance of the lever assembly 19-26 is obtained as shown in the views of the closed press.

   In other words, the upper end 26 of the compound movement lever 25 completely occupies and closes the grooved space 20 of the head arm 19 and is approximately the same thickness as the legs 21, so that the arm 26 oscillates in the arm 19 without freeing up any maneuvering space between these two movable parts relative to one another.



   This joint action of the two swinging members 26 and 19 provides a fully enclosed and shielded head operating mechanism at the rear upper part of the machine, so that there is no danger in the maneuver or for persons who may stand. Behind the machine in action, because, during operation, no moving parts project backwards while opening or closing the press. This part of the description is especially considered in connection with Figures 1, 8 and 9;, as far as it is noted that these are side and rear views in several different positions.



  The fact thus appears that the maximum movement up and down of the two members 19 and 26 occurs without opening a dangerous and unforeseen play between them. Note that in the wide open position, the dotted straight edge of the lever end 6 remains hidden between the head arms 19, 21 which embrace it. This inner and outer covering of the side surfaces of two movable members relative to each other

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 The other 19 and 26 provide a means of shielding and thus fill the functional clearance 20 on both sides of the arm and lever assembly 19, 26. This arrangement increases the strong closed appearance and general safety of the machine.



   In Figure 8, the upper end 26 of the control lever is expressly shown in dotted lines, behind the front branch 21 for clarity of illustration, but in the present construction, the upper surface of the head support arm 19 and that of the lever can be perfectly coincident with each other to give a shape: of a united appearance, in which the parts merge into analogous or similar contours. The invention, therefore, takes into account not only safety, utility and simplicity, but also the beautiful appearance in the structural form of the press.



   The compound motion lever 25 extends vertically downward a considerable distance and its lower end 28 adjoins the bottom of the press. When the press is open, the lower end 28 is substantially under the axis 22 of the press head 17. When the press is closed (figures 4,5,6,8,13 and 14) the end lower end of lever 28 is moved outward from foot frame 2-3 into a position which is no further than that of the outer edge of upper end 26 of lever when the press is open (Figures 1 , 2 and 12). This vertical and compact control assembly enables the manufacture of a press that can be installed against a wall, and takes up minimal space.



   The lower end 28 and the central part 25 of the lever curve inwards towards the face 3 of the press frame to form a prominent support bracket 29 by

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 relative to the longitudinal axis of the lever. This prominent support arm 29 curves upwards, below and in front of the support bracket 9 when the press is open, thus cooperating in compactness in form and construction, and stands at about one. third of the vertical distance of the lower end 28 of the lever. It can be seen that the extension 29 of the lever arm is mechanically connected with a system of high power and high pressure levers with variable stroke, while the lower end 28 is connected with a primary motor or any other control means. .



   The motor not only operates lever 25 to initially close the press, but also operates the lever system at high pressure through this lever 25, without rest or interruption. The complete movement from the position of Figure 2 to that of Figure 5 is therefore a smooth and continuous movement achieved by the simple system of low power levers 19, 25 which, alone, is not capable of. apply the strong ironing pressure on the head 17, although its leverage is well suited for the initial movement of the head 17 towards the bock 16.



  As a positive fact, it can be seen that the lower end 28 represents only a third of the length of the upper end 26, taking the arm 29 as the fulcrum of the long lever 25.



   The compound motion lever 25 is hinged between its ends, approximately two-thirds down, for full swinging movement relative to the press frame, on a high powered lever mechanism or advanced broken lever system comprising relatively short upper and lower connecting rods 31 and 32. These two short connecting rods are articulated one on the other by means of a pivot forming a broken lever toggle 33.

   The

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 upper link 31 is carried by or is articulated on a fixed support frame 34 in the. console 9, while the other lever 32 is connected at its lower end with the downwardly extending lever arm 29 by a free-moving or compound pivot 35 which follows the movement of the lever 25 upon release. opening or closing the press.



   The ratio of the levers of the broken lever mechanism 31, 32 only conforms to the achievement of high ironing pressure; the term high ratio, or high power lever system is used because of the lack of a better term. The magnitude of its force multiplication is so great that it is absolutely unusable as an initial means of closing the press, a function which is not required in the first place by high power. A multiplication of the driving force towards a mechanical force amplified several times is only required for the passage from the position of figure 4 to that of figure 5 and that for a displacement of the head of approximately one inch, while the displacement from the position of Figure 2 to that of Figure 4 can be twenty times greater.



   Experience has shown that the principle of the invention can be achieved with types and shapes of low ratio levers other than those indicated here at 19, 25 and with high ratio levers other than the characteristic broken lever. 31, 32, and its equivalent forms shown in Figures 8 to 12. At the same time, it is recognized that the particular forms of linkages chosen to illustrate the invention and its principles are also new and form part of the invention. invention.



   The upper link 31 is integral with a balancing arm 36 extending rearwardly of the support frame 34.



  A counter spring or press opening 37 is attached

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 at its upper end on a spindle 38 carried by the balancing arm 36 while its lower end is attached at 39 to the press frame. It is often desirable, in presses having a large and heavy movable head, to employ more than one spring 37 in order to increase the lifting force required to open the press. This is shown in Figures 6 and 7, but a simple spring 37 is first shown to illustrate the invention in its simplest form (Figures 1 to 7).



   The lower connecting rod 32 of the high pressure broken lever system 31, 32 forms an integral part of a guide rod or adjustment arm of the variable stroke broken lever 41. This rod 41 extends laterally towards the front towards the frame 3, from and as part of the side of the short vertical connecting rod 32. The front end of the connecting rod arm 41 rotates downward from the top 6 of the press. In other words, this member has a wide end 32 with neighboring centers 33 and 35 in a vertical plane and a narrow end 41 extending therefrom a distance greater than the length of the vertical link 32. The end 32 of the arm 41 may have the shape of a fork to embrace the two parts 29 and 31 articulated with it.



   The free end of the projecting arm 41 is articulated by a pivot 42 with one end of a short vertical guide or radial connecting rod. The latter has, in turn, its other end articulated, by an adjustable support frame 44, with the short arm of a broken lever adjustment lever, ie a broken lever 45. Therefore the radial connecting rod must oscillate around its pivot 44. The angled lever 45 is mounted inside the machine on a fixed support frame 47, with its other end extending along the face

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 of the frame 3, that is to say vertically upwards. A steering wheel 48 is journaled in the frame 3 and is fixed on a screw which is screwed into the longer part of the adjustment lever 45 of the broken lever mechanism.

   By turning the steering wheel in one direction or the other, its screw enters or leaves an articulated nut of known shape mounted in a branch of the elbow lever 45, which moves the latter around its pivot 47.



   The mechanism which provides allows full up and down movement of the adjustable support frame 44 to adjust the arm 41 around the pivot 35 to. movement composed of lever 25. Thus the broken lever mechanism 31, 32 at high pressure is adjustable relative to the press frame, and thereby relative to the bock 15. The aim is to modify the relative angular position of the three lever supports or pins broken 33, 34, 35 with respect to the upper pivot 27 of the swinging traction lever 25, modification by which the high power lever mechanism 31,32 can be adjusted to apply more or less pressure large between the cooperating jaws.

   Although this adjustment is seldom employed, it is or may be provided for the purpose of establishing or re-establishing the high power lever system 31,32 to compensate for the varying factors which may arise when the padding 16 is changed, or more particularly when a padding of one thickness is replaced by another of different thickness.



   A control means comprising a compressed fluid or pneumatic motor 50 is mechanically connected to the lower end 26 of the lever 25 to apply an outward angular force thereto and rotate the lever around its moving pivot. compound 35 carried by the high ratio lever system. Cylinder 50 has one of its ends

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 mounted on a pivot 51 which at its other end allows to oscillate and to follow the movement of the lower end of the lever 25. A piston 52 and its rod 54 are articulated by a pivot at the lower end 28 of the lever .

   An air hose 55 is connected with the cylinder head 50 above the piston to supply it with compressed air and push the piston in its rearward driving stroke to close the pressure. The air hose is connected through a main valve with manual control described below.



   As piston 52 pushes outward in its driving stroke, lever 25 rotates clockwise about its carried compound motion pivot 35 (movable fulcrum). by the lower end of the high pressure broken lever 31, 32. As a result, the upper end 26 of the lever moves to the right, but the support pin 27 moves on its axis around the support frame 22, and the head 17 is brought down by its arm 19. For this, the lever 25 turns clockwise on a pivot 35 and its lower end simultaneously swings outwards around its other pivot 27, as shown in Figures 2, 3 and 4.

   This movement brings the press head 17 to its initial closed position in which the elastic padding resists subsequent movement of the head. At this point, a substantial part of the driving stroke of the track 52 remains (FIG. 4).



