BE539927A - - Google Patents

Description

       

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  "CUTTING PRESS"

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The present invention relates to machines serving to cut, using a die, sheets of paper or other material arranged in the form of a stack, these machines pushing the die to be placed towards the stack of sheets. .



   In the old technique, such a machine consists of a standard die-cutting press, which comprises a slide, or head, driven by a continuous reciprocating movement and driven by a shaft carrying a heavy flywheel. The operator places the stack of sheets on the cutting board, places the matrix on the stack in the desired position, then pushes the board, with the stack and the matrix that it supports, under the slide, for that it is in the upper part of its stroke, so that the die is driven through the stack of sheets by the slider during the descending phase of its stroke.

   The operator then exits from below the grout. bucket the cutting board, with the stack of sheets and the die, when the slider moves upwards away from the stack, and before it descends a second time. The operation is repeated after a short time interval, which depends on the time required for the operator to remove and arrange the cut blanks, as well as to re-place the die on the stack of sheets.



   This process of moving the cutting board by hand is painful for the operator and requires from him a great regularity of movements involving great skill. The operator must take care to place the die under the slide at the correct

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 moment. He must also take care to place the entire die under the slide, because the die risks breaking if it is only partially under the slide.

   This method also has another drawback, namely the danger to which the operator is exposed; this one must be in fact extremely careful not to get his fingers caught under the cutting head when pushing the cutting board and the stack of sheets up to the cutting position., It is also common, when all that remains of the stack of sheets is debris, to be carried back, out of the machine and across to the cutting table. During this operation, the operator must still be very careful to avoid being injured in the hands by the slider.



   It has been proposed to modify the previous process by giving up continuous operation of the slider and by providing a mechanical system allowing the operator, when he has correctly arranged the cutting board, the stack of sheets and the matrix, to trigger a mechanically controlled operating cycle, in which first the plane. che is drawn towards the interior of the machine to bring the die under the slide, the latter then descending and then rising before the cutting board is erased. In a device of this kind, a constantly rotating flywheel is arranged so as to be connected from time to time to a clutch intended to actuate the slide, which is normally at rest.

   As it takes a great deal of power to pass the die through the sheets, the clutch must be able to withstand very great forces, and the parts of the machine are therefore massive.

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 ves and exposed to rapid wear. Such a machine is often broken down.



   In US Pat. No. 2,259,320, filed October 18, 1939, an improvement to the machine just described was proposed; the die-cutting press described in this patent comprises a flywheel mechanism, for permanently actuating the slide, in combination with a mechanically actuated mechanism for controlling the cutting board, the latter mechanism being normally capable of being operated. made active at the will of the operator and being so arranged that, when it has been so made active, it performs a single operating cycle of the board in a mechanically synchronized manner with the operating cycle of the ram .



   This arrangement, although constituting an improvement of the preceding machines, does not eliminate the danger which arises when the operator removes the debris during the reciprocating movement of the slide; in addition, it has the drawback of requiring constant supply of the maximum operating power, both during empty strokes and during active strokes of the slide.



   None of the mechanisms mentioned above allow the amplitude of the slide stroke to be adjusted.



   Finally, in the patent application filed in the United States of America on May 8, 1949 under No. 126,187, a die-cutting press has been described in which the slide is actuated directly by hydraulic means. In this press, the slide and the cutting board are normally all

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 two at rest, but are actuated every second synchronism with respect to each other. When the operator a. correctly placed the stack of sheets of paper and the die on the cutting board, it activates an electrical contact to trigger a movement of the: Cutting blank towards the interior of the machine.

   The board therefore moves inward and then comes to a stop, but it triggers a distributor, before stopping, to control the movement of the slide downwards under the action of. hydraulic means. When the slider comes near the lower end of its downstroke te, it triggers a reverser, which applied hydraulic power to return the slider. to its upper position and stop it in that position. When it moves upwards, the slider controls a movement of the cutting board towards the outside. The latter therefore moves towards the outside until: its initial position, in which it comes to a stop.

   This machine has proven to be a considerable advance over older machines. However, various characteristics of this machine have been further improved, and it is these improvements which form the subject of the present invention.



   An important feature of the invention relates to a novel device for connecting the control piston rods of the slide, in order to actuate the latter. In the machine described in the aforementioned patent application, the upper and lower pistons actuate the slide by means of piston rods, which pass upwards through the heads of the upper cylinders.

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 to be connected directly to the slide. In this arrangement, the oil tends to escape from the upper cylinders; on the other hand, dust and foreign bodies can be deposited on the piston rods, which enter and exit the upper cylinders during operation.



   This drawback is avoided, thanks to the present invention, by using beautiful, which are arranged outside the open ends, upper and lower cylinders, and by connecting the free ends of these connecting rods to a common mechanism of slider control. A characteristic point is that the common slider control mechanism allows relative vertical overlap of the piston rods, which reduces the overall height of the machine.



   Another important feature of the invention is an improved equalizer mechanism. In the machine according to the aforementioned patent application, two piston rods extending upwards from the cylinders are connected directly to the slide, halfway between the front edge and the rear edge thereof, and front and rear equalizers are provided to keep the front and rear edges of the slider constantly horizontal; these equalizers include four corner columns, which serve exclusively as equalization and guide members. This involves the use of a large number of parts and makes it necessary to fully apply the force of the longitudinal equalization on the spacers connecting the columns and the piston rods on the one hand, and the slide on the other hand. .

   The columns are only braced at the upper ends by the in-

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 intermediary of the slide itself. The piston rods work in high pressure cylinders containing oil; they can have a detrimental effect on the oil seals and the pistons ,. if they are subjected to the stresses resulting from the equalization.



   According to the invention, the four columns are used both for transverse equalization and for controlling the slide. The pistons located on the opposite sides of the machine are rigidly connected to two conjoined columns by the intermediary of massive blocks forming spacers, which define, with the columns and the slide itself, on the sides opposite of the machine, rigid rectangles providing longitudinal equalization.



   According to another characteristic, the invention. tion realizes a new combination of the elements of the frame and the table with the guide sleeves provided for the control rods of the slide. These sleeves are carried by the table, the latter rests on side panels, and the sleeves constitute a means of connection between these panels and the table. In addition, the upper cylinders and lower cylinders are all fixed to the table. In this way, the need for a heavy and stiff bottom plate to withstand the thrust and pull of the cylinders and pistons is eliminated.



   There is also a simplified and improved control mechanism for the clutch operating the cutting board.



   Furthermore, an important arrangement consists in providing an improved control mechanism for the switch intended to trigger the movement.

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 the cutting board to the outside. In a practical and advantageous embodiment, a cam driven by the slider is frictionally driven and controlled to act in the same interval and the same fraction of the upstroke of the slider regardless of the variations. limits, upper or lower, and the amplitude of this course.

   According to another feature, the cam and the conjugate member are arranged so as to pass 1! One over the other without producing any effect during the downward travel of the slide, but to actuate the switch on the contrary. during the upward stroke of the slide.



   In general, the invention proposes to simplify and improve the arrangement of the machine with a view to achieving a simple, light, compact, robust, well-adapted and high-efficiency construction, and also to improve in their details the different mechanisms.



   Other characteristics and advantages will become apparent during the description which follows.



   In the accompanying drawing, given by way of example only: FIG. 1 is a side elevational view, partially cut away, certain parts being omitted, of a cutting press according to the invention; FIG. 2 is a front elevational view of the press of FIG. 1, some parts broken away and some others omitted; FIG. 3 is a partial view, in front elevation, of a clutch mechanism used for driving the cutting board;

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 FIG. 4 is a partial cross-sectional view, taken along line 4-4 of FIG. 1, viewed in the direction of the arrows, some parts being omitted;

   - Figure 5 is a partial and horizontal section taken substantially along the line 5-5 of Figure 4; FIG. 6 is a partial rear elevational view of the machine, some parts being omitted; FIG. 7 is a partial section, vertical and longitudinal, taken on the line 7-7 of FIG. 5; - Figure 8 is a vertical and longitudinal section taken along the line $ - $. of Figure 9; - Figure 9 is a vertical and transverse section taken along the line 9-9 of Figure
8; - Figure 10 is a partial sectional view of a detail along the line 10-10 of Figure 8;

   FIG. 11 is a vertical and longitudinal section taken along line 11-11 of FIG. 5, this figure being drawn on a scale much larger than the preceding figures; FIG. 12 is a vertical and longitudinal section taken along line 12-12 of FIG. 5, the scale being the same as in FIG. 11; - Figure 13 is a sectional view of a detail taken along line 13-13 of Figure 12; FIG. 14 is a partial view of a detail in elevation, certain parts being cut away with partial section on the line 14-14 of FIG. 13;

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   - Figure 15 is a sectional section taken along line 15-15 of Figure 12;

   - Figure 16 is a partial view, partly in elevation and partly in section, of the upper part of the front end of the navy, the section being taken along line 16-16 of Figure 18; FIG. 17 is a partial and complementary view of FIG. 161 against the lower front part of the closed enclosure surrounding the motor and the front closure plate of this enclosure; \. Fig. 18 is a partial front elevational view with some parts in section;

   - Figure 19 is a partial plan view of the table stroke adjustment mechanism, this
Mechanism being shown in particular in Figure 18; FIG. 20 is a perspective view of a cam carriage with a control handle shown elsewhere in FIG. 19; - Its figure 21 is a detail section taken on the line 21-21 of figure 7; - figure 22 is a fragmentary plan view of the parts shown in figure 231 - figure 23 is a partial section, lengthwise and vertically, taken along the line 23-23 of figure 22;

   Figure 24 is a partial vertical and cross section taken on line 24-24 of Figure 23; FIG. 25 is a partial section, longitudinal and vertical, taken along line 25-25 of FIG. 24; - Figure 26 is a partial section, ion,

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 gitudinal and vertical, taken along line 26-26 of figure 27; - Figure 27 is a horizontal view of the parts shown in Figure 26, the table being shown in phantom; FIG. 28 is a partial front elevational view showing the upper left part of the machine, the mechanism being cut away towards the middle of its height to make the figure more compact;

   - Figure 28a is a detail section taken along the line 28a-28a of Figure 28; FIG. 29 is a partial side elevational view showing the part of the machine already shown in FIG. 28; FIG. 30 is a partial detail view, in side elevation, of the parts shown in FIG. 29, its scale being larger than that of FIG. 29; FIG. 31 is a partial view, in front elevation, with a partial section taken on the line 31-31 of FIG. 30; FIG. 32 is an exploded view of the lower parts shown in FIG. 31; - Figure 33 is a horizontal section taken on line 33-33 of Figure 29;

   FIG. 34 is a partial cross section, transverse and vertical, taken substantially along the line 34-34 of FIG. 37, certain parts being broken away; this figure represents a control box and certain associated parts; - Figure 35 is a partial section taken on line 35-35 of Figure 34;

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   - Figure 36 is a partial and horizontal section taken on line 36-36 of Figure
34; FIG. 37 is a partial longitudinal and vertical section taken on line 37-37 of FIG. 34; FIG. 38 is a schematic view showing the hydraulic system and the associated parts; FIGS. 39 and 40 are detailed diagrammatic views showing some of the parts of FIG. 38;

   FIG. 41 is a diagram of the electrical installation showing certain parts combined with the latter.



   The die cutting press shown comprises side and vertical panels 10 (Figures 1, 2, 5,8 and 10), which are connected to each other at their lower end by cross members 12 and 14, at their upper end by a table 16 and by other parts which will be described later. Table 16 constitutes a support for a die board. sliding cutter 18, this support enabling the board 18 to resist the pressure of a reciprocating slide 20, during the cutting operation.