   The pressure flowing through the air pipe 55 increases rapidly, so that the piston pushes towards the outer end of the cylinder, without stopping until the position of FIG. 5. The support pin 27 undergoes a substantial short movement towards the bottom of figure 4 to figure 5, while

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 Say that the hinge pin 54 is pushed rearward a considerable distance, and the joint of the broken lever 33 moves to a neutral line defined by the axes of the pins 34 and 35, but not beyond it.



   .The linkage 32, 41 initially acts (Figures 2 to 4) as a means for supporting and guiding the pusher 31 and the movable fulcrum 35 so that the control lever 25 can turn clockwise. shows around the pivot 35 to preliminarily close the press against the backing of the counter spring 37, then, (figures 4 and 5) the broken lever 31, 32 more particularly functions as a high pressure lever for the straightening action of the broken lever towards a straight line to produce pressure through its toggle joint 31 straightening up to achieve the strong jaw compression when the broken lever connecting rods 31 and 32 straighten up to a point where the driving piston 52 stops against the resistance of the bock 15.

   During the preliminary closing, the upper link 31 oscillates a relatively large angle (about 60 to 70 degrees) around its pivot frame 34 since it is only idle and not intended to exert pressure, while, during the final movement, the connecting rod 31 rotates through a smaller angle (i.e. about 40 to 45 degrees) and thereby amplifies the force application function required at that moment to push and produce the high compression of the jaws.



   In all, the push rod 31 oscillates through an angular distance of around one hundred degrees, without its toggle joint 33 passing beyond neutral. As long as the movement of the head for the final pressure (figures 4 and 5) is short, a broken lever with short connecting rods is advantageous to provide a great effort while taking up little space. It is

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 There is no need to have long and cumbersome broken lever links taking up considerable operating space when the initial press shutdown is not a large amplitude power consuming operation and can be accomplished by a lever 25 direct-acting with low mechanical advantage ratio.



   Figures 6 and 7 show the same system of broken high pressure levers as described above, but in a more perfected form to show more closely the principle of commercial construction, and to show more specifically a new antagonistic means to crank to open the press. The same reference marks are applied to the parts described above, except for the additional or secondary elements now defined and explained.



   The previously described arm 36 has an associated counter arm 36A which is integral with or is fixed on the short rod 31 of the broken lever described above, these three members taking the form of a fork, as shown in FIG. back of the press. An associated spring 37a has its extension on the arm 36A with its upper end attached to a pin 38A / and its lower end attached to the frame at 39A. The two opposing arms 36 and 36A are in the form of two spaced crank arms, flanking the support 9, the support frame 34 acting as a crank support. Pins 38 and 38A of both springs act as crank pins against which the springs exert a rotational force.



   It will be noted that the secondary crank shaft 36a is shorter than the first arm 36. In addition, these two arms 36 and 36A are spaced from each other by a substantial angular distance of approximately 60 to 80 degrees, so that the two springs 37 and 37A balance each other and thus do not act

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 not against the last portion of the engine's driving stroke (Figures 4 and 5) when the press is operating under high pressure.



  Since the tension of both springs 37 and 37A is approximately the same, the longer crank arm 36 extends the spring 37 to apply a counterclockwise torque slightly greater than the spring. shorter 37A. This double spring balance is built as an integral part of the high pressure lever system 31,32 and is efficient and smooth in its action.



  These springs act directly on the joint of the broken lever mechanism 33 to bend the connecting rods 31 and 32 and bring them back to their normal press opening position when the compressed air is released from the cylinder 50, thereby raising the ironing head 17 towards its wide open position.



  Thus, the two crank arms 36 and 36A provide a method of installing multiple springs to open the press. Two sets of twin springs are sometimes used, two parallel springs in 37 and two in 37A, that is to say in all four springs. Multiple counter springs are sometimes preferable to distribute the opening force among several springs to achieve easier extension.



   When the elastic spring padding 16 comes under final ironing pressure (Figure 5) a strong reaction is exerted against the head 17. The elastic padding 17 therefore helps to initiate the opening movement of the head 17 when the engine 50 is de-energized and releases the force of the broken lever 31, 3'2 ..

   The reaction of the elastic padding 16, and the tension of the springs 37, 37A quickly start the opening movement of the press. -When the crank pin 38A has oscillated counterclockwise to the left of the crank holder 34, the secondary spring 37A applies a twisting motion around it

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 support and help the spring 37 to return and maintain the press in its wide open position. the guide rod 41 has additional functions which give an improved mode of operation to the high pressure lever system 31, 32 which, for ease of reference, is referred to as a "broken lever" although it does not all work. quite differently from the normal broken lever.

   From another point of view, linkage 31, 32 may be regarded as a variable stroke crank, a term by which it has been referred to from time to time during the relatively long period of development of this invention. Whatever it may be, it is now explained that the element or guide 41 itself constitutes a broken lever control or regulator, which in its series of actions of Figures 4 to 5 acts to modify the stroke of the broken lever elements or mahivel- les 31, 32. This reference to a variable cpurse crank obviously concerns the two short oscillating connecting rods
31 and 32 of Figures 1 to? which should not be confused with the crank arms 36 and 36A of the opposing springs of Figures 6 and 7.



   There is another broken lever action to note, which is also controlled by the lever system adjustment means 41, 43. Reference is now made to pins 27 and 34. Tragging a straight line passing through their center , it will be observed that the pivot 35 does not exceed this line when the press is in its final position of FIG. 5. The pivot 35 moves fairly quickly to the left, but the connecting rod 41 continues to push back. 'broken lever joint
33 to the left to increase the distance between the support frame 34 and the compound movement pivot 35 which moves downwards, so that the latter does not exceed the dead center defined by a straight line passing through the pivots 27 and 34.

   In

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 Consequently, what can be called an inverted broken lever connecting rod 25, is arranged so that it depends on two pivots 27 and 35, the latter of which cannot be blocked beyond neutral, because of the amplitude variator 41 - 43. Another characteristic of the intention can be noted by the study of figure 5. The press exerts its maximum pressure here and is under tension. The control lever mechanism and its pivots are not only compactly arranged with a view to structural unity, but are also placed to exert the compressive forces most effectively and to use them for compression. the padding of the bock 16.

   It will be observed that the three pivots 34, 22 and 27 are located on an arc of a circle, the extension of which passes approximately in the axis of the two press jaws. In Figure 5, the center of a compass for plotting this circular force path will be found, by trial, slightly above and to the right of mark 9. This arrangement has been found to be advantageous, as most of the pressure force withstood by the machine when it is under final pressure is thus concentrated in a small space near the top of the machine, near the solid frame cover 6. The forces react and bend the circle in question 'and reach a static equilibrium on the ironing piece between the press jaws, due to the particular arrangement of the three main supports 34, 22 and 27.



   The existence of the force circle described above is further illustrated in FIG. 13 where the reference 127 defines the position of the center of this circle passing through the center of the closed jaws and through the three main supports 111, 22 and 27. Thus, the main effort under which the press

  <Desc / Clms Page number 25>

 remains finally closed is supported by the top of the frame 109 and the vertical horns 5 which form a body and which are at best qualified to carry such a load. Thus, the light chassis housing 2, 3 is not unduly stressed.



   The high power fixed cam lever system is shown in figure 8.



   This view features a fixed cam type high power lever system for guiding the movable fulcrum 35. The construction of the press may be exactly the same, and the same marks are used, except for the cam and the press. the modified roller lever system substituted for the broken lever system 31, 32 described above.



   The press opening counter spring 57 has its active end attached to the lower end 28 of the lever 25 by a hinge pin 54, while its upper end is attached, as shown, to the top 6 of the press frame. . The spring is placed at an angle such that it exerts an upward and forward pull on the lever 25, to lift the movable press head 17.



   A cam 58 is adjustably mounted on a fixed pivot 59. This cam has a substantially vertical stroke 60 and a horizontal stroke 61. A roller 62 journaled on the pivot with movement compound at the movable fulcrum is housed in the parts 60. - 61 of the cam, where it can move vertically and horizontally. The vertical travel 60 of the cam supports and guides the lever 25 as it rests on its pivot 35 to exert an initial closing force on the head 17.



   An adjustment handwheel 63 and a screw adapted to thread in and out of a cardan nut mounted at the end of the cam 59 are similar to the adjustment for the crank lever 45. The rear end of the horizontal stroke 61 of the cam is moved downward by the flywheel 63 to produce

  <Desc / Clms Page number 26>

 pulling down on the lever 25. The stroke 61 of the cam can be adjusted to compensate for the differences in the thickness of the padding of the bock 16 and to adjust the high final pressure between the jaws of the press.