   We will begin by briefly explaining the general principle of the mechanism shown (which is the same as that described in patent application No. 126,187 cited above by reference), under focusing on the details, so as to facilitate understanding. of the following description.



   The cutting board 18 normally occupies a retracted or recessed position, shown in FIG.

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 Figure 1, and supports a stack 24 of sheets of paper from which blanks are to be cut by means of a cutting die 26. All parts are normally at rest, except a worm 28 (Figures 4, 5 and 7 ) which forms a part of a clutch 30 and which is constantly driven by a motor 32 ..



   When you have correctly placed the matrix 26 on the! Stack. 24, and when you want to perform a cutting operation, you actuate a switch handle. 34. An electromagnet is thus energized, which activates the clutch 30 for a half-turn of rotation; as a result, the cutting board 18 is dragged rearward a distance approximately half its length, and then comes to rest.



   In the last part of this backward movement of the plank 18, a distributor is actuated which causes the admission of a liquid under pressure into the upper cylinders 36 (Figures 1 and 2) of a system. hydraulic so as to drive down the slider 20. This downward movement of the slider 20 occurs when the cutting board 18 is at rest and has the effect of passing the die 26 through the stack 24. This downward movement of the slider 20 also serves, at the time of its completion, to actuate the hydraulic distributor, so as to introduce the liquid under pressure into the lower cylinders 38 and to expel it from the upper cylinders 36. .

   The direction of movement of the slider 20 is thus automatically reversed and the slider therefore returns to its normal position shown in FIG. 1.

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   When the slide moves upwards, it again causes the clutch to release.
30 for controlling the cutting board, and this clutch thus turns the control mechanism for the cutting board by a second half-turn; if, the board returns to its original and normal position shown in FIG. 1. At the end of its ascending course *, the slide 20 comes to a stop automatically so that the different pieces return exactly to their original position and are ready for a second cycle of operation, as soon as the operator has taken delivery of the cut blanks and replaced the die 26 for a new cutting operation.



   In the position of figure 1, the cutting board 18 rests on support bars 40 (figures 4, 7 and 18), which extend forward from the table 16, their upper face being in a horizontal plane parallel to the plane of the face, upper 'of the table. Each bar 40 is fixed by screws 42 on an angle iron 44 which serves as its support.



   The angles 44 have at their rear end tabs 46 folded down, which allow the bars 44 to be fixed by means of screws 48 on the front face of the table.



   Each angle bar 44 comprises a wing 50 directed downwards and extending all the way along the bar; this wing is fixed by rivets 52 on a vertical plate 54. The plates 54 rest on the floor and constitute the side walls of an enclosure in which the motor 32 is housed. The plates 54 also support, concurrently with the table, bars 40. They are reinforced along

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 from their upper edge by angles 44 and along their rear vertical edge by angles 56.



   The reinforcement angles 56 are fixed at their upper end to the table 16 by suitable members, such as rivets 58.



   The cutting board 18 is made of hardwood.



   It is arranged so as to slide on the table and on the bars 40, between lateral guides 59 (Figures 1 and 2), which are fixed to the table by screws 61; these screws, directed vars the bottom, pass through tabs 63 forming an integral part of the guides 59. A bracket 60 (Figures 1,16,18 and 19). is mounted on the board 18 by means of screws 62, which are, screwed towards' back into the board 18. A cap screw 64, extending forward through bracket 60, is threaded into a board control rod 66. This rod is connected at its front end to a coupling device 68, which is adjustably connected to a rod 70 and which will be described a little later.

   The rod
70 extends rearwardly from device 68 and its rear end is connected to a sliding block 72.



   The sliding block 72 can slide along the longitudinal axis of the machine on a horizontal and fixed bar 74. This bar is fixed at its rear end on the front of the table 16. The sliding block 72 is articulated on the front end of a connecting rod 76, the rear end of which is articulated on the free end of a crank 78 mounted on a drive shaft 80 (FIG. 5).



   It is desirable that the stroke of the cutting board control mechanism be short, because in this case it is possible to realize a mechanism

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 of a compact construction and at the same time saving time and energy in the use of the machine. As in 'the demap-. of patent No. 126,186 already cited, the mechanism shown is adapted to impart to the cutting table a stroke equal to substantially half of its length; on the other hand, means are provided for connecting the coupling device 68 to the rod 70, by means of a blot 82 (FIG. 16) which forms part of this device, in one or the other of two possible positions with respect to this rod.

   When one of the coupling positions is achieved, the rear half of the cutting board is driven alternately under the slider 20 and out of reach of the latter; on the contrary, when the other position is actually achieved, it is the front half of the cutting board which is brought alternately under the slide and out of reach of the latter. The same is true in the already cited patent application No. 126,187, but the present machine comprises a coupling device of a new and advantageous construction.



   The new coupling device, intended to selectively achieve the two coupling positions between block 82 and rod 70, is clearly shown in Figures 16, 1c and 19. Rod 66 is connected. , at its front end, to a crossbar 84 by means of a screw 86. The crossbar 84 rests in a groove 88 open on one side and formed in the upper part of the block 82.



  Rod 66 extends into block 82 passing through an open slot 90 which is provided in the upper face of the block. Thanks to this arrangement, the rod

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66 and crossbar 84 are free to move in the vertical direction, relative to block 82; they can act at un.niveau different from that of the block 82, and it is not necessary to fix the bracket 60 on the block at a determined level. This method of construction also makes it possible to lift the rod 66 and the transverse bar 84, out of the machine, with the cutting board, when desired, in particular whenever it is necessary to repair or repair. .replace the board.



   The two coupling positions of the block 82 and of the rod 70 are achieved by front and rear plungers 92 and 94 respectively; these fingers are mounted in bores of the block 82, so as to be able to move vertically. They respectively comprise, at their lower end, eccentric parts 96, 98 of reduced diameter. These parts 96 and 98, or appendages, are designed to fit respectively in bores 100 and 102 formed in the rod 70. In FIG. 16 we see the front finger 92, with its part 96 of reduced diameter engaged in the bore 100 and the finger 94 in the inactive position.



   The fingers 92 and 94 have bores 104 containing coil springs 106 for compression. Each spring 106 pushes the conjugate finger down, the reaction force being supported by a plate 108 fixed to the block 82.



   The bores 100. and 102 of the rod 70 are not aligned with respect to each other in the direction of movement of this rod. This is for the purpose of allowing the fingers 92 and 94 to cooperate selectively with the bores 100 and 102 quton a ex-

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 centered the extensions 96 and 98 of reduced diameter.



  Fingers 92 and 94 have side studs 110 and 112 which extend through slots 114 and 116 of block 82 (Figure 19). The studs 110 and 112 cooperating with the slots 114 and 116 determining the orientation of the fingers 92 and 94 and thus serve to keep the parts 96 and 98 of reduced diameter respectively aligned with the bores 100 and 102, for cooperate with them.



   The free ends of the pins 110 and 112 extend in a transverse passage 118 formed in the upper face of the block 82. A carriage 120 forming a cam is slidably mounted in the passage 118, inside which it is held by the tray 108 forming a cover. The carriage 120 has a handle 122 and a body 124 (Figure 20). Body 124 has two portions 126 and; 128 facing upwards but inclined in the opposite direction, the pins 110 and 112 resting on these portions 126 and 128, which respectively constitute cams.



   As can be seen in FIGS. 16 and 19, the cam 128 maintains the stud 112 in the high position so as to disengage from the rod 70 the appendage 98. The stud 110 is on the contrary located on a lower part of the cam 126 and therefore allows the appendix 96 to engage the bore 100 of the rod 70. With the parts in these positions, the carriage 120 is in the left limit position of its movement (looking at the figure 18). A washer 130 attached to the right end of the carriage 120 (Figure 19) by a screw 132 prevents the latter from moving further to the left.

   The thrust washer 130 extends beyond one of the side limits of the cha-

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 riot 120, to a position where it can be brought into contact with the right face of the block 82 and stopped by it.



   A stop ball 134 (Figure 18), which is seated in a bore 136 of block 82 and which is urged upward by a compression coil spring 138 also housed in this bore, prevents carriage 120 from dying. 'accidentally move away from the position shown. This ball 134 is resiliently applied against a shallow cavity 140, which is formed in the underside of the slide.
120.



   The coupling mode shown makes it possible to impart to the cutting board 18 a reciprocating movement backwards and forwards, so that its rear end successively occupies and leaves the cutting position under the slide.



   To change the coupling mode, such as the front end of the cutting board. ge 18 comes alternately to occupy, then to leave, its cutting position under the slide, the drive shaft 80 is first rotated by half a turn to drive the rod 70 up to the rear limit of its movement and to stop it in this position.



  This movement of the rod 70 drives the cutting board rearward and serves to position the rear half of the board under the slider. The handle 122 of the carriage 120 is then grasped and pushed to the right (FIG. 19) to move the carriage 120 to the right limit of its stroke. The appendage 96 is thus removed from the bore 100 and the appendix 98 is released, which its spring pushes and applies between the rod 70. The carriage 120 is resiliently retained.

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 only in its new position, due to the fact that the stop ball 134 is engaged in a second cavity 142 of the carriage 120.



   The appendage 98 cannot penetrate into the bore 102, because the latter is at this moment quite far behind this appendix. However, by bringing the rod 70 to the front limit of its movement, the bore 102 is moved forward so as to align it with the appendage 98. The latter then instantly engages in the bore 102 ( figure 16), by automatically fixing the block 82 in the new desired position, with respect to the rod 70.



   When it is desired to modify the coupling to restore the positions shown in the drawing, the carriage 120 is first grasped by its handle 122 and it is pushed to the left limit of its movement (FIG. 19). The rod 70 is then moved, independent of the block 82, to the rear limit of its movement, and as a result the appendage 96 clicks and engages the bore 100 to restore them. primitive positions. The rod 70 is then brought back to the left limit of its movement (figure 16), bringing with it the cutting board, so that the original rest position is achieved.



   The coupling device 68 (Figures 16, 18 and 19) is provided with guide rollers 144 with flanges, which are arranged in a rectangle and which overlap marginal and longitudinal parts of the rod 70, so as to guide the latter. -Here when it is moved relative to the device 68 during the coupling change which has just been described.



   Rollers 144 are mounted at the four corners

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 of block 82. They are all identical and it is therefore sufficient to describe only one. Each roller is rotatably mounted on a headless bolt 146 having a flange 148 provided in a middle portion of its length. The upper end of bolt 146 passes up a corner of plate 82 and is secured by nut 150.

   A spacer sleeve 152 is mounted on bolt 146, below collar 148; it comprises at its upper end a flange 154 resting against the collar 148. The roller 144 surrounds the body of the sleeve 152; it can rotate freely between the flange 154 of the sleeve and a washer 156. The latter is firmly tightened against the lower end of the sleeve 152 by a nut 158 screwed onto the lower end of the bolt 146.



   The rod 70 is provided at its rear end with a groove 160 disposed opposite a groove 162 of the sliding block 72. A key 164 is housed in the grooves 160 and 162 to center and secure the rod 70 and the sliding block 72 relative to each other, Screws 166 pass down through rod 70 and screw into block 72.



   The sliding block 72 comprises at its lower end a passage 168 with a square section, in which is slidably mounted a portion 170 with a square section of the support bar 74 forming a guide. A plate 172 extends transversely to the lower open face of the corridor 168 and is fixed by screws 174 on the sliding block 72.