   Note that in its two forms (figures 1 and 8)
The compound motion pivot / is adapted to undergo substantially the same angular motion. This is due to the fact that the lower end 28 of the lever first rotates clockwise around its compound motion pivot 35, in each form of the high pressure lever system for pressing. forward against the upper pivot 27, after which this lever 25 moves downward (although still rotating on its pivot 35) to complete the initial closing action, and finally its hanging lower end switches / outwards on its upper support pin 27.



   The foregoing new mode of action is effective because the motor 50 first uses the upper long lever arm (portions 25-26) above the arm 29 to achieve a relatively fast closing speed. Then, a strong amplification of the force exerted by the lever 25 is gradually achieved by transforming its rotation around the pivot 35 into an outwardly oscillating movement around the upper pivot 27. This movement of the lever is transformed into a downward pull exerted by the stroke 61 of the cam on the head arm 19.



   The guide or varlator linkage 41 - 43 explained previously and the vertical travel 60 of the cam discussed here, both perform a guiding function for the lever 25 as it rotates about its pivot 35, until a subsequent displacement of the head 17 is stopped by the cap- tonnage of the tank 15. Then, the lever broken at high pressure

  <Desc / Clms Page number 27>

 31,32 and the horizontal stroke 61 of the cam also exert a powerful downward pull on lever 5 and its upper pivot 27, so that lever 25 no longer rotates around pivot 3 $, but oscillates. from the head support arm 19 on which it pulls down.



   The motor and its control are shown in FIG. 11 in schematic form, the motor element 50 having already been described. The already mentioned air tube 55 is connected to the central part of a main control valve body or housing 67 placed at the lower part of the machine frame.



  A main air supply line 68 from a compressed air source is connected directly to the top of the main valve 67. When this main valve automatically opens the compressed air, under full pressure, flows. the directly through the tube 55 into the cylinder 50 without passing through a manually operated start-up throttle valve briefly described below.



   Any suitable control device can be employed for starting the engine 50 and for the initial closing of the press (Figure 4) and an example of such control is necessarily shown here since it cooperates with a new automatic control of the engine. as characteristic of the invention.

   One. known form of two-handed control is chosen as the starter valve for the purpose of illustrating the characteristic in question. a left hand button 69 is mounted on the face of the press table, while a right hand button 70 is spaced to the right of it, although 3.1 is not seen in the side view (Figure 1 ) since it is behind the button 69. The operator must press the two buttons 69 and 70 and keep them pressed with both hands to start the motor 50 and keep it in action as the press head 17 passes through the zone dangerous (figure 3) and

  <Desc / Clms Page number 28>

 reaches the bock (Figure 4), after which the operator can safely release the buttons.

   It can be seen that, then, the automatic valve 67 automatically maintains the engine in a state of excitation by keeping the main duct 55, 68 open to maintain the brisk air pressure on the piston 52.



  The press jaws are thus kept in contact under strong compression and the head 17 continues to press against the elastic padding throughout the pressing. This is because, as piston 52 passes opening 89, air passes through pipe 90 and bends diaphragm 92 upward, thereby keeping valve 97 open.



   A branch 72 of the air tube is connected at one end thereof with a combined intake and exhaust valve body 73 which is one of the two hand valves and which is actuated by a button 69. A tube. air valve 74 connects valve 73 with a chamber 75 in main valve 67, and an exhaust tube 76 connects chamber 75 to an exhaust valve body 77 which is the other hand valve actuated by an air valve. further button 70. The valve body 77 contains a normally open exhaust valve with a stem 78 arranged to be closed by the button 70 to close an exhaust opening 79 and thereby obtain the tube 76, so that the air entering the chamber 75 of the main valve cannot escape to the atmosphere.

   In this way, the air flowing downward through tube 75 is directed upward into the cylinder through tube 55.



   Button 69 is depressed to push inwardly a valve stem 80 common to a normally closed intake valve 81 and a normally open exhaust valve 82. This action reverses the position of the valve torque 81, 82. against the action of a spring 83 the now

  <Desc / Clms Page number 29>

 in its normal position (FIG. 11) so that the intake 81 opens and the exhaust 82 closes. Thus, the outlet opening s4 of the branch '/ 2 is closed, and this branch opens directly into the air tube 74 connected to the valve body 73 between the opposite seats of the valves 81-82.



   A throttle valve 86 is placed in the branch 72 between the supply tube 68 and the valve 73.



  This throttle valve 86 has a threaded valve needle or stem 87 with an adjusting handwheel. Valve needle 87 can be screwed or unscrewed to adjust the size of the passage opening shown in valve body 86 so as to restrict and adjust the initial flow of compressed air from branch 72 into tube 74 and from there through the air pipe 55 into the cylinder 50 to start the piston 52.



  The high air pressure from the supply tube 68 to the hoses 72, 74 is preferably reduced by the hand valve 87 in order to properly control the speed of the piston 52 and thereby the closing speed of the valve. press head 17. The needle adjustment valve 87 is adjusted according to certain conditions such as the air pressure available in the supply pipe 68 and the personal desire of the operator.



   On the other hand, the full air pressure of the feed tube 68 is desirable when the head 17 reaches the bock (figure 4) so that no stoppage occurs in the movement due to the resistance offered by the upholstery 16.



  Rapid and full supply pressure compensates for the sudden drop in pressure in cylinder 50 caused by the rapid outward stroke of piston 52 and prevents hesitation of the piston when the head meets resistance from the padding.

  <Desc / Clms Page number 30>

 



   The operator presses the two buttons 69 and 70 and starts the motor piston 52 in its forward stroke towards an opening 89 which is not discovered by the piston 52 as long as the head 17 has not passed the danger zone. and reaches the initial closed position (Figure 4). It should be remembered that the button 69, by its depressing, opens the normally closed inlet valve 81 and closes the normally open exhaust valve 82, that the button 70, by its depressing, closes the valve d. normally open exhaust, and operation of the release lever 99 opens a normally closed exhaust valve 100 which releases air from the diaphragm chamber 91, thereby allowing valve 94 to return to its position. normal in which the head 97 is closed.



  When the opening 89 is discovered by the piston 52, the compressed air from the cylinder 50 passes through a diaphragm feed tube 90 into a chamber 91 where it bends upward a diaphragm 92. The diaphragm 92 pushes on a rod. 93 to close a main exhaust valve 94 against its seat 95. In its upward movement, this valve 94 in turn pushes against a rod 96 and opens a normally closed main intake valve 97.



   The compressed air now by-passes branch 72 and flows directly from the supply pipe 68 through the open inlet 97 into the air pipe 55. Since the valve head 94 is now closed against its seat 95, the compressed air coming from the feed tube b8 can no longer escape into the atmosphere through the tube 76 and its exhaust valve 77 open.



   A spring 98 normally applies the main inlet valve 97 to its seat and keeps the exhaust valve 94 away from its seat 95. The thrust of the diaphragm 92 is sufficient to compress the spring 98 and reverse.

  <Desc / Clms Page number 31>

 the position of the valve shown in the figure. 11 when the piston 52 discovers the opening 89 of the cylinder. Spring 98 returns the main valve to its press-open position, as shown, and straightens diaphragm 92 downward when pressure is released from diaphragm chamber 91, and thereby de-energizes motor 50 by means. which will now be described.



   The opening 89 of the cylinder, in conjunction with the main valve 67, bypasses or eliminates the action of the engine starting line 72, 74 with its choke valve 86 and its two-control valve. manual 73, and performs this action just when the press head 17 meets the resistance of the padded bock 16, 17. The application, at this moment, of the entire flow of compressed air, without restriction or pressure , nor in volume, coming directly from the supply pipe 68 increases the pressure in the cylinder 50 to continue the driving stroke of the piston.

   Without this by-pass action the head 17 would stop when it hits the bock until the pressure has increased in cylinder 50, but the new air line control device allows for continuous stroke. of the piston until the compression on the bock stops the engine (fig. 5) under the maximum ironing pressure.



   A simple form of exhaust click lever 99 for opening the press is mounted on the table, or on the front flange 7 thereof, for ease under the two-handed control valves 69 and 70. This exhaust click 99 can be hinged to a valve body 100 having a large normally closed exhaust opening 101 by a valve head with a stem 102. A spring holds the valve 102 in its seat to normally close the opening. 101 and keep the click 99 in its lower position. This press opening exhaust valve 100 is connected by an exhaust tube 103 to the diaphragm chamber 91.

  <Desc / Clms Page number 32>

 



   By lifting the click 99, the valve lu2 is pushed inwards against the pressure of the spring tending to apply it to its seat, and the large exhaust opening lul immediately connects the diaphragm chamber 91 to the atmosphere. sphere through tube 103. The outlet through the exhaust opening is slightly larger than the opening 89 of the cylinder, so that a pressure drop occurs instantaneously in the chamber. diaphragm 91 when the click 99 is raised. The spring of the main valve 98 then abruptly closes the inlet valve 97 and opens the exhaust valve 94 (position of Figure II), resulting in rapid exhaust of air from the cylinder. 50 through the pipe 55 then outside through the tube 76 and the opening 79 of the valve body 77. The springs 37 and 37A then open the count press explained above.