   The slide block 72 is provided with felt wiper strips 176, which are disposed in contact with the faces of the bar 74 for applying lubricant thereto. There are four 176 bands at each end

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 of block 72, each of them being applied against one of the faces of the bar. Each strip 176 is clamped by an angle bar 178. Each angle bar 178 is secured to the block 72 by screws 180.



   The bar 74 has at its rear end a round part 182 (FIG. 7), shoulders 184 being formed at the junction of the square and round parts of this bar. The round part 182 passes through a round hole drilled in the front edge 186 of the table 16.



  The rear end of the round portion 182 passes through a round hole drilled in a tab 188, which extends downward from and forms an integral part of the top of the table. A pin 190 is forcibly engaged upwardly through the round portion 182 of the bar 74, into the tab 188, so as to secure the bar 74. The shoulders 184 thereof bear toward the lug. back against the edge 186 of the table.



   The connecting rod 76 is connected by its front end to the sliding block 72 by means of the plate 172 and by means of a head pin 192 (FIG. 18).



   A flanged bush 194, extending through the forward end of connecting rod 76, surrounds the body of the shaft 192 and rests on the head thereof. The axis 192 is fixed on a boss 196 of the plate 172 by means of: a transverse pin 198.



   The rear end of the connecting rod 76 has a flanged bush 200 (Figures 7 and 18) forcibly inserted through that end. A head screw
202, forming an axis and directed downwards, passes through the pad; it has a threaded end 204 of reduced diameter, which passes through the outer end of the crank 78. A nut 206 is screwed onto

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 this threaded part 204, so as to tighten the crank 78 strongly against a shoulder formed at the lower end of the body of the screw 202.



   The crank 78 has at its inner end a split hub 208 (Figures 5 and 7). Set screws 209 secure hub 208 to drive shaft 80.



   The rod drive mechanism 70 comprises a motor 2, as already indicated. Although the rod 70 is normally at rest, this motor rotates continuously.



   The motor 32 is fixed on support bars.



   212 ending at the back with clevises. Each yoke straddles a stud 214 having the shape of a U and facing backwards, the bar being connected to this stud by an axis 215. Each stud 214 embraces the transverse bar 14 and its arms are clamped on this bar by means of a head screw 216, which crosses the upper arm of the crampon and screws into its lower arm. Each bar 212 carries adjustable feet 218 intended to rest on the floor and to constitute a fixed and horizontal support for the motor 32. Each foot is carried to the lower end of a head screw 220. A lock nut 222 is screwed onto each screw 220.



   On the shaft 224 of the motor 32 (Figures 4, 5 and 7) is wedged a multi-groove pulley 266, which drives, via V-belts 228, another multi-groove pulley 230, attached on the shaft 232 of an endless screw. The shaft 232 is rotatably mounted in bearings 234 fixed by screws 236 on a support 238; this is fixed on a horizontal and transverse plate 240 which is suspended

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 hanged from table 16. Spacer blocks 242 are interposed between the ends of plate 240 and table 16. Fixing screws 244 (Figure 5) pass through plate 240 and blocks 242 upward. screw into the table.



   On the shaft 232 is wedged an endless screw
246, which drives a helical toothed wheel 28.



   This wheel can turn freely on the vertical shaft 80; it is supported on this shaft by means of a pulley or brake drum 248 (FIG. 7), which is fixed on the shaft 80, at the lower end thereof. The shaft 80 extends upwards through the support 238, and on its upper end is fixed the hub 208 of the crank 78. This hub presses you against an upper faxe of the support 238 and supports the shaft. 'shaft so that it can rotate freely in the support.



   The helical gear 28 drives the braking pulley 248 and the shaft 80 through the "half-turn" clutch 30. The clutch 30 is the same, from a construction point of view, as that described. in the aforementioned patent application of the United States of America No. 126,187; it has therefore not been considered useful to represent or describe it in detail here. Reference may be made, if necessary, to the description contained in this patent application.



   The "half-turn" clutch 30 is controlled from an oscillating balance 250 (Figures 3, 4, 5 and 7) by means of two lugs 252 and 254. These two lugs are offset one by one. relative to each other by an arc of 180 centered on the shaft 80 and are mounted so that they can slide vertically in

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 extensions 255 of the support 238. They are controlled by the oscillating balance 250 in such a way that, when one of them is withdrawn into an inactive position (to allow the drive of the shaft. 80 to par - shooting of the helical gear 28, as seen in figure 3), the other is brought into an active position, in which it interrupts the drive of the shaft 80 after half a -tower.



   The balance 250 is wedged on an oscillating shaft 256 supported in a bracket 258 with two arms.



   This console is arranged on a boss 260 of the support 238 and it occupies a fixed position relative to the latter. The balancer 250 includes arms 261 and 263 which extend in diametrically opposed directions from the shaft 256. Each of the two arms 261 'and 263 carries a pin 262 or 264, respectively, the end of which is constantly engaged in a groove 266 formed at the upper end of the control pins 252 and 254. It can easily be seen that, if the pin 262 is lifted by the rocker 250 so as to lift the pin 252 (FIG. 3) the pin 264 is lowered so as to also lower the lug. 254. When the balance wheel moves in the opposite direction, it obviously produces the opposite effect.



   The rocker actuator mechanism 250 includes two solenoid valves 268 and 270 (Figures 5 and 6), which are mounted on a fixed bracket 271; these solenoids are at a certain distance from each other
A and are axially aligned. A common frame 272 is carried on a rod 274 passing through the solenoid 168. This frame is made of a ferromagnetic material; it is arranged between the solenols so as to extend normally inside

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 of each of them. When solenoid 268 is energized, the armature and its rod are driven to the right (looking at Fig. 5), and when solenoid 270 is energized, the armature and rod are driven to the left.



   The rod 274 is connected by a pin 276 to a hurdy-gurdy 278. The latter is articulated, by its other end, via a pin 280, on a crank 282 wedged on the shaft 256, so that the linear motion of rod 274 is transformed into an oscillating motion of shaft 256.



   The parts are normally held elastically in an intermediate position by a centering mechanism 284 (figure 6), which acts on the axis
280. Plungers 286 and 288 slidably mounted in ears 290 of a fixed console 292 are applied on the opposite sides of the axis 280. The console 292 is fixed on the table 16. Each of the plungers 286 and 288 has a collar. 294; it is surrounded by a helical compression spring 296, which bears by its inner end against the mating collar 294 and by its outer end against the mating outer ear 290 of the console 292.



   The role of the centering mechanism is to center the armature 272, relative to the solenoids 268 and 270, so that it can normally be actuated vigorously and quickly by either of the solenoids. . The centering of the armature consequently equalizes the positions of the clutch control lugs 252 and 254. An important point to point out is that when the lugs 252 and 254 are. thus maintained at the same level, their lower extremity

  <Desc / Clms Page number 27>

 The upper part is placed at a level rendering the clutch inactive, and either of them actually maintains the clutch in the disengaged position.



   The slider 20 comprises a head 300 (Figures 1 and 2), which is guided, supported and actuated by four vertical columns 302 (Figures 5,9 and 10).



   Each column 202 extends downwardly through table 16 and passes through vertical guide sleeves.
304. The columns 302 protrude at their lower end, beyond the lower end of the sleeves 304. The lower end portions 306 of these columns 302 are threaded and have a reduced diameter. The two columns to the right of the machine are rigidly connected to one another by means of a massive block forming a spacer 308 (FIGS. 8 and 9). The block 308 is engaged on the lower end portions 306 of reduced diameter of the corresponding columns and it is fixed on these columns by nuts 310. The parts 306 of the columns 302 located to the left of the machine are connected. to each other in an analogous manner.



   The guide sleeves 304 are mounted rigidly on the table 16. Each sleeve has, in a middle section, a flange 312, the general shape of which is rectangular and which bears upwards against the underside of the table. . Upwardly directed head screws 314 pass through this ledge and thread into the table. Each sleeve 304 receives, at its upper and lower ends, flanged sleeves 316 (Figure 8), the metal of which is harder than that of sleeve 304, and which are actually designed to guide column 302 and to absorb the material. wear resulting from the operation of this column. The body

  <Desc / Clms Page number 28>

 of each insert sleeve 316 is introduced into a cavity 318 provided in the sleeve 304.

   Screws 320 pass through the collar of each sleeve 316 and are screwed into the sleeve 304. The upper sleeve 316 has an annular cavity 322 (FIG. 10), in which is housed a washer 324 for wiping and lubricating. A retaining ring 326 covering the washer 324 is fixed by screws 328 on the sleeve 316.



   The sleeves 304 also provide a means for securing the side panels 10 to the table 16.



   Screws 329 pass through bosses 331 of uprights 10 and screw into bosses 333 of sleeves 304 (Figure 5).



   A sliding drive mechanism 20 is provided on each side, that is to say on the right and on the left of the machine. These two drive mechanisms are identical, so that only one need only be described. Energy is supplied by the upper cylinders 36 (Figures 8 and 9), via the spacer blocks 308, to drive the slide
20 down; power is also supplied by the lower cylinders 38, through the same blocks 308, to produce the drive of the slide upward.



   A piston rod 330, the role of which is to drive the slide downwards, projects downwards beyond the lower end of each upper cylinder 36? The rod 330 has a lower end portion 332 (FIG. 9), of reduced diameter, and which engages in a sleeve 334 with a collar. The body of this bushing fits into a bore 336 in block 308. An upwardly directed head screw 340 passes through a flanged bushing 342 and screws into the lower end 332 of the rod.

  <Desc / Clms Page number 29>

 
330. The rod 330 and the screw 340 grip the block 308 by means of the flanges of the sleeves 334 and 342. A shoulder 338 of the rod 330 rests against the collar of the sleeve 334.



   A piston rod 344 (Figures 8 and 9), the role of which is to drive the slide 20 upwards, projects upwards beyond the upper end of each lower cylinder 38. This rod 344 . is connected at its upper end to the body
346 (see also Figure 5) of a caliper 348 by means of a cap screw 350. The caliper body 346 is at a slightly higher level than block 308, but it has arms 352 which extend down to and form an integral part of block 308.



   The upper cylinder 36 includes a sleeve-shaped portion 354 (Figure 11) and a cylinder head portion 356. These two parts are connected to each other by rings 358 and 360, at the same time as by cap screws 362. The ring 358 is slotted and is located in a groove 364 of the sleeve 354. The ring 360 rests upwards against ring 358; it is pushed upwards by the screws 362, the rods of which pass through the ring 360 and screw into the head 356. The previous construction allows to press, in a forceful manner, against the inner face of the head. , the upper end of the sleeve, together with a seal 366 surrounding this end.



   The entire cylinder 36 is supported by table 16, through head 356, at. means of screws 368, which pass downwards through the upper part of the table and are screwed into the head.

  <Desc / Clms Page number 30>

 
The head 356 has a channel 370 terminating in a groove 372. A cap 374 is fixed in the groove 372 and covers the channel 370. This cap has a channel 376, which is located above the channel 370 and communicates with this one. A line 378 attached to the cap 374 serves to supply the pressurized liquid to the cylinder and to evacuate the liquid used therefrom.



   The seal between the head 356 and the cap 374 is produced by means of a washer 380 which surrounds an attached tube 382, short and rigid; this tube holds the washer. Cap 374 is pressed down vigorously and evenly against head 356 by screws 384. These screws are screwed into the top of table 16 and rest against the top face of cap 374; they are fitted with locknuts 386.