   Quickly after pressing in both push-buttons 69, 70 the air passes from the main line 68 through the pipe 72 and the pressure reducing valve therein, to the valve housing 73, passes through the valve open intake 81, through pipe 74 to valve housing 67 and from there through pipe 55 to cylinder 50 where it acts on the cylinder in its driving stroke. Since the valve operated by the push button 70 is closed, air cannot escape from the valve housing 67 through the pipe 76. Air cannot pass from the main line 68 to the cylinder, the valve. 97 being closed.



  When the piston 52 passes, in its driving stroke, the opening 89, the air passes from the cylinder through the pipe 90 into the diaphragm chamber 91 where it actuates the diaphragm 92 to close the valve 94 against its valve. seat 95 and open valve 96 so that air can flow from pipe 68, through open valve 97 and pipe 55 to the cylinder. Air cannot escape from pipe 90 through pipe 103 and the exhaust valve.

  <Desc / Clms Page number 33>

 ment '100 because the valve in the housing 100 is closed. Therefore, because of the reducing valve 86 the press moves to its closed position under reduced air pressure but achieves the final compression with air under full pressure.



  Acting on the exhaust valve lever 99 to open the exhaust valve in the housing 100 releases the pressure under the diaphragm 91, allowing the valve 97 to close to shut off the air pressure, and as the operator has previously released the buttons 69, 70.) the valves actuated by these are already in the normal position. Thus, the operator keeps the push buttons 69, 70 depressed until the piston exceeds the opening 89, at which point the button 69 can be released, the press remaining closed by the action of the compressed air. on the diaphragm 91.



  It will remain closed until the exhaust lever 99 is opened.



   A further explanation is now given with respect to the first form of lever system variator shown in the previous views, but more particularly of a new form of variable stroke high pressure lever system combined with a regulator. hydraulic speed.



   This new system of levers (Figures 12 to 16) is a continuation of the material based on the US patent application Ser. N 104,672, and is largely covered by it.



   The slightly disordered action of the head, which might otherwise occur, is smoothed and coordinated with the drive means by the fully automatic high power, variable stroke lever system under the control of the reduced radius variator lever system 41 shown in the previous views. But the whole combination is now more perfected in certain peculiarities by realizing it in the form of a system of variable-speed levers.

  <Desc / Clms Page number 34>

 free tion shown in Figures 12 to 16 as a
118 oscillating cam They. The movement of this cam variator / is capable of very fine adjustment, as it is not subject to the restrictive influence of the radial connecting rod 43 trapped on its fixed center 44, as shown in the previous views.



   By presenting this modified or improved form of the invention shown in the new views, it is understood that the reader will now know the construction and operation of the laundry presses explained above, and more particularly of the forms shown in Figures 1. at ?. These views show a high pressure, variable stroke lever system comprising what may be called broken lever rods 31, 32 which are under the control of a regulator which may be referred to as the coordinator or variator 41 of the controller. lever system. The front end of the latter to the pivot 42 is, as can be seen in its operation, limited to a displacement in an arc of a circle around the pivot 44 by the radial connecting rod 43.

   For this reason, 11 is limited in its action of adjusting or varying the lever system, and is therefore not of maximum efficiency. These limitations are overcome by adopting the new cam and roller variator 118 shown in Figures 12 and 13 because its movement is controlled by a cam calculated for smoothness and constructed to accommodate the various factors encountered for efficient maneuvering of the gear. ironing head by a single cylinder high speed compressed fluid motor.



   Reference is first made to the previous views (Figures 1 to 7) and to the parts there identified by 9, 31, 32, 41, 43 as well as to their support pivot in order to explain that they are the particular elements which are represented there and which have now been modified in construction and mode of operation.

  <Desc / Clms Page number 35>

 operation and which are identified by new numbers for the following explanation of Figures 12 and 13. The same reference numbers are used in Figures 12 and 13 for parts of the machine which are identical to those of the previous views. . Therefore, the new reference numbers are only used for the new parts which are now explained.



   One or more counter springs 105 have their lower end attached to a frame pin or pivot 109 and their upper end to a tractor pivot 107 at the rear of the head support arm 19,21. A spring longer than springs 37 is used to achieve greater elasticity and lower resistance along the long, fully automatic closing action of the press. A spring 105 is shown, but in some cases two or more are used, depending on the size and weight of the ironing head 17. This spring 105 is placed between the vertical frame sheets 2 and extends along of the tractor lever 25. Sometimes two or more springs are used, then they are placed, one or more, on each side of the tractor lever.



  The springs are used to open the press when the compressed air escapes from the motor 50 by the operation of the click valve 99 (FIG. 11) and they maintain the press in its normal open position. Counter springs are powerful enough to quickly open the head and release the ironed piece on the canister 15 so that the operator can remove it and place another piece to be fed.



   A console 108 carrying a high pressure lever system hangs from the top cover of frame 109 at the rear of the press and is roughly similar to console 9.



  This console is preferably made with a cover of

  <Desc / Clms Page number 36>

 frame 109. The latter extends rearward from the front plate 3 to form a support for the bock 15, then upwards in the vicinity of the pivot frame 22 where the head-carrying arm 19 is articulated between the two vertical frame horns or brackets 5. It is preferable that the vertical frame horns 5 are integral with the top plate 100 in order to bring together in a small space the parts carrying the main force and the force exerted on the shifting capmtonnage 16.



   The support bracket 108 has a protrusion integral with it, in the form of a stopper or shoulder 110 centered on a powerful lever system pivot or shaft 111 journaled to oscillate in the chassis console 108. In fact, this console preferably comprises two parallel frame parts 108 integral with the frame cover lv9, by which the high pressure, variable stroke lever system is interconnected between these press frame consoles 106 and the motion transmitting members 19, 25.



   A short radial arm, which may be called a broken lever link 112 may have its upper end hinged to the support frame III, but the broken lever arm 112 is currently hinged to the shaft 111 so as to oscillate. in the support frame 108; in order to establish a direct attack of the hydraulic speed regulator (Figures 14 to 16) described later. This broken lever link 113 also has a stopper or shoulder 113 which is integral with it and which is also concentric with the pivot 111, adapted to tilt clockwise (Figures 12 and 13) and comes to rest, and thereby abut against the fixed frame shoulder 110.

   The free end of this

  <Desc / Clms Page number 37>

 arm carries a pivot 114 approximately identical to the broken lever joint 33 in the first views of the drawings.



  Next, a second pivot 115 is provided on the arm 29 of the compound motion tractor lever 25, similar to the pivot 35 in the previous views. A connecting rod 116 mechanically connects the two pivots 114, 115.



   If there were not for these levers a differential or variatenr 41 and its new successor 118 in figures 12 and 13, the two connecting rods 112 and 116 taken together could constitute an ordinary broken lever, but the action of the latter is so different from that of a normal broken lever that this new way could be called partial rotation variable stroke crank. However, this part 116 can be referred to as a connecting rod of a broken lever since it connects the two pivots 114 and 115, although it is currently the rear or left portion of the new lever system variator 118 to be described.

   The connecting rod 116 may be fork-shaped to receive the lower end of a short arm 112 and the upper end of a longer arm 9. Another equally favorable construction is a forked shape of the members 11 and 29 receiving at inside the short connecting rod 116.



   The broken lever regulator, or what may be called a lever system variator, motion regulator, or guide 118, forms an integral part with a broken lever link 116. extends forward. in the press frame, and, being controlled by a cam, has an improved mode of operation over previous systems 41 of the preceding views. This type of cam lever system variator 118 modifies or guides the action of the broken lever links 112 and 116 so as to produce a new element in the lever systems of the levers.

  <Desc / Clms Page number 38>

 fully automatic pressing machines.

   It can be said that only the two acting connecting rods 112 and 116 constitute a broken lever, but the flexible variator control member 118 is considered not to form a new broken silk lever but also a new combination. Thus, each of the variators 41 or 118 coupled in the connecting rods 112 and 116, forms a broken lever entirely different from the generally accepted form. As far as they are structurally and functionally known and understood, and regardless of the number of names that one can give to these parts, alone or in combination, this new arrangement provides a marked improvement in the systems of levers of the presses. laundry.



   We see that the variator of the lever system itself is integral with the connecting rod 116, but for convenience, a number identifies the straight part 116 coupling the pivots 114 and 115 while another number 118 identifies the right end. The or regulating part of the lever system having automatic stroke adjustment action on the broken high power lever 112, 116 as well as on the stroke of the driving piston 53.