   The upper piston 388 includes a head
390, which is screwed onto an upper end portion 392 of the piston rod 330; threaded part 392 has a reduced diameter. A guide and wear ring 394 surrounds the lower part of the head 390; it is fixed on it by screws
396, which pass through a collar 398 of the ring
394, this collar being directed inward.



   On the upper end of the head 390 are assembled successively by engagement on an unthreaded end portion 400 of the rod 330 a flexible lower sealing washer 402 with a collar, a spacer disc 404, a upper flexible sealing washer 406 with flange and a clamping disc 408. These elements are firmly clamped by screws 410, which pass through them towards the

  <Desc / Clms Page number 31>

 low to screw into the head 390. The washers 402 and 406 are provided with attached metal rings 412, which surround the shanks of the screws 410.

   These ba. These inserts are initially somewhat thinner than the mating washers and serve to limit the compression applied thereto.



   The flange of the upper washer 406 faces upwards; is pressed outwards by a cylindrical flange of a flexible metal ring 414. The flange of the lower washer 402 is directed downwards and is pressed outwards by a cylindrical flange d a flexible metallic ring 416. The collar of the washer 406, which is resiliently pressed, serves to hold the oil in the working chamber of the upper cylinder. The flange of the washer 402, elastically pressed and directed downwards, serves to oppose the admission of air into the working space of the cylinder, under certain conditions which may occasionally occur during periods of stress. stop times.



   The lower cylinder 38 includes a sleeve-shaped portion 418 (Figures 12, 13 and 15) which is screwed at its lower end into a head 420. A plate 422 surrounding the sleeve 418 with some clearance is applied towards the head 420 by. screws 424. It rests against a seal 426, which occupies a groove formed between it and the head 420.



   One end of a pipe 432 is fixed inside a block 428, itself fixed to the head 420 by screws 430; the pressurized liquid arriving through this pipe is brought to the working chamber

  <Desc / Clms Page number 32>

 cylinder 38 and the liquid used is also discharged through this line. Line 432 communicates with the cylinder through aligned channels 434 and 436 formed in block 428 and head 420, respectively.



   The cylinder 38 is supported by the table, by means of a structure comprising rods: suspended 438 '(see also Figures 8 and 9).



  Each rod 438 has an upper end portion 440, of reduced diameter, which is threaded and screws into the table 16. A block 442 rests against the lower ends of the rods 438. It is clamped thereon. by screws 444, which pass through the block upwards and screw into the lower ends of the rods. These screws pass through bores 446 in the block, the diameter of these bores being considerably larger than that of these screws. There are three angularly equidistant screws 448 associated with each bore 446. These screws are threaded through the block and extend radially inside the corresponding bore 446. This has been given a large diameter to avoid too tight manufacturing tolerances.

   When the parts are assembled, screws 448 are set on the corresponding screw shank, in "a defined position, which is not necessarily concentric with the bore.



   Sleeve 418 passes through block 442 and has a shoulder 450, which faces upward and abuts a corresponding shoulder of the block.



  This sleeve is pushed, relative to the block, by rings 452, 454 and by screws 456, so as to force these two shoulders against each other. Ring 452 is a split ring which is housed in a groove 458 of the sleeve. The screws 456, directed

  <Desc / Clms Page number 33>

 upwards, pass through ring 454 and screw into block 442.



   The lower piston 460 includes a socket head 462. The piston rod 344 has a threaded end portion 464 of reduced diameter; this downwardly facing portion 464 passes through the center of the head 462. A flanged sealing washer 466 and a clamping disc 468 are engaged, below the head, on the end portion 464 of the head. the piston rod. Washer 466 surrounds an intermediate diameter portion 470 of the piston rod, while disc 468 surrounds narrower threaded portion 464 and bears upwardly against a shoulder formed at the junction of portions 464 and 470. The disc 468 is energetically pressed upwards, against this shoulder, by a nut 472 screwed onto the lower end of the portion 464 of reduced diameter.

   The rod portion 470 projects beyond the head 462 over a length slightly less than the thickness of the washer 466, and it thus serves to limit the compression of this washer by limiting the upward movement of the disc 468. .



   The large diameter portion of the piston rod 344 has a groove 474 in which a sealing ring 476 is housed.



   During operation, some oil leakage inevitably occurs along the piston 388 of the upper cylinder (Figure 11). An annular drip cup 475 is provided at the lower end of the sleeve 354. This cup is secured to the sleeve by a band 477, which extends all around the sleeve and the bowl overlapping them. Band 477 includes nipples 479 that fit into

  <Desc / Clms Page number 34>

 holes provided on the circumferential surface of the drip pan. Band 477 is provided at its opposite ends with perforated ears 481. The shank of a bolt 483 passes through the ears 481.



    , A tightening nut 485 screwed on, this rod holds the parts together and presses the ears towards each other so as to firmly tighten the band on the sleeve and the cup.



   The bowl 475 has on one side (see also Figure 14) a drain port 487 through which the collected oil flows. A guide plate 489 disposed below the orifice
487 leads the oil into an arinular channel 491, which is defined by block 442 and by the upper end of the sleeve 41 $ of the lower cylinder 38. The ridge 491 includes a deep portion 493, which communicates by a bore 495 with a tube 497 terminating in the reservoir 494. The tube 497 is fixed to a block 499 mounted by means of screws 501 on the block 442 (FIG. 13).



   The admission of oil to the upper and lower cylinders 36 and 38 and the discharge of the oil from these cylinders is controlled by a distributor 480 (FIG. 38). This dispenser may advantageously be identical, in all respects, to the corresponding dispenser described in United States Patent Application No. 126,187 already mentioned; we will refer to this request for detailed explanations of this dispenser. The distributor 480 comprises a housing 482 and a spool 483 disposed in this housing and actuated by a rod 484. This rod normally maintains the spool in a neutral position, so that pressurized oil is neither supplied to the upper cylinders 36, nor

  <Desc / Clms Page number 35>

 to the lower cylinders 38.



   When the rod 484 is moved upward from the position shown in Figure 38, a pressurized fluid supply line 486 is communicated through the distributor and a line 488, with the driving
378 which communicates with the upper cylinders 36.



   At the same time, the duct 432 communicating with the lower cylinders 38 is placed in communication, via a duct 490 and the distributor
480, with the discharge conduit 492 leading to a reservoir 494. These communications are maintained throughout the downward stroke of the slide.



   At the end of this stroke, the distributor rod 484 moves downward to reverse the communications. As a result, the pressure supply conduit 486 is placed in communication, through the distributor and the conduit 490 ', with the conduit 432 which communicates with the lower cylinders 38. It also results that the conduit 378 communicating with the upper cylinders 36 is placed in communication with the discharge conduit 492, through the conduit 488 and the distributor 480.



   These communications are maintained throughout the upstroke of the slide. At the end of this stroke, the rod 484 is returned to the neutral position shown in FIG. 38.



   The hydraulic mechanism, which controls the lowering and raising of the slide, is shown as a whole in schematic form in Figure 38. With the exception of a pilot valve 496, which has been added and which will be described in detail a little later, and with some minimal modifications

  <Desc / Clms Page number 36>

 ted to the pressure regulator, the hydraulic mechanism is the same as in the state patent application =
United States of America n 126.187 already mentioned, to which reference may be made for further explanations.



   The hydraulic mechanism consists essentially of a pump 498, which is driven through the intermediary of the shaft 232 from the motor 32 for controlling the cutting board; this pump sucks the oil from the reservoir 494 through a pipe 500 (including a filter 502) and discharges the oil under pressure in the pipe 504:

   The oil is supplied through this conduit to a relief valve 506, which is constructed and controlled to channel the oil directly to the reservoir 494 through a conduit 50 when a predetermined pressure exists in a pressure relief device 510. , but to deliver the oil in this device to accumulate
 EMI36.1
 cumulat & 1i4, / when the pressure therein is infé.JD.ct 'higher than said predetermined value. The device 510 comprises a duct 512 in which is interposed a check valve 513 and on which is mounted a pressure gauge 514. The duct 512 communicates by a duct 516 with a duct 518, which extends in opposite directions from it. of conduit 516.

   One branch of conduit 518 terminates in a pressure accumulator 520, which comprises a metal housing 522 and a deformable bag contained therein and filled with nitrogen (not shown). A valve 524 which can be operated by hand and intended for the emptying of the device is provided in a bypass 526 communicating with the duct 518.



   The second branch of the conduit 518 communicates freely with the pressure supply conduit 486, which terminates at the distributor 480. The conduit 518 extends beyond the conduit 486 and communicates with it.

  <Desc / Clms Page number 37>

 the pilot distributor 496 (see fig & re 39) via a part of the body 528 of this distributor, in a middle portion of this body.



   A bypass 530 from the conduit 518 terminates in a body 532 of a pressure regulator
534 and communicates with the interior of this body via an orifice 536. A piston 538 slidably mounted in the body 532 comprises a channel 540 shown in FIG. 39; this channel places the orifice 536 in communication with the left end of a bore 542 formed in the body. Piston 538 is pushed towards the left end of bore 542 by a compression spring
544.



   An adjusting screw 546 is threaded through the right end of the body 532 and rests via a sliding block 548 against the right end of the spring 544. This spring mounted in the ex - the right end of the bore 542 acts by exerting a controlled pressure, against the pressure of the oil admitted in the left end of the bore, the pressure of this oil being determined by the adjustment of the screw 546. A second conduit 550 communicates with bore 542 through port 552, which is a short distance to the right of port 546.



  At its other end, the conduit 550 communicates with a bore 554, formed in the body 528 of the pilot distributor, through one of the ends of this body. A drain line 556 communicates with the bore 542 of the pressure regulator 534 at a point beyond the right-hand limit of the stroke of the piston 538. The right-hand end of the bore 542 is kept constantly in place. communication with

  <Desc / Clms Page number 38>

 a groove 558 in the piston, via a bore 560 formed in the piston 538.



   The pilot distributor 496 includes a piston 562 mounted in a bore 554. A compression coil spring 564 rests against the distributor pilot, at the left end of the bore, and in a cavity 566 formed. in the left end of the piston 562, so as to constantly push the latter towards the droire end of the body 528. A drain duct 568 communicates with the bore 554 through an orifice 570 of body 528. Another conduit 572 communicates with bore 554 through port 574 located a short distance to the left of port 570.



   The upper end of the conduit 572 enters the lower end of the body 576 of the relief valve 506 and communicates with the lower end of a small bore 578 formed in that body. A small piston 580 can slide in bore 578. This bore communicates with a larger bore 582, in which a larger piston 584 can slide. This has a fairly large groove 586, which separates one ae. the other its upper and lower heads 588 and 590.



  The conduits 504 and 512 still communicate with each other through the groove 586.



   A compression coil spring 592 disposed in the upper end of bore 582 rests against the upper end of piston 584 so as to urge the latter downward. The conduit 508 communicates with the bore 582, at a point located substantially above the conduits 504 and 512. As seen in FIG. 39, the upper head 588 cuts off the communication of the conduit 508 with the conduits.

  <Desc / Clms Page number 39>

 
504 and 512. The upper end of the bore 582 is kept in constant communication with the drain line 508 by a channel 596 formed in the body 576; it also constantly communicates with the lower end of bore 582 by a channel 594 pierced through piston 584.

   The oil which leaks along the small piston 580 thus loses its pressure and cannot accumulate.



   The operation of the described mechanism can be explained by supposing that one wishes to have a determined maximum pressure in the accumulator; one can therefore refer to the pressure gauge 514 to know when the desired pressure is reached. We first adjust the screw
546 of regulator 534 in a position sufficiently to the right that the desired pressure cannot be achieved after one cycle of operation.

   Under these conditions, a moderate pressure is sufficient in the duct 518 to push the piston 538 of the regulator 534 from the position shown in FIG. 39 to that shown in FIG. 40. In this latter position, the ggrge 558 of the piston 538 makes communicating the orifices 536 and 552 with each other; the pressurized oil coming from the conduit 530 can therefore pass into the conduit 550 and arrive in the right end of the bore 554 of the pilot distributor.



   The oil pressure thus applied to piston 562 immediately pushes it from the right limit of its stroke (Figure 39) to the left limit (Figure 40). As a result, the duct 518 is placed in communication with the duct 572 by a groove 600 formed in the piston 562.



   Oil admitted under pressure into the duct

  <Desc / Clms Page number 40>

 572 is transmitted to the lower end of the small random. sage 578 from the relief valve. The small piston 580 is therefore pushed upwards and comes into contact with the large piston 584, which it pushes back to the upper limit of its stroke, shown in FIG. 40.



  The conduits 504 and 512 then communicate freely with the discharge conduit 508. All the liquid returned by the pump is therefore directed into this discharge conduit and the oil cannot pass through the check valve 513 of the accumulator device. pressure 510.



    However,. the check valve traps in this dis. positive all the oil which has already passed through this valve.



  Under these conditions, the pressure in the accumulator device remains at the characteristic value corresponding to the position in which the regulator screw has been adjusted. By gradually adjusting the regulator screw 546 so as to increase the pressure on the spring $ 44, the pressure in the accumulator device can be gradually increased until the desired pressure is indicated by the pressure gauge 514. .



   When an operating cycle of the press begins, oil flows from the accumulator device into the upper cylinders through distributor 480. The pump is unable to supply the oil with the desired flow rate, but its insufficiency is compensated for by the discharges oil that has been stored in the accumulator. This results in a rapid drop in pressure in the accumulator device. When the pressure drops, the piston 538 moves to the left, cutting off the communication between the conduits 530 and 550 and causing the conduit 550 to communicate with the conduit.

  <Desc / Clms Page number 41>

 drain 556 through groove 558 and channel 560.



   As soon as the conduit 550 is brought into communication with the drain conduit 556, the pressure drops in the conduit 550, so that the piston 562 of the pilot valve is returned to the right limit of its stroke, in the position shown in FIG. 39. This return of the piston 562 cuts off the communication of the duct 572 with the duct 518 and puts the duct 572 in communication with the drain duct 568.



  As a result, the spring 592 returns the piston 584 to the lower limit of its stroke and that the communication is thus cut between the conduits 504 and 512 on the one hand, and the conduit 508 on the other hand.



   The pump then begins to pump oil into the accumulator device again through line 512; it continues to supply oil to this device during the whole operating cycle and after the end of this cycle, until the determined pressure is again reached for which the screw 546 of the regulator has been settled.



   The mechanism described differs essentially from the mechanism of the aforementioned patent application in that a pilot valve is interposed in the present mechanism between the regulator and the relief valve. If the pilot valve of Figure 39 were omitted, the end of conduit 518 which terminates at the pilot valve would be closed, and conduit .550 would be connected directly to the relief valve instead of conduit 572; the provision would then be substantially identical to that provided for in the aforementioned patent application. However, with the latter arrangement, the relief valve exhibits a tendency

  <Desc / Clms Page number 42>

 this to instability, and the use of the pilot distributor provided in the present arrangement makes it possible to eliminate this tendency.

   It may be assumed that this elimination results from the fact that the oil controlling the discharge valve is found substantially at the full pressure of the accumulator, since it is not subjected to the reducing action of the distributor of the regulator, as in the old construction.



   In the aforementioned patent application, front and rear equalizers are provided for the slide.
The front equalizer forces the front edge of the slider to remain constantly horizontal, while the rear equalizer forces the rear edge of the slider to keep at all times; a horizontal position. Front and rear equalizers are provided for the same purpose in the present machine, but their construction has been simplified and made more robust, less time than more efficient.



   In the patent application already cited, the actuating pistons extended upward through the opposite sides of the table to be connected directly to the slide, on the opposite sides thereof and midway between its leading edge and its trailing edge; four corner columns were foreseen, the sole role of which was to achieve equalization and guiaage.



   In the present machine; the drive of the slider is transmitted through the four corner columns 302, and these same columns are used to effect both lateral and longitudinal equalization. As already explained, the columns 302 located on each side

  <Desc / Clms Page number 43>

 of the machine, are rigidly connected at their lower end, to each other and to the control pistons by means of a spacer block 308, so that these guided columns form with the block and the slide a rectangle rigid and.extremely resistant to any longitudinal deformation. Equalizing connections are also provided between the columns 302 of the front pair and the columns 302 of the rear pair.

   These front and rear equalizing links are identical, and it will therefore suffice to describe only one.



   A transverse shaft 602 (Figures 4, 5, 8 and 9), carrying at each of its ends a gear wheel 604, is mounted in bearings 606, which are fixed by screws 608 to the bosses 331 formed on the sleeves 304. An upwardly extending rack 610 is rigidly attached to each end of each spacer block 308; this rack meshes with the corresponding wheel 604. Each rack moves in a guide groove 612 fixed on the conjugate sleeve 304; this / guide 612 is made of a wear resistant metal which is harder than that of the sleeve.



   So that the racks 610 can be adjusted individually, with a view to making them mesh properly with the toothed wheels 604, an adjustable mounting on the blocks 308 which carry them is provided for these racks. Each end of block 308 has a transverse groove 614 (Figures 4 and 8), in which is fixed a block 616 having an inclined rib 618. The rack 610 is fixed to the block 308 by screws 620, which pass through slits

  <Desc / Clms Page number 44>

 verticals 622 of short length formed in the rack.

   This comprises on its rear face a transverse groove 624 intended to receive the inclined rib 618 and designs 626 and 628, which are forcibly inserted into the groove on either side of the rib "" re. These wedges 626 and 628 are thick enough to be tightened strongly against the block 308 by the rack when tightening the screws 620.



   The various parts are first assembled with play, the rack meshing correctly with the combined toothed wheel. The wedges 626 and 628 are then forcibly engaged so as to maintain the adjustment, then the screws 620 are lightly tightened. If a new adjustment is to be made, the screws 620 are partially loosened; we push back the wedge which was in a position where it was opposed to the desired adjustment, and we drive the other wedge inwards until the moment when / we obtain the new desired position of the rack 610 with respect to the block 308. At this moment, the wedge which has been released is forcibly engaged up to its clamping position and the screws 620 are tightened again.



   It was previously stated that the front and rear equalization mechanisms were replicas of each other; however, the rear equalizer shaft
602 is alone subjected to the action of brakes 630 (figures
6 and 7) intended to apply a frictional force to the head 300, in opposition to the hydraulic action, that is to say to brake the head so that the hydraulic thrust meets a resistance making it progressive. action of the head throughout its downward stroke and also making the reversal of movement progressive.

   Without this friction force, the

  <Desc / Clms Page number 45>

 head would tend to fall more quickly than if the hydraulic pressure acted alone; then a resistance, resulting for example from contact with the upper part of the die, would mark a stopping time until the pressure acted again. It would result in a shock. The same happens at the lower end of the stroke, when the machine is running without paper or with a very low cutting action. Under these conditions, the head descends more quickly under the action of its own weight than under the action of the training to which it is subjected, then the pressure catches up its delay and a shock is produced at the moment of reversal of movement.



   Two brakes 630, respectively adjacent to one end and the other of the rear equalizer shaft 602, are applied to this shaft. 'These brakes are identical and it is therefore sufficient to describe only one. Each brake includes two shoes 632 and 634.



  Jaw 632 includes band 636 and liner 638, while jaw 634 includes band 640 and liner 642. Band 636 has an arm 644 at the mpyen of which it is connected to an interior face of the jaw. a rear rib 646 of the table 16 using a screw 648.



   A screw 650 passes through strip 640 and threads into strip 636, holding the two strips together, yet still leaving them free to perform a relative pivoting movement. The jaws grip the shaft 602; on the opposite side to the screw 650, they are held together and elastically pressed together. A bolt 652, the shank of which passes through bands 640 and 636, is surrounded by

  <Desc / Clms Page number 46>

 of its head by a helical compression spring
654. A nut 656 screwed onto the protruding end of bolt 652 rests against band 636, against the action of spring 654. The brake pressure can be adjusted by means of nut 656.



   The brakes 630 are constantly applied, but since they serve only to prevent the descent of the slide by gravity, they can be applied with relatively low pressure so as not to put undue resistance on the hydraulic mechanism and to avoid excessive wear.



   Oh will describe the control and co-ordinating mechanism of the cutting board 18 and slider 20 with reference mainly to schematic figure 41. Under operating conditions, an incoming switch 660 is closed to connect lines. lead 662 and 664 respectively to main conductors 666 and 668. Branch conductors 670 and 672, on which is interposed a switch 674 normally closed, connect the conductors 666 'and 668 to the motor 32.



   To initiate a normal operating cycle, handle 34 is actuated to close a switch 676. This closes a circuit passing through conductor 666, conductor 678, switch 676, conductor 680. , the solenoid 268, a conductor 682, a two position switch 684, which is shown in the down position, a conductor 686 and, finally, the conductor 668. As already explained, the energization of the solenoid 268 triggers a half-turn rotation of the shaft 80, to effect an inward stroke of the cutting board.



   As we have already said the tree 80 entails

  <Desc / Clms Page number 47>

 the crank 76, which transmits the movement to the cutting board. This crank carries a side arm 686, itself carrying a cam 688 at its outer end. When this cam is about to fail, that is to say a little before the end of the half-turn of the shaft 80, it comes into contact with a roller 690 carried by a push rod. 692. This rod is supported at its free end on a crank 694 wedged on a shaft 696. A spring 698 urges the crank 694 and the shaft 696 in a clockwise direction (looking at FIG. 41).



   An arm 697 fixed on the shaft 696 and terminated in the form of a yoke acts on a control member 699. switch 684 to move it to its upper position; this change of position is essential to then trigger the movement of the cutting board outwards.



   A crank 698a (Figures 34 and 36) rigidly connected to the shaft 696 carries a triangular lever. laire 700 forming a lock which is driven upwards, when this shaft rotates counterclockwise under the action of the cam.



  688 of the crank 76 (figure 41). A block 702, integral with an arm 704 and freely mounted on a shaft 882 aligned with the shaft 696, has a projection 706 which is in the path of a spout 708 provided on the triangular lever 700. The arm 704 has a pointed outer extremity 710, which cooperates with a roller 712 carried by a lever 714 mounted oscillating on a shaft 716. A spring 718 mounted on a guide rod 720 acts via the intermediary thereof. ci on lever 714, which it tends to turn clockwise (looking at figure 34).

  <Desc / Clms Page number 48>

 



   When the lock 700 rotates the tip
710 of the arm 704 in an anti-clockwise direction, this point is driven upwards beyond the roller 712, which retains it in the high position,
Furthermore, a roller 720 carried by the latch 700 comes into contact with a rod 722 during the upward movement thereof. When the tip 710 of the arm 704 has passed the roller 712, the rod 722 opposing the movement of the roller 720 rotates the latch 700 and disengages the nose 7Q8 from the projection 706.