   The lever system variator 118 is recessed in its outer or front end with a long downward sloping cam profile 119, joining a short upward sloping cam profile for high pressure displacement. The last portion 120 is almost horizontal when the press is open (Figure 12) but assumes a vertical position when the press is closed (Figure 13). The cam profile for closing the press 119 and the cam profile for the high pressure 130 are connected by a fillet 131.

   The first cam profile 119 is defined, between its outer end and the fillet 21, by an arc of a circle

  <Desc / Clms Page number 39>

 whose center is located just above the lower edge of the limb They. Likewise, the. second cam profile 120 is defined by a shorter arc of a circle directed upwards and to the straight line, the center of which is just beyond the upper edge of the member 118. The curvatures of the two curves appear here on a small scale. , but are more pronounced on a large scale and when observed on the full-size machine.



   The differential cam or lever system variator arm 118 is trapped on a cam follower 122 journalled on the elbow lever heretofore identified 45 but now indicated as 123 in Figures 12 and 13. The roller 122 acts as a frame support since it is held in a fixed position by an elbow lever 123 adjustable in an adjustable manner to the press frame. This lever is articulated on the inside face of the press in 124 by the console 10.-One end of the lever 123 carries the cam roller 122, and its other end is capable of a limited adjustment movement around the pivot 124 in the aim to adjust the position of roller 122 in height.

   This adjustment is preferably employed only by the press builder to properly place the press head and high pressure lever system to a predetermined position measured and accurately marked after press assembly and placement. padding 16 on the bock. Such an adjustment, once made, is permanently fixed and remains in its position when the press is in use unless it has been improperly adjusted by clumsy hands.



   The upper end of the bent lever 123 is shown provided with any means suitable for an adjustable fixing of the latter on the frame and for carrying out the above-mentioned adjustment in the factory. A suitable device can

  <Desc / Clms Page number 40>

 be a fork at the upper end of the elbow lever, to receive an articulated nut 13 into which is screwed one side of an adjusting screw 126 provided with a locking nut against the outer face of the press frame 3, and a collar fixed to this screw with tab 16 inside it.

   When the press is assembled and the padding 16 placed, a key is used on the bolt 126 and its locking nut in order to very exactly adjust the position of the obstructed lever 13 around its pivot 124. Thus, the position of the cam follower 122 is carefully adjusted in height so that it, .. correspondingly moves the front end of the lever system variator 118, and thence moves the interconnected motion transmitting elements 25, 19. between the motor 50 and the head 17, to apply a predetermined ironing compression between the head and the bock, the most suitable for the type and the particular model of press when it is put into service.



   The above-described arrangement for achieving the required ironing pressure is placed in the shop machine as a part of and inherent in its construction. It is not necessary for the purchaser or user of the press to manipulate device 126 or to change its setting originally made by a specialist in the manufacture. The adjusting handwheel 48 shown in the previous views serves the same purpose, but it has been found that, following an erroneous impression, certain operators can disturb the press by turning the handwheel 48 suitably placed.

   It has thus been found that it is often preferable to remove it and replace it with this small adjusting screw head 126, which, being under the table and not being provided with a suitable adjusting handwheel, is not seen by a curious operator, nor so quickly adjustable. On the other hand, some

  <Desc / Clms Page number 41>

 Users are not satisfied if they cannot adjust their press, so that sometimes the presence of an easily accessible adjusting wheel is preferable.



   Arriving at the description of some of the operating characteristics of this new press, reference can be made to the previous views, particularly to Figures 2 to 4 presenting the study of the movement. One sees that the roller 122 is normally at rest in the vicinity of the press fillet 131 when the press is open (Figure 12) and lies along the long camber 119. When compressed air is admitted to the front end of the press. cylinder 50, the lower end 28 of the main lever 25 tilts rearwardly about its pivot 35 or 115.



   The press head 17 now starts down around its pivot axis 22, thereby moving the support point 115 downwards, and the cam profile 119 for the press closure first moves towards. down and to the right on the roller 122 for the main displacement (figures 2 to 4) of the head 17 towards the padding 16. making this displacement, the action of the first cam profile 119 rapidly transfers the seal from the lever 114 to the left in a clockwise direction (and thus moves or advances this central pivot or broken lever joint. 114 between the outer pivots 111 and 115) and thereby increases the amplitude or stroke of the levers or cranks 112 and 116 acting at this time (Figures 2 to 4) as an additional guide for lever 25.

   In other words, the low power lever 25 carries with it the high power lever system 112, 116 and the lever system variator 118 accelerates the moving fulcrum: because of the gradual decrease in the mechanical advantage of the low power lever system 19, 25 which

  <Desc / Clms Page number 42>

 accelerates the closing movement of the press head and thus saves the piston stroke 52.



   As a result, the broken lever seal 114 is accelerated counterclockwise about its fulcrum 115 during the simultaneous clockwise movement of the upper link 112 by the actuator. tion of variator 118 guided by its cam and its roller. This broken lever joint is advanced to the left (note the same pivot 33 in figure 2) above the pivot 115, thus pushing the latter downwards by pulling down the lever 25 and the head 17 without expense. exaggerated stroke of the engine piston.



   Just before the short connecting rod 112 reaches its lower position (figure 13) it begins to boost the power of the motor 62 and applies the final pressure before its stop 113 reaches the shoulder 110 of the frame * This is due to the fact that the ironer head 17 has reached its high pressure position and the motor 52 has stopped due to the resistance of the padding 16.

   When the head reaches the bock, the variator of the lever system 118 reverses and acts in approximately the same way as the connecting rod 41 (compare its position in figure 4 to that of figure 3) and now moves in the opposite way. up and left until the cam fillet 121 returns back to the roller 122, where the ironing head absorbs the fluffy slack from the upholstery 16. The cam fillet 121 then rotates around the roller 122 and the second cam profile moves slowly to the left and down on the roller as the high power lever system 112, 116 rests the head from the position of figure 4 to that of figure 5, performing compression final jaws.



  The piston 52 finally stops under the force, but maintains the pressure on the head 17 to advance it each time the padding 16 is ceded.

  <Desc / Clms Page number 43>

 



  However, the broken lever stops 110, 113 do not yet come into contact, because the connecting rod 112 preferably remains free to move clockwise when the driving piston 52 forces the head more strongly against the padding. 16.



   At the origin of the movement of the head, that is to say at the start of the head 17 downwards overcoming its inertia, the motor 50 uses its first pulse of energy to directly articulate the low lever. power 25 on pivot 35 or 115, which means that the motor acts directly on lever 25 and not on the high power lever system 112, 116; the latter simply follows the lever 25. The ratio of the lever arms inherent in the low power motion transmitting elements 19, 25 itself is just sufficient to achieve an easy starting of the head. Head start is not hindered by the high power lever system 112, 116.

   Then, the continued movement of the head does not require additional power; in fact, an effort sufficient only to tension the counter springs 37, 105 is all that is required.



     The high power lever system 31,32 as well as 112 does not withstand the push of the piston as long as the head is moving towards the bock (figure 2-4) but it simply follows the downward movement with the lever 25. Thus, the driving force applied to the joint 54 acts directly to rotate the lever 25 around the pivot 35 or 115, to effect the long closing movement of the head, and, meanwhile, the locking system. high power levers (figures to 4) act to accelerate the downward movement of lever 25 and reduce the required stroke of piston 52, so as to keep it until the end (figures 4 and 5)

  <Desc / Clms Page number 44>

 for compressing the padding under the final ironing pressure.

   Easier and less abrupt starting of the head is now obtained with these motion transmitting means forming a new compound lever system than with ordinary laundry presses with a single cylinder connected with the high power side of a system. me of compound levers.



   When the press begins to close, cambrue 119 moves down and right on roller 122 and the outer free end of the lever system variator 118 swings counterclockwise on the roller. , but, when the head reaches the bock (Figure 4) the first cam profile has reversed its movement and brought the cam fillet 121 against the roller.

   As the cam fillet 121 again revolves around the roller and passes it, the ironing head begins to compress against the padding 16, and the short outer profile 120 controls the reduction lever system 112, 116 and works with it in such a manner. that the driving piston 52 now increases the length of its stroke in proportion to the reduction of the downward stroke of the fulcrum 115, to cause a slight movement to the ironer head 17 under a reduced lever arm ratio ', by the straightening movement of the connecting rods of the broken lever 112, 116 during the relatively long stroke of the piston 52.



   The cam and roller 120 only support a small portion of the total load or thrust and are not subject to the considerable wear and deterioration seen in normal presses with direct acting levers and cams. Only a small fraction of the total load carried by the high power lever system 112,116 is transferred to the cam profile and roller 112. Minimal wear.

  <Desc / Clms Page number 45>

 occurs and the mechanism gains in service life.