   The arm 704 can therefore then pivot downwards without transmitting its movement by the locking lever 700 to the shaft 696. - The upward movement of the arm 704, which has just been described, drives the connecting rod 484 upwards which , as we have already explained, command the hydraulic distributor: 480. As a result, the slide 20 begins to descend.



   When the slider 20 approaches the end of its downward stroke, it acts, via a guide 724 and a cam 726 carried by the latter, on a roller 728, so as to make it rotate in counterclockwise a rocker arm 729 mounted on a pin 730. The rocker arm 729 carries an arm. 732 which, by means of a link 734, cranks 736 and 738 wedged on an oscillating shaft 740, and a connecting rod 742 (see also Figures 34 and 41), rotates the arm 704 clockwise by means of an arm 744 integral with the latter.

   The tip 710 of the arm 704 passes down the roller 712 and the arm 704 moves down, beyond the neutral position, in which it is shown in FIG. 34, and up to the internal limit.

  <Desc / Clms Page number 49>

 of its movement. It follows that the connecting rod
484 reverses the position of distributor 480, as well as the direction of movement of slide 20. The arm
704 is stopped in its lower position by an adjustable stop screw 746, which is threaded through a wall of a housing 748 and which is retained by a lock nut 750 in the selected adjustment position.



   An instant after it begins to move upward, the slider 20 initiates the outward movement of the cutting board 18.



   During the downward movement of the slider, a cam
752 of the equalizing front shaft 602 has passed without producing any effect a roller 754 carried by an elbow lever 756. During the return stroke, and at the beginning of this stroke, the cam 752 rotates the elbow lever 756 in clockwise (figure 41). The angled lever 756 comes into contact with the control member 758 of a switch 760 and causes the displacement of this control member, in response to the pulse received from the cam, so as to close the switch. light switch.



   A circuit is thus established passing through the conductor 666, the switch 760, a conductor 762, the conductor 680, the solenoid 270, a conductor 764, the switch 684 (in its upper position and finally the conductor 668. The movement of the cutting board 18 outward is thus triggered by the action of the solenoid 270 on the clutch lug 254. The closing of the switch 760 has no other purpose than to trigger outward movement of the cutting board During the upstroke of the slider, cam 752 allows elbow lever 756 to return to its original position so as to

  <Desc / Clms Page number 50>

 open switch 760 again.



   The movement of the cutting board outward is stopped by the action of the lug 252 of the clutch 30. The switch 684 is returned to its low position by the action of the spring 698, as soon as the cam 688 of the arm 76 is released from the push rod 692, at the start of the return of the board.



   As the slider 20 approaches the upper limit of its stroke, a cam 766 (Figure 28) carried by the guide. 724 comes into contact with a roller 768 of the rocker arm 729 to rotate the latter in the direction of clockwise. This movement is transmitted through the intermediary of the mechanism which in the preceding description rotates the arm 704 in the counterclockwise. As a result, this arm returns to its original neutral position (FIGS. 34 and 41), cutting off the output of the eight 'fed by the accumulator device. The slide therefore stops in its normal rest position, at the upper limit of its travel.



   . The return of the arm 704 to its neutral position also has the effect of allowing the latch 700 to return to its original position shown in FIG. 34.



  The normal operating cycle is thus terminated.



  Both cutting board 18 and slider 20 were brought to rest in their original positions and the entire operating mechanism also returned to its original state. In the general explanation of the operation which has just been given, many details have been overlooked. We will now describe them.



   Switch 676 comprises a housing 770 (Figures 28 and 29) on which the

  <Desc / Clms Page number 51>

 control handle 34. The switch is of a well known type; it is operated by the handle 34 in a conventional manner. The housing 770 is mounted on the head 300 of the ram, in an easily accessible position near the front of the machine.



   The switch 760 comprises a housing 722 (Figures 22 and 23), fixed on a support 774, itself carried by the table 16 (Figure 7); on the lower side of the plate 240. A control shaft 776 of the switch mechanism is mounted oscillating on the housing 772; the control braa 758 is fixed on this shaft.



   The elbow lever 756 comprises a fork-shaped arm 778, which is attached to a shaft 780, and an arm 7 $ 2 at an angle with the arm 778 'and mounted on the same shaft so that the two arms move together. same time as the shaft around the axis thereof. The arm 782 carries the cam follower 754.



  The shaft 780 is mounted oscillating on brackets 784 and 786 of the support 774.



   It will be remembered that the cam 752 passes through the roller 754 when the slide moves downwards without acting on this roller, but on the contrary actuates the latter during the return stroke of the slide.



  To allow this mode of operation, the arm 782 is mounted so as to be able to oscillate about an axis perpendicular to the axis of the shaft 780.



   The arm 782 is not mounted directly on the shaft 780 but is carried by a support 788 (figs. 24 and 25), fixed to this shaft. The support 788 comprises two parallel arms 790 and 792. An axis 79 is mounted in the arms 790 and 792, in a plane perpendicular to the axis of the shaft; it extends outwards, beyond these two arms. The arm 782

  <Desc / Clms Page number 52>

 also includes arms 796 and 798 spaced apart from each other. These overlap block 788 and extend downward along the outer sides of arms 790 and 792, respectively. Arms 796 and 798 are pivotally mounted on the projecting ends of axle 794.

   A mechanism is provided between the arms 790 and 792 to resiliently bias the arm 782 towards a position perpendicular to the axis of the shaft 780.



   800 and 802 levers are supported on the axis
794; they are urged towards each other by a helical tension spring 804, which extends through holes in the levers and each end of which is connected to the corresponding lever. A fixed finger 806 mounted in the support / 788 constitutes a stopper serving to limit the movement of the right lever 802 '(figure 24) to the left and the movement of the left lever
800 to the right. An 808 spindle mounted in arms 796 and 798 also extends between the levers
800 and 802. This pin can move freely relative to the support 788, since it passes through slots 810 formed in the arms 790 and 792.



   When the arm 782 rotates in the reverse direction of that of the hands of a watch (figure 24), the spindle 808 pushes the lever 800 in front of it, but the lever 802 being stopped by the finger 806 cannot follow the movement. The tension of the spring 804 is therefore increased, and when the displacement force ¯ applied to the arm 782 is removed, the spring returns this arm to its normal and central position. When arm 782 swings in the opposite direction from its normal position, the action is analogous, but this time lever 802 is moved to the right by the

  <Desc / Clms Page number 53>

 pin 808 and lever 800 is retained by the finger
806.



   The cam 752 is mounted on the shaft 602 and driven by this shaft, thanks to a friction ring 812 (Figures 4, 7, 22 and 23). The ring 812, constructed as a brake, comprises two jaws articulated one on the other by an axis 844. Each jaw is constituted by a band 816 of generally semi-circular shape. re and by a gasket 818. The gaskets are arranged in a groove 820 of a collar 821 fixed on the shaft 602; the sides of this groove prevent movement. axial ment of these linings. The bands have ears 822 that face each other.

   A pin 824, fixed in one of the lugs, passes freely through the other lug and is surrounded by a compression coil spring 826. This spring is pressed against the second lug by an adjusting nut 828. pressure; a lock nut 830 maintains the nut in the chosen adjustment position.



   The arm 786 of the support 774 has an extension 832, in which is formed an arcuate slot 834, which is concentric with the shaft 602. The axis 84 extends, at one of its ends, beyond the legs. side faces of the friction ring 812 and engages with play in the slot 834. The ends of this slot are in positions such that they can stop the axis 814; they serve as stops to limit the amplitude of the movement of the cam 752.

   With the frictional drive of cam 752, and the use of stops, the cam is driven with the same amplitude and is synchronized uniformly during its active stroke, despite variations in the upper limit setting. and lower of the stroke of

  <Desc / Clms Page number 54>

 slide.



   The cam 752 is mounted on a seat 846 (FIGS. 22 and 23) provided on one of the bands 816 and fixed to this band by the screws 838. The cam 752 comprises two members 840 and 842. The member '840 is intended to rotate roller 774 sideways and keep it out of reach of member 842 when shaft 602 rotates clockwise (figure 23) during descent of the slide; on the other hand, the member 840 allows the roller 754 to be actuated by the member 842 during the return stroke of the shaft.
 EMI54.1
 - ........ ¯ .......- ": -.... 1kLii ... l ..



  602.



   As the cam rotates clockwise (Figure 24), a front end portion 844 of member 840, which extends obliquely to the direction of rotation, contacts the shaft. roller 754 and pushes it laterally, so that it is driven by a pivoting movement of the arm 782 at the reach of the member 842. An active portion 846 of the member 840 keeps the roller offset until when organ 842 has completely passed it.



  At this moment, the roller is released from the portion 846 and is instantly returned to a position where it is within reach of the member 842.



   Substantially at the start of the return stroke, member 842 comes into contact with roller 754, which therefore moves on this member and rotates elbow lever 756 clockwise (figure 23); as a result, switch 760 closes despite the resistance of a return spring (not shown) housed in the switch housing. Switch 760 is only kept closed

  <Desc / Clms Page number 55>

 for a short while. The contour of the member 842 allows it to return to the open position at the start of the return stroke of this member.

   During this stroke, the face of the cam portion 844, which is turned. facing the viewer in Fig. 23, meets roller 754, but this is simply pushed sideways, due to the pivoting mounting of arm 782, and can then be instantly returned to its normal position shown in Fig. Figure 22 ', after that, the cam portion 844 has left the path free.



   When switch 760 has been returned to the open position by its return spring, the arm
778 rotates and comes into contact with an adjustable stop screw 848, which is screwed into: Plate 240 and held by a. lock nut 849 in its adjustment position. Screw 848 determines the normal position of the elbow lever 756.



   Details of shaft 696 and associated parts, shown in Figure 41, have been shown in Figures 6, 26 and 27. Shaft 696 consists of two parts or aligned sections. The arm 694, which cooperates with the push rod 692, is fixed to each of the adjacent ends of the sections and joins them together as seen in FIG. 26.



   The push rod 692 is slidably mounted in the ears 848 formed on a support 850 (Figures 26 and 27). This 850 support is fixed by screws
852 on the underside of the plate 240. The push rod 692 has a rectangular section; it moves in rectangular openings provided in the ears 848; these openings prevent it from turning

  <Desc / Clms Page number 56>

 ner. A threaded rod 854 is screwed into the end of the rod 692 which is remote from the roller 690; it is fixed in an adjustment position by means of a lock nut 856, which maintains it at a desired effective length. This threaded rod 854 is supported at its free end against a roller 858 mounted on the arm 694.



   The support 850 comprises an arm 860 forming a bearing, in which the shaft 696 can oscillate. One of the ears 848 comprises an extension '862 through which is screwed a screw 864 constituting an adjustable stop. This screw 864 cooperates with a finger 866 carried on the push rod 692 so as to limit the travel of the roller 690 corresponding to the path of the cam 688. The spring 698, which urges the shaft 696 in the direction of the needles of a watch (looking at figure 41), is attached at one end to a finger 868 (figures 26 and 27), on one of the ears 848, and at its other end to a pin 870, which is carried by the arm 694 and on which is mounted the roller 858.



   Switch 684, which determines the direction of movement of the cutting board and which is shown schematically in Figure 41, comprises a housing 872 (Figures 6, 26 and 27), which is attached to a portion. vertical 874 of a support 876; this is fixed to the underside of the table 16.



  The rear end of the shaft 696 is mounted in a bearing 878 integral with the support 876. On this end of the shaft 696 is fixed the arm 697 forming a yoke, through which the switch 684 is actuated. The switch control arm 699 responds to the arm 697; it is wedged on a switch control shaft 880 carried by the housing 872.

  <Desc / Clms Page number 57>

 



   The control mechanism combined with the front end of the shaft fi96 is housed in the control box 748. A fixed shaft 882 (figures 2, 34,
35 and 36) is carried by boot 748, inside thereof, and is axially aligned with shaft 696. One end of shaft 882 is mounted in a boss 884 of a plate 886, which constitutes a wall of the control boot, and it is fixed in this boss by a screw 888. The other end of the shaft 882 extends to the end. inside of a $ 90 hub of the 698a crank. The hub 890 is mounted in the opposite wall 892 of the control box and extends rearwardly beyond this wall.

   A coupling 894 (Figures 26, 27 and 37) washed on shaft 696 includes a split collar 896, which will be re-attached to hub 890 by screw 898, so that crank 698a is connected to shaft 696.



   The triangular lever 700 is pivotally mounted on the crank 698a by means of a pin bolt 900 (Figures 34 and 36). The body of this bolt constitutes the support of the lever 700, while its rod 901 passing through the crank 698a is held on - the latter by a nut 902. An axis 904 provided with a collar let (figure 37) is riveted in the triangular lever 700 and consitute a bearing for the roller 720.

   A pin 906 passes through the pin 904 to hold the roller 720 in place thereon. A tension coil spring 908 is attached at one end to the pin 904 and at the other end to a finger 910. carried by the crank 698a, so as to urge the trian lever. gular 700 in a clockwise direction (Figure 34).



   Block 702, which is mounted os-

  <Desc / Clms Page number 58>

 To wink freely on the fixed shaft 882, has a hub 910 '(Figures 34 and 35), which extends transversely to contact the wall 886 of the control box. The arm 704 is mounted on the hub 910 ', against a shoulder 912. Screws 916 pass through the arm 704 and screw into the block 702 so as to fix the arm on the block.



   Connecting rod 484 (Fig. 41) has a clevis-shaped upper end which is shown in Figs. 34-37 and which overlaps arm 704.



  A head pin 918 passes through the end cap of the connecting rod 484 and the arm 704; its end opposite the head is pushed back. The arm 744 (Figures 34 and 37) is integral with the block 702; is therefore obliged to turn at all times at the same time as the arm 704.



  The control box is fixed by screws 919 on the rib 186 of the table 16.



   It has already been indicated that the cam 726 limiting the downward stroke and the cam 766 limiting the upward stroke are carried by a guide 724, which is driven by the slide 20. The cam 726 is fixed on the guide. 724 by rivets 920, (figures 28, 30 and 31).



  Since it cooperates with the roller 728, which is at an invariable level, the vertical adjustment of the guide with respect to the slider 20 determines the level at which the slider reverses its downward movement.



   Guide 724 comprises a flat bar with rectangular section 922, at the upper end of which is fixed by screws 926 a block 924 (Figures 28 and 29). It also includes a threaded rod 928, which is screwed into the block 924. An upper, unthreaded part of the rod 928 passes through a bracket 930 fixed by screws 932 on the head 300 of the.

  <Desc / Clms Page number 59>

 slide. The rod 928 is blocked against any axial displacement, with respect to the stem 930, by a clamp 934 keyed on the stem below the stem, and by the hub of a control wheel 936 which is locked. vetée on the rod above the gallows. The useful length of the guide 724 is adjusted by rotating the wheel 936, so as to rotate the rod 928 in the block 924.



   Provisions are made to lock rod 928 and prevent it from rotating, when the desired adjustment has been made. A grub screw 938 (Figure 28a) is engaged in a bore 940 of the post 930. The rod 928 passes upwardly through a notch 942 formed on one side of the screw and prevents rotation of the same. this. A knurled nut 944 is screwed onto a protruding end of screw 938 and normally rests against a face of stem 930. Turning nut 944 in the desired direction to screw it onto screw 938 exerts pressure on it. ci pulling outwardly, so that one face of the notch 942 energetically clamps the rod 928 and consequently prevents the latter from rotating.

   If you want to make a new adjustment, you start by slightly unscrewing nut 944. When the new adjustment is complete, you tighten this nut again.



   The upper stroke limiting cam (Figures 30, 31 and 32) is mounted so that it can be adjusted longitudinally with respect to the slide bar 922. Since the lower cam 26 is attached to this bar, the adjustment of the cam 766 determines the stroke of the slide, by determining the height, above the lower limit of its movement, at which the slide is normally located

  <Desc / Clms Page number 60>

 at rest.



   The lower end of the slide bar 922 has a longitudinal recess 946 on the operator's side. Behind this recess, the sliding bar 922 has a slot 948 which extends along the recess 946. The shank of a screw 950 passes through the slot 948 and screws into the cam 766; the head of this screw is normally biased so as to tighten the bar by pressing against the face 952 forming the bottom of the recess 946. A second screw 954 likewise passes through the slot 948 and is screwed into the cam 766. However, , the shank of this screw also passes through a small rectangular plate 956 against which the head of the screw rests.

   This plate carries a stud 958 which extends rearwardly and can be selectively inserted into any of a series of holes 960, formed in the left section of wall 952.



   When an adjustment is desired, the screw 950 is slightly loosened, then the sight 954 is sufficiently loosened to be able to disengage from the wall 952 the stud 958 of the plate 956. The desired adjustment is then made by making slide cam 766 along slide bar 922 to the desired position. Plate 956 and its pin 958 move with the cam during adjustment. When the desired position of adjustment has been determined, the stud is inserted into one of the holes 960 and the screws 954 and 950 are then tightened again.



   A finger 962 extending forwardly through the slot 948 is attached to the cam. This finger carries at its front end an index 904, which cooperates with an adjustment scale 966 provided on the bar

  <Desc / Clms Page number 61>

 sliding 922, along the right side of recess 946 (Figure 30).



   The sliding bar 922 passes freely through an opening 968 (Figure 28) provided at the edge of the table 16. It is guided in a holder 970 (Figures 28, 29 and 33) mounted below the table.



   This support is fixed by a screw 972 below the table 16; it is also fixed by screws 974 on the boss 331 of an adjacent sleeve 304 (FIG. 28). This support 970 comprises a groove 976 intended to receive the sliding bar 922. Guide strips
978 fixed by screws 980 on the walls of the groove cover the edges of the bar 922.



   The support 970 comprises an extension 982 on which the axis 730 is fixed. The rocker arm 729, which carries the rollers 728 and 768 and of which the crank 732 is an integral part, is mounted to pivot on the axis
730. This has at its free end a head
986 to hold the rocker arm 729 in place.



   Cams 726 and 766 are mounted on slide bar 922 in positions such that they are not vertically aligned with each other (Figure 30). The rollers 728 and 768 carried by the rocker arm 729 are also not aligned vertically with respect to each other (figure 29), but are aligned respectively with the cams 726 and 766 (figure 33) so as to each be actuated by the corresponding carne. The offset position of the cams also makes it possible to adjust them in a relative overlapping position, without them interfering with each other, when an adjustment is desired.



   In the neutral position of the parts, shown in FIG. 34, a transverse pin 986, which.

  <Desc / Clms Page number 62>

 makes the connection between the arm 744 and the connecting rod 742, is located at the left end of a slot 990 formed in the connecting rod 742. This position obviously results.

   because the arm 704 has been operated counterclockwise to the position shown, in response to a push exerted by the connecting rod 742. Since the slot 990 extends to the right] from the stud 988, the arm 704 can be moved freely upwards to produce a downward stroke of the slide, without disturbing the position of the connecting rod 742.



   As arm 704 moves upward to initiate a downstroke of the slider, it abuts an adjustable screw 992 (Figure 37) and remains in contact with that screw until the downstroke of the slider is complete. At this time, as already explained, the arm 704 is driven by the connecting rod 742 (see also figure 28) up to the lower limit of its stroke, where it is in contact with the adjustable stop screw 746. .



   The screws 746 and 992 were made adjustable to allow the upper and lower limits of the displacement of the arm 704 to be selected at will and thus to control the degree of opening of the distributor 480 during the downstroke and the stroke, respectively. rise of the slide. The flow rate of the liquid to the cylinders 36 and 38 respectively is thus determined, and it is therefore possible to separately control the speed of descent and the speed of rise of the slide.



   It is sometimes desirable to work the cutting board by bringing it to its cutting position and then moving it away from that position.

  <Desc / Clms Page number 63>

 tion, without actuating the slide. A situation requiring this mode of operation has already been described in connection with the change of coupling between the rod 70 and the block 82 by which the cutting board is driven. For this purpose, a means other than the switch 676 has been provided for triggering the movement of the cutting board without actuating the slide.



   A handle 994 (figures 4 and 41), guided with play so as to slide in a support 996 fixed to the table 16, is articulated on an arm of an elbow lever 998, which can pivot freely on the shaft 740a . The other arm of the elbow lever 998 is connected by a push rod 1.000 to an arm 1002 wedged on the shaft 716. On this is also fixed an elbow lever 1004, which comprises arms 1006 and 1008 steten- respectively upwards and inwards (see also figure 34).



   The arm 1006 is capable of cooperating with a push rod 1010. The latter is mounted cou-.



    'smoothing in a wall 1012 of the casing 748 of the control box and in a tab 1014 integral with this casing. A compression coil spring 1016 surrounds the rod 1010; it rests at its left end (figure 35) against the wall 1012 and at its right end against a collar 1018, which is fixed on the rod 1010 and which normally rests against the left face of leg 1014.



   In the end of the rod 1010, on the side opposite to the arm 1006, is screwed a head screw 1020 held in place by a lock nut 1022. The head of the screw 1020 is in contact with the control arm 1024 d ' a switch 1026. This arm is wedged on a control shaft 1028, which is mounted oscillating in the casing 1030 of the switch 1026. This casing is.

  <Desc / Clms Page number 64>

 fixed on the table 16 by screws 1032.



   When it is desired to move the cutting board 18 backwards without actuating the slide, the handle 994 is pushed downwards; the shaft 716 is thus rotated in a counterclockwise direction. so that the arm 1006 pushes the rod 1010 to the left (figure 35) and closes the contacts of the switch 1026. This results in the closing of a circuit (figure 41) passing through the conductor 666, a conductor 1034, l 'switch 1026, one conductor
1036, conductor 680, solenoid 268, conductor 682, switch 684 in the down position, conductor 686 and finally conductor 668.

   The cutting board 18, or at least the rod 70, if the cutting board is detached from this rod, is therefore driven to the rear limit of its stroke where it stops.



   A mechanism has been provided which responds to the movement of the handle 994 and makes it possible to prevent the triggering of the slide stroke when the cutting board is actuated by means of this handle.



   The $ 100 arm of the elbow lever 1004 fixed on the shaft 716 carries at its free end a roller 1038 (figures
34, 35 and 37) intended to act on a plunger sleeve
1040, capable of reciprocating movement in a vertical bore 1042 formed in the leg
1014. This sleeve 1040 has a horizontal slot 1044 on the outside, in which the roller 1038 engages. The latter accesses the slot 1044 through a wider slot 1046 formed in the tab 1014; the latter slot is wide enough to allow the movement of the roller 1038 without any hindrance.