   Each of the various mechanisms of the lever system 41 or 118 is very economical in the expenditure of the stroke of the piston b2 between the start of the head 17 and the position of FIG. 4, passing through that of FIG. 3. Thus, the variator 118 saves the driving stroke of the piston to the position of FIG. 4, from which the second cam profile 120 rapidly expends the stroke of the track.



  This action cannot of course be achieved by the use of an ordinary broken lever linkage, but is largely performed by the trapped link 43 regulating the movement of the variator of the lever system 41 in the first. re form of this invention, and more effectively accomplished to a degree driven by the contour of the cam profiles 119-120 in the new lever system variator 118.



  In short, the cam groove 119 and the roller 122 perform approximately the same movements as the arm 118 and the
112 and 116 briaé lever links / (figure 12) like the connecting rod 43 approximately replace the arm 41 and the broken lever links 31, 32 (figure 1).



   When the elastic padding 16 of the bock becomes thin and loses some of its elasticity, this press produces the same ironing compression as when the padding is new and fluffy and has its original elasticity.



  This is achieved by the additional stroke of the piston 52 and the action of the system composed of levers with its variator 41 or 118. Thus, there is no blocking action of the broken lever (overrun of neutral) in the pad wear stages, and for the thinnest worn padding, there is always sufficient piston stroke to achieve the same compression of the jaws as when the pad is new and thick.

  <Desc / Clms Page number 46>

 



   The upholstery 16 gives way with use and loses its strength and elasticity, but this system of levers compensates (or here follows down) this regression of the upholstery by pressing the head down for each fraction of the decrease in thickness. original upholstery. Consequently, this new system, composed of levers, produces a uniform pressure and a uniform ironing quality for all degrees of thickness of the pad 16. New upholstery of the same manufacture, thickness and construction can be placed. - ced by the operator without modifying the adjustment device 48 (Figure 1) or 126 (Figures 12 and 13).

   However, if the user or operator places any other type of upholstery that does not conform to the factory standard upholstery, the lever. setting 45 or 123 must be readjusted to the conditions of this upholstery.



   When the compressed air is released from the cylinder: 50 the reaction and expansion of the springs of the padding 16 give an opening pulse to the press. The two counterclockwise springs 37 and 105 then act quickly to impart to each pivot 35 or 115 a counterclockwise return movement to open the press. This is true for any relative position of the ironer head of Figure 4 to Figure 5 and for any degree of wear or sagging of the padding.



   In placing new padding on the bock, as well as for any other convenience, the broken lever stops 110, 113 simply prevent the broken lever toggle joint 114 from accidentally being overproduced. far to the left (Figure 13). The power of the opening spring of the press 105, or other forces, may accidentally throw the broken lever seal 114 far enough beyond its normal stroke to render it

  <Desc / Clms Page number 47>

 hard to go back and, as can happen during machine maintenance or repair, the broken lever stopper 110,113 is provided as a means to prevent this difficulty.



   In order to control the speed of the prepassing head 17, and in particular to make possible its up and down movement at high speed without shock or mechanical stress on the press, a combination of a speed controller and a shock absorber is mechanically connected directly with the press lever system in a new and efficient way. Ordinarily, this device is referred to as a "speed regulator" and its two functions are believed to be performed by an improved mode of operation superior to the practice of ordinary laundry presses.



  The construction of this hydraulic regulator is the subject of United States Patent Application No. 338,785 filed June 4, 1940.



   It will be noted, in the examples given, that the hydraulic regulator is directly connected to the main shaft carrying the high power lever system, either shaft 34 (figures 1,7) or shaft 111. (Figures 12, 14), the hydraulic regulator being referred to these latter views.



  Accordingly, the oscillating link 31 of the broken lever must be attached to the shaft 34 to make it oscillate, and likewise the broken lever link 112 is shown wedged at 129 on the shaft 111 of the high power lever system for drive or oscillate the latter as a drive means of a hydraulic regulator 130 now described. The shaft 34 or 111 of the high power lever system has a large oscillating movement.



   The oscillating action of the high power broken lever system 31.32 ¯ where 112-116 acts to positively oscillate

  <Desc / Clms Page number 48>

 the shaft 34 or 111 in the frame supports 9 or 108 as the drive shaft for the regulator 130. The shaft 111 is tilted clockwise by the driving piston 52 to close the ironing head 17, and it is tilted in the opposite direction by the action of the counter springs 105 to open the press. 1.1 It is important to note that the shaft 111 is directly connected to the regulator 130.

   This regulator acts to control the closing speed of the press by keeping the press at a constant speed, and thus preventing any exaggerated speed during the fast closing cycle, and it also acts to allow an open speed. .maximum but it slows down the inertia and absorbs the shock at the end of the rapid opening cycle.



   The hydraulic regulator comprises a cylinder or fixed block 130 / mounted on the side of the press frame either by screws 132 screwed into bosses 133, a pinion shaft 134 journalled in the upper part of the cylinder block 130 so as to be in the The axis of the shaft 111 or 134. The shaft 134 is provided with a coupling sleeve 135 which mates the coupling sleeve 136 on the shaft 111 of the press. A pinion 138, housed just below the cylinder block cover 131, is secured to the shaft 134 inside the cylinder block. Pinion 138 meshes on its opposite sides with racks placed on plunging pistons working in holes in: cylinder block 130.

   One of these plungers 139 is provided with a piston 141 working in the cylinder 140 of the cylinder block 130. The other plunger 145 is provided with a piston 146 working in another cylinder 147. During the oscillation of the pinion 138, these divers move in the opposite direction of each other. Appropriate valves are placed to control the flow of liquid in and out of it. the lower end of the cylinders towards the

  <Desc / Clms Page number 49>

 terior of the cylinder block 130 which forms a reservoir. 142 designates valve boxes.

   These valve housings also respectively carry throttle needles 143 and 1480 As the material of this hydraulic damper does not form part of this invention, but constitutes the material of another application, it is sufficient to keep in mind. However, as far as this invention is concerned, that the opening and closing movement of the press is controlled by this hydraulic damper by a shaft of the high power system of the press mechanism, such as shaft 111.



   In the operation and use of the press, the operator places the wet leached garment or part on the container 16, in the usual way, then presses the control buttons 69 and 70 (figures 1 and II). as previously described, to energize the motor 50 and close the press. Any suitable form of motor and control can, of course, be employed in connection with the various features of this invention, so that motor and its control are referred to herein merely by way of illustration. The ironing head 17 remains under the final pressure of the jaws until the ironed part is dry, after which the operator opens the press by making any suitable opening control, as indicated in 99 (figures 1 to 11).



   In operation, the motor 50 provides an outward thrust on the lower end 28 of the lever 25, which initially rotates the lever clockwise on the movable fulcrum 115.



  This movement causes a downward and forward movement at the head arm pivot 27, with the result that the lever 25 undergoes an overall downward and clockwise movement, and at the same time , begins to straighten out the broken high power lever system 112-116.

  <Desc / Clms Page number 50>

 



  When the latter is upright, the lever variator 118 operates as previously explained to accelerate the downward movement of the movable fulcrum 115 and, at the same time, reduce the stroke of the piston 52, thereby partially saving the length. of the latter for the application of the greatest force required by the passage to the final pressure (figures 4 and 5).



   Thus, the motor 50, or any other form of motor, initially acts on the system of low-power levers 19, 25 to bring the ironing head 17 onto the bock (Figures 1 to 4) and then the motor acts directly on it. lever 25 to pull the head down through the high power lever system 112, 116 into the final press position. During this press closing operation, governor shaft 134 swings clockwise to move the speed regulator piston downward. The hydraulic piston 146 acts as a means to prevent the motor 50 from accelerating the ironing head and preventing the latter from exceeding the speed for which the hydraulic regulator is set by its speed regulating valve stem 148.



   It is important to note that in the final straightening action (Figures 4 and 5) of the high power lever system 31, 32 and 112, 116, there is a slowing down of the movable fulcrums 35 and 115. This reduction is due to the fact that when the broken lever at high power straightens up, it pushes down the pivots 35 and 115 near the limit of travel, and it is a natural characteristic of the broken levers to slow down and to push harder as they approach the righting limit. This slowing down reduces the speed of the ironing head 17 when

  <Desc / Clms Page number 51>

 it approaches the bock so that it comes under final pressure (Figures 4 to 5) without impact on the padding.



   It will also be observed that the latter part of the downward movement of the speed regulating piston 146 is similarly slowed down and no longer withstands the force of the motor 50 so that the latter provides a high final pressure at the same time. head 17 without encountering resistance from piston 146 of the hydraulic speed regulator. This becomes clear when it is understood that the oil escapes freely from the speed regulator cylinder 147 without offering resistance to the movement of the plunger for any speed of the latter less than the speed at which it is regulated by the valve stem 48. .



   During the reverse operation, when the ironing head moves upward, the hydraulic regulator shaft 134 rotates counterclockwise. As a result, the speed regulating piston 146 moves upward, while the shock absorber piston 141 descends to now perform its damping work.



   In general operation, after pressing the manual control buttons 69, 70 the air passes into the cylinder 50 through the main valve 67 and the pipe 55, and through the action of the piston 52, the control lever 25 Switches from edge to rear around fulcrum 36, thus starting head 17 and moving it by a high lever arm ratio system all along its forward and downward arc path. low, to close the press beforehand or to bring the head against the press and pass over the bock 15 or the padding 16 thereof.

   The high ratio lever system consists of the short arm of the lever between the pivot 54 and the fulcrum 35 and the long arm is represented by a line joining the fulcrum 35 to the fulcrum 27,

  <Desc / Clms Page number 52>

 lever 25 being what may be called, for convenience, a floating lever resting on the end of its short arm.



  When the force is applied to the lower end of the lever 25, the latter tilts backwards, and the fulcrum 35 moves. Since the head moves in the course downwards and the front of its arc of movement the fulcrum of the lever is moved downwards and slightly backwards under the action of the piston. . During this movement illustrated in Figures 2, 3 and 4, the connecting rods 31 and 32 of the broken lever are held bent, or are held against the straightening until the press head comes into contact with the bock 12 and is subjected to resistance, as shown in FIG. 4, and the fulcrum 35 moves downwards while the broken lever remains folded.

   As force continues to be applied to lever 25 to move it rearward, that lever now oscillates around pivot 27, and in that movement the variator now straightens broken lever 31-32 to apply pressure. effort by a system of levers with reduced ratio, pulling the. lever 25 rectilinearly downwards like a traction rod, and therefore, by pulling the head 17 rectilinearly downwards into the final pressing position against the padding 16 of the lower bock 15, the mechanism automatically shifting from the high ratio lever system to low ratio lever system, easily and without shock, due to the broken lever arrangement. The variator 41 operates to keep the broken lever connecting rods folded during preliminary closing.



   In the form shown in Figures 1 to 6 inclusive, this variator, or broken lever regulator 41 is controlled in its movement by a connecting rod device. The latter is the device of the connecting rods 43 and 45, and these connecting rods

  <Desc / Clms Page number 53>

 are arranged to produce a resultant similar to the cam groove of Figure 8.

   The shape of the cam groove 60 in Figure 8 is therefore such that it initially maintains the fulcrum 35 against the free rearward movement, while the lever is free to swing rearwardly around the point. support, but allows the fulcrum to move downward when the press head tilts from its open position to its position: forward and down, from its arc, into the closed position preliminary without pressure, and then, then, forces the fulcrum 35 downwards as the lever 25 rotates around its upper pivot 27, and thence causes the lever 25 to act as a pull rod and move the lever. repeater head in the short vertical high pressure part of its movement.

   The connecting rods 31, 32 of the broken lever perform the same resulting movement as the cam groove of figure 8. The cam groove 119, figures 12 and 13, performs the same movement of the variator 118 as the connecting rod 41 and the lever. 45 of Figure 1, to control the recovery of the broken lever.



   To open the. press, the click 99 is actuated to release the air from below the diaphragm 98 and thereby allow the main valve to close the air line 68 and open the tubing 55 to release air from the cylinder, so that the press - is labre to open under the action of the opposing springs which replace the control mechanism in its starting position.



   This invention is presented to fulfill a need for improvement in textile ironing presses. it is understood that various modifications in its structure, as well as changes in its mode of operation, assembly and instructions for use may occur.

  <Desc / Clms Page number 54>

 to those familiar with this art, and will often be introduced, especially after they have benefited from the teachings of this invention. Therefore, it should be understood that this description is illustrative of the preferred means for carrying out the invention in its usual form, explaining their construction, operation and advantages.



   Claims.

** ATTENTION ** end of DESC field can contain start of CLMS **.


    

Claims (1)

--------------------------- l.- Ironing press for textile articles., with mechanical action comprising a frame, a padded bock and a press head adapted to move high above the bock and to close against the latter, a system of low power levers permanently connected to the press head to tilt it in its long movement relative to the bock, a system of high power levers fixed on an oscillating shaft journaled in the frame, the system of low power levers having its fulcrum between its ends on the system of high power levers, the latter moving freely with the low power lever system during the long head movement, and a simple control means mechanically connected between the frame and the low power lever system, acting directly on the latter to initially tilt the press head from its wide opening position onto the bock, and indirectly on the high power lever system to place the latter out of its free movement position in a pressure position to exert a great force against the system of levers at low power thus applying the final high pressure on the padded tank, in -combination with a hydraulic regulator fixed to the frame, and actuated by the oscillating shaft. <Desc / Clms Page number 55> 2.- Variable motion transmission device for a machine having an opening and closing movement, comprising a frame and a work transmitting element movable inside this frame, comprising a lever, one end of which is permanently connected to the working transmitting element and the other end connected to an energy-producing element, and a means with a movable fulcrum fixed on an oscillating shaft journaled in the frame and articulated with ¯le lever between its ends, whereby, at the start of the closing movement, the movable fulcrum means acts on the lever to modify the force exerted on the work transmitting element, when the latter moves with respect to the frame, and the energy producing means thus initially impart high speed and low force to the moving work transmitting member and gradually reduce the speed by increasing the force during the closing movement until, at the end of this closing movement, the work transmitting element moves with great force under the action of the mobile fulcrum means which transmits all the effort of the energy producer to the work transmitting element, in combination with a hydraulic regulator placed on the frame and actuated by the oscillating shaft. 3. - In a clothes or laundry press, the combination of a frame, a fixed bock mounted on the frame, a press head mounted to move when approaching or moving away from the block in a downward and forward arcuate path with the vertical portion of the arc extending approximately at right angles to the pressing surface of the bock, means for supporting and guiding the head in its movement, a control mechanism comprising a hinged vertical lift. at its upper end on these <Desc / Clms Page number 56> head-carrying means, this lever having a fulcrum close to its lower end arranged to allow the lever to oscillate around its fulcrum and to move downwards during closing in an arc of a circle. the press head, a primary motor connected to the lower part of the lever, means for limiting the rearward movement of the fulcrum during the rearward oscillation of the lower end of the lever comprising broken lever links articulated to each other and respectively to the frame and to the fulcrum, and means actuated by the rocking movement of the lever to keep the broken lever rods folded or to straighten them only when the head press reaches the vertical part of its arc of movement, these broken levers and this fulcrum being arranged to straighten towards a vertical line cutting the articulated connection between the upper end of the control lever and the head-port means. 4. - In combination in a garment or laundry press, a frame, a fixed bock mounted on the frame, a movable press head from and to the bock, in an arched path forwards and downwards. low, with a vertical portion of the arch extending approximately at right angles to the pressing face of the bock, a head support arm hinged to the frame at the rear of the bock, a control mechanism including a vertical lever hinged to the bottom bfas head holder between the pivot of the latter and the head, the lever having a movable fulcrum close to its lower end and arranged to allow tilting from front to rear of the lever around the axis of the point support during the opening and closing movement of the press, a primary motor connected to the lower part of the lever in order to tilt the latter around its point of support, means operating the control of the translation from the point of support towards the <Desc / Clms Page number 57> down during the rocking movement towards the rear beyond the lower part of the lever comprising split lever rods articulated on each other and respectively to the frame and to the lever at its fulcrum, the connecting rods of broken lever being folded back when the press is open, and means operated by the rocking movement of the successively broken lever to keep the connecting rods folded up until the press head reaches the vertical part of its arc. movement then to straighten them, the pivot points of the lever on the head support arm, of the arm to the frame, and of the broken lever link to the frame being placed, when the press is closed, approximately in an orbit intersecting the intermediate part of the head and the bock. 5. - In combination in a clothes rack or laundromat, a frame, a fixed bock mounted on the frame, a press head movable from and to the bock following an arcuate path downward and forward with the vertical part of the arc extending approximately at right angles to the pressing surface. .of the bock, a head-carrying arm articulated to the frame at the rear of the bock, a control mechanism comprising a vertical lever articulated to the head-carrying arm between the pivot of the latter and the head, the lever having a fulcrum close to its lower end and arranged to allow the lever to oscillate from front to back about the axis of the fulcrum during the opening or closing movement of the press, a primary motor connected to the lower part of the lever to cause the latter to swing around its fulcrum, means acting to control the movement of the fulcrum downward during the backward tilting movement from the lower end of the lever comprising broken lever rods articulated on each other and respectively on the frame and the lever at the fulcrum of the latter, the lever rods <Desc / Clms Page number 58> broken being folded when the press is open, and means actuated by the rocking movement of the lever for successively maintaining the folded connecting rods until the press head reaches the vertical part of its arc of movement and then for them. straighten the joints of the lever and the press-holder arm, of the arm and the frame and the broken lever to the frame being placed when the press is closed approximately in an orbit intersecting the intermediate part of the head and the bock, the joints of the broken lever to the frame, and to the lever at the point of the support of the latter being movable approximately in a straight vertical line passing through the point of articulation between the lever and the head support arm when the press is closed. 6. - In a clothes and laundry press, the combination of a frame, a fixed bock mounted on the frame, a press head mounted to move to and from the bock in a downward arc path and forward with a vertical portion of the arch extending approximately at right angles to the press face. bock, des. means for supporting and guiding the head in its movement, a control mechanism comprising a vertical lever articulated at its upper end to this head-carrying means, the lever having a fulcrum close to its lower end arranged to allow the tilting of the lever around its fulcrum and its downward translation during the arched closure of the press head a primary motor connected to the lower part of the lever, means for limiting the rearward translation of the point d 'support during the tilting towards the rear of the lower part of the lever, comprising broken lever links, articulated to each other and respectively to the frame and to the fulcrum, a guide arm integral with one of the connecting rods and movement variation connections between the guide arm and the frame to control the movement <Desc / Clms Page number 59> connecting rods relative to each other and to delay and perform the recovery of the broken lever relative to the closing movement of the press by the lever. 7.- In a garment or laundry press, the combination of a frame, a fixed bock mounted on the frame, a press head mounted to move to and from the bock in a downward arc path and towards the front with a vertical part of the arc extending approximately at right angles (on the pressing face of the bock, means for carrying and guiding the head in its movement, a control mechanism comprising a lever vertical articulated at its upper end on this head-holder means, the lever having a fulcrum close to its lower end arranged to allow the lever to tilt around its fulcrum and its translation downward during the arched closure. of the press head, a primary motor connected to the lower part of the lever, means for limiting the rearward translation of the point, bearing during the rearward tilting of the lower part of the lever, comprising broken lever rods articulated to one another and respectively to the frame and at the support point, a guide arm integral with one of the connecting rods and the movement variation connections between the guide arm and the frame comprising a connecting rod articulated at one end to the guide arm and at the other to a point fixed relative to the frame, the connecting rod extending at an angle relative to the longitudinal dimension of the guide arm. 8.- In a garment and laundry press, the combination of a frame, a fixed bock mounted on the frame, a press head mounted so as to move from and to the bock in an arcuate path towards the down and forward, with the vertical portion of the arch extending approximately at right angles to the pressing face of the <Desc / Clms Page number 60> bock, means for supporting and guiding the head in its movement, a control mechanism comprising a vertical lever articulated at its upper end to these head-carrying means, the lever having a fulcrum near its end lower arranged in such a way as to allow the lever to tilt around its fulcrum and its translation downwards during the arched closing of the press head, a primary motor connected to the lower part of the lever, means for limiting the rearward movement of the fulcrum during the rearward tilting of the lower end of the lever comprising broken lever links articulated to each other and respectively to the frame and to the fulcrum, a guide arm integral with one of the connecting rods, and movement variation connections between the guide arm and the frame, comprising a cam profile and a follower cooperating with the latter, one being fixed relative to the frame and the other being mounted on the guide arm. 9. - In a clothes and laundry press comprising: - a frame, a fixed hock mounted on the frame, a press head movable from and to the bock following an arcuate trajectory downwards and towards the front with a part vertical path extending approximately at right angles to the pressing face of the bock, and means for supporting and guiding the head in its movement, the combination of a control mechanism comprising a vertical lever articulated at its part superior to the head-carrying means, a fulcrum for the lever spaced from the fulcrum disposed to permit the front to rear oscillation of the lever around the fulcrum, whereby the lever moves from side to side. front to back around the fulcrum, a primary motor connected to the lever at a point spaced from the fulcrum and the pivot of the <Desc / Clms Page number 61> lever and acting on it to move the lever around its fulcrum and cause it to swing around its pivot, a fulcrum guide means cooperating with the fulcrum to successively cause the lever to move around of its fulcrum while closing the press and guiding the fulcrum. in its forward-to-backward and downward trajectory, then the swing of the lever around the pivot at its upper end and the. traxting the lever down so that it acts as a draw rod during the final closing movement, and transforming the backward swinging motion of the lever into a downward pulling rod movement. 10.- In a clothes and laundry press comprising a frame, a fixed bock mounted on the frame, a press head movable from and to the next bock & netrajec- tory arched down and forward, with the vertical part of the trajectory extending approximately at right angles to the pressing face of the bock and means for supporting and guiding the head in its movement, the combination of a control mechanism comprising a vertical lever articulated at its upper end on the head-holder means, a fulcrum for the lever spaced from the pivot and arranged to allow the front to back oscillation of the lever around the point (: support, whereby the lever moves to the had and rearwardly around its fulcrum, a primary motor. re ied to the lever at a point spaced from the fulcrum and the pivot of the lever and acting on the latter to cause it to swing around its fulcrum and around the pivot of its upper end, a guide means of fulcrum that can be punched with the fulcrum and can be actuated during the closing of the press to successively cause rotation <Desc / Clms Page number 62> lever around its fulcrum and act as a lever again, and guiding the fulcrum on its path from front to back and down, then the oscillation of the lever around the pivot at its upper part, forcing the fulcrum downwards and causing this lever to act as a traction rod during the oscillation of the lever around the articulation of its end upper during the final closing of the press. II.- In a garment and laundry press comprising a frame, a fixed bock placed on this frame, a press head movable from and to the bock in an arcuate path downward and forward, with a vertical part of the path extending approximately at right angles to the pressing face of the bock, and means for supporting and guiding the head in its movement, the combination of a control mechanism comprising a vertical lever articulated at its upper end by means of the head-holder, a point of support for the lever at a point spaced from the pivot of the latter and arranged to allow the lever to swing back and forth around the point of support, thanks to what the lever moves forward and backward around its fulcrum, a primary motor connected to the lever at a point spaced from the fulcrum and the articulated end of the lever, a fulcrum guide means cooperating with the fulcrum to successively force the lever to move around its fulcrum during the closing of the press from its open position to the pre-closed position and to transform the backward rocking movement of the lever into a downward pulling rod movement during the final movement closure, this means comprising broken lever rods articulated to each other and respectively to the frame and to the fulcrum, and a mechanism operated by <Desc / Clms Page number 63> the rocking movement of the lever by the primary motor and cooperating with the broken lever rods to keep them folded weighing the initial closing movement of the press and to cause it to straighten and thus force the lever to act as a pull rod when the press head reaches the vertical part of its arc of movement. 12.- In a garment and laundry press comprising a frame, a fixed bock mounted on the frame, a press head movable from and to the bock following an arcuate path forward and downward with the vertical part of the trajectory approximately at right angles to the pressing face of the bottle, and means for supporting and guiding it. head in its movement, the combination of a control mechanism comprising a vertical lever articulated at its upper end on the head-carrying means, a fulcrum for this lever close to its lower end and arranged for allow the oscillation of the lever from front to rear around the fulcrum, a primary motor connected to the lower part of the lever, fulcrum guide means cooperating with the fulcrum to successively force the lever to move around its fulcrum while closing the press from its open position to its pre-closed position and to transform the backward rocking motion of the lever into a downward connecting rod motion of traction during the final closing of the press, average cases comprising a cam profile having a vertical portion, and an angularly inclined portion starting from. the lower end of the vertical part, the fulcrum having a follower cooperating with the cam and movable along the vertical part during the movement of the lever around its fulcrum and in the angularly inclined cam part during the operation of the lever as a traction rod. Minister, With respect to Patent No.482,966 of June 7, 1948 which was granted in the name of the company: THE PROSPERITY COMPANY, INC. as an import patent based on UK Patent No. 503,839 of October 8, 1937, we have the honor to inform you that there is a corresponding US Patent No. 2,326,015 and dated August 3, 1943 from such that this Belgian patent will not expire until August 3, 1960, the normal expiration date of said US patent. We kindly ask you to attach this letter to the patent file so that it is brought to the attention of third parties and for this purpose we enclose ffs. 15, - in revenue stamps. Pending receipt of your acknowledgment of receipt, please accept, Mr. Minister, the assurance of our highest consideration. <Desc / Clms Page number 65> Minister,, We have the honor to bring to your attention that it exists at. patent n.482,966 dated June 7, 1948 in the name of THE PROSPERITY C INC. for "Press for ironing articles in textile materials, introduced as an importation of English patents ns 503,839 of October 8, 1937 and American ns 2,326,015 of August 3, 1943, a corresponding French patent n 962,523 of February 28, 1948 (regulator patent of duration). We kindly ask you to attach this letter to the patent file and we thank you in advance. Please accept, Sir, the assurance of our highest consideration.