   A bore 1048 of the sleeve 1040 is passed through

  <Desc / Clms Page number 65>

 by un.cloison 1050, disposed substantially in the middle of the length of the bore. A compression coil spring 1052, housed in the lower part of the bore 1048, rests at its upper end against the bulkhead 1050 and at its lower end against the part of the tab 1014 at the lower end. of bore 1042. This spring 1052 normally holds the sleeve in a position corresponding to the upper limit of its movement in bore 1042, against a flanged plug.
1054.

   This plug is attached to the end of bore 1042 by screws 1056 (Figure 37), which are screwed into tab 1014.



  * The rod 722, which is in the path of the roller 720 of the triangular lever 700 and which serves to pivot the spout 708 to release it from the projection 706 of the block 702, after the point 710 of the arm 704 has passed through the roller 712 during normal operation is slidably mounted in the sleeve 1040. It is guided in the partition 1050, the plug 1054 and the lower part of the tab 1014. This rod 722 comprises a collar 1058 located above the partition 1050.

   A compression coil spring 1060, which surrounds the rod 722 and is located in the upper part of the bore 1048, this spring resting at its upper end against the plug 1054 and at its lower end against the flange 1058 , thus maintaining this collar normally applied by its lower face against the partition 1050.



   In order to clearly understand the particular operation which takes place without any movement of the chicken, it is necessary to explain in more detail what occurs in normal operation.

  <Desc / Clms Page number 66>

 when arm 698a rotates counterclockwise (figure 41). When the triangular lever 700 (Figure 34) is driven upward by the arm 698a, the spout 708 rests against the projection 706 of the block 702 and drives the arm 704 a sufficient length to produce at the tip 710 of this arm the click action discussed above.

   A short time after the triangular lever 700 has started to move up, the roller 720 of this lever comes into contact with the rod 722 and causes the latter to compress the spring 1060, while the triangular lever 700 continues to move. .to the top; At the precise moment of the click action, the wishbone lever 700 must do a major job of rotating the arm 704 counterclockwise despite resistance. opposed by the spring. 718 acting on the lever 714. However, as soon as the tip 710 of the arm 704 crosses the roller 712, the projection 706 moves away from the spout 708.

   The frictional contact, which was maintained between the protrusion and the spout, is thereby eliminated, so that the energy stored in the compression spring 1060 can push the rod 722 down and clear the spout 708. projection 706.



   However, in the special operation considered here, during which the cutting board is actuated without the slider being set in motion, the triangular lever 700, the nose 708 of which is disengaged from the projection in the normal position of the Parts, pivots. to drive this nose and disengage it from the projection before the arm 698 has rotated. this is

  <Desc / Clms Page number 67>

 produced through the sleeve 1040 and the rod 722.
 EMI67.1
 



  The communicated pivot, <* "to. shaft 716 by handle 994 is applied to arm 1008 so as to push sleeve 1040 down overcoming the resistance of spring 1052. Spring 1060 forces rod 722 to follow sleeve 1040 downward. down and come into contact with the roller 720, pushing the latter far enough down to cause the spout 708 to pivot and disengage it from the projection 706. The force exerted by the spring 1060 is relatively small in these conditions. . here, but there is no frictional force interfering with the pivoting of the nose at this time, and the force exerted by the spring 1060 is sufficient to overcome the force of the spring 908 to return the latch 700.

   Consequently, when the cam 688 acts, at the end of the travel of the cutting board inward, to rotate the crank 698a, counterclockwise (figure 34 ), the beak 708 of the lock has already pivoted by disengaging from the projection 706 so as to eliminate the connection between the arm 698 and the arm 704. This therefore results in no movement of the arm 704 and of the conjugate connecting rod 484. .



   The distributor 480 therefore remains closed and the slide remains at rest.



   To relieve the operator of the obligation to keep the handle 994 in the low position for any prescribed period, arrangements are made to lock the sleeve 1040 in its low position. This lock removes the possibili. tee for the spout 708 to return to the engagement position with the projection 706 in conditions causing an untimely control of the arm 704.

   A lo62 lock,

  <Desc / Clms Page number 68>

 pivotally mounted on an axis 1064 integral with the leg
1014, can act in a groove 1066 formed in this tab; lock comprises a spout capable of automatically engaging in a notch 1068 u sleeve 1040 to lock the latter in the low position, when it has been lowered by the arm 1008.



   A plunger pin 1070, slidably mounted in a bore 1072 of the tab 1014, is pushed towards the. Bottom against the heel of latch 1062 by a compression coil spring 1074 housed in this bore and resting against a stopper 1076 screwed into the upper end of the bore. Latch 1062, thus made capable of holding lever 700 in the inactive position, is held active when the handle 698a moves up.

   However, when this crank approaches the upper limit of its stroke, and after the spout 708 has been driven upward beyond any position making it possible to engage with the projection 706, a portion 1078, protruding towards the top and integral with the crank 698a, comes into contact with the heel of the lock and rotates the latter by disengaging it from the notch 1068 of the sleeve and thus allowing the latter to move instantaneously towards the top.



   When the cutting board has been driven backwards, as has just been explained, without the slide having undergone any displacement, and when it has stopped, it is necessary for the operator to trigger the return movement of the board. This is done by actuating the handle 994 a second time. As a result of this maneuver, the switch 1026 closes again. The circuit

  <Desc / Clms Page number 69>

 established passes as previously through conductor 666, conductor 1034, switch 1026, conductor
1036, and lead 680. However, the current, instead of passing through solenoid 268, then passes through solenoid 270 because switch 684 is at this time in the up position.

   From solenoid 270, the circuit continues through conductor 764, switch 684 in the up position, and conductor 668. As a result, the board is returned to its forward position.



   When you operate for the second time. handle 994, in the same manner as the first time, arm 1008 of coted lever 1004 is pivoted downward and sleeve 1040 is caused to lower.



  However, this movement takes place on no load, because the latch 1062 is kept inactive at this time by the part 1078 of the crank 698a, which is at the upper limit of its movement. Therefore, as soon as the handle 994 is released the sleeve returns to its upper position. The beak 708 of the locking lever 700 can therefore automatically return to its normal position. when arm 698 has itself returned to its normal position. This occurs as soon as the cam 698 disengages from the roller 690, that is, an instant after the start of the outward movement of the cutting board.



   Handle 994 also serves as a safety handle. If the operator, after having actuated the switch 676 to initiate a normal operating cycle, realizes that, for some reason the cycle cannot be carried out normally, he can stop the operation of the slide by quickly actuating handle 994. This maneuver

  <Desc / Clms Page number 70>

 exerts no effect on the movement of the cutting board, but renders the locking lever 700 inactive as described above. When the cutting board finishes its inward movement, it therefore comes to a stop without having actuated the slide.

   The operator can then return the cutting board to its outer position by actuating handle 994 a second time, as has already been explained.



   It sometimes happens that one wishes to actuate the slider 20 upwards to any position of the cutting board 18 during its cycle. The operator may notice, for example, that, despite the precautions described, after a period of stoppage and when he is ready to resume work, the slide has been lowered by gravity to its lowest position, or all in the hand. to an intermediate position. In either case, the slider is no longer synchronized with the cutting board, and it is desirable to return it to its highest position without changing the normal resting position. of the decoration board and its control mechanism.



   On the other hand, if the slider is stopped during its downward stroke (for example when it descends on an inverted die accidentally on the stack of sheets), it becomes necessary to return the slider to its highest position, then to return the cutting board to its front position, independently of the slide, if it has not been brought back automatically by the return of the latter.



   - Moreover, if the operator notices that the matrix is inverted, or that any other obstacle whatsoever -

  <Desc / Clms Page number 71>

 that, when the slide has started to descend during a normal cycle, it needs to be able to reverse the movement of the slide, before it comes in contact with the die or other obstacle and to bring it back at its highest position
In order to meet all these requirements, a mechanism has been provided which can be actuated at any time to return the slide to its highest position, when it has left. This mechanism is clearly shown in Figures 4 and 5.



   A pedal 1080 is attached to a shaft 1082, which is mounted oscillating in fixed bearings 1084 and 1086. A tension coil spring 1088 connected to the pedal and to a fixed finger 1090 maintains the pedal in a normal high position, in which it is applied against a stop (not shown). A crank 1092 attached to the shaft 1082 carries a lug 1094, which sits above a disc 1096 wedged on a lower end portion of the valve control rod 484.



   The lug 1094 is normally maintained at a height such that the rod 484 can complete its full cycle of operation without the disc 1096 coming into contact with the axle 1094 or being stopped by the latter. However, by operating the pedal, the lug 1094 can be lowered, so as to bring it into contact with the disc 1096 and lower it far enough to drive the rod 484 to the lower limit of its stroke. It is possible to carry out this operation at any time, either while the various parts of the machine are at rest, or in

  <Desc / Clms Page number 72>

 at any time during an operating cycle.

   When the rod is biased downward with the engine running, the distributor connections are established such that pressurized oil is forced into the cylinders 38 to drive the slide 20 to its highest position.



   When, after a period of stoppage, the operator notices that the slide has moved away from its highest position and must be returned to this high position, he first closes the switch 660 of the slide and engine switch 674. He then opens an easily accessible switch 1098 for cutting the board control circuit (see also FIG. 41); this opening has the effect of making inactive all the circuits likely to affect the solenoids 268 and 270.



  The operator then operates the pedal 1080 to return the slider 20 to / its highest position, as explained.



   There is a reason that switch '1098 is open before the pedal is actuated; that is, the upward movement of the slider normally performs closing and opening of the switch 760. If the switch 760 was left closed momentarily during this upward movement of the slider. it would cause the solenoid 268 to be energized and consequently an unwanted movement of the cutting board to its rear position, that is to say interior.



   It may happen that the slide has undergone, from its normal rest position, a displacement of such a small amplitude that its return upwards would not produce a closing of the switch 760. In this case,

  <Desc / Clms Page number 73>

 in this case, opening switch 1098 would be superfluous. However, the opening of this switch is of no consequence in this case and the obligation of such opening, in such circumstances, can therefore be regarded as a uniform rule. When the slider has been brought up, the operator again closes switch 1098 to prepare for resumption of normal operation.



   When the movement of the slide has been reversed by actuating the pedal 1080 during a downward stroke of the slide, there is no time to open the switch 1098. However, it is not necessary to open this. switch, since the cutting board is already in its rear position, ie inside. If the rise of the slider causes the cutting board to return to its front position, the desired movement is obtained precisely. If, on the other hand, the cutting board remains in its rear position, the operator can return it to its front position independently of the operation of the slider, by operating the handle 994 as explained.



   When the slide is stopped during its downward travel, the maneuvers are identical to those just described. The operator first actuates pedal 1080 to raise the slide, and if he then notices that the board has remained in its rear position, he actuates handle 1094 to return the board to its forward position.



   A brake mechanism 1100, shown in detail in Figure 21, can act on the brake drum 248 (Figures 7 and 21) which is mounted on the shaft 80. This brake mechanism serves to prevent the shaft 80 from turning. exceed a normal range of motion and avoid

  <Desc / Clms Page number 74>

 ter the well-known shocks which tend to occur commonly in "one-turn" clutches. The braking mechanism 1100 includes two bands 1102 and 1104; the first of these bands comprises an arm 1106 fixed by a screw 1110 to a fixed support 1108.

   These bands are provided with linings which rest in a groove 1112 formed in the drum 248. On one side of this drum, the bands 1102 and 1104 are interconnected by ears 1114. A screw 1116 passes through one of the bands. these ears and screws into each other. On the opposite side, a head screw 1118 first passes through a compression coil spring 1120, then a lug 1122 formed on the band 1104 and finally the arm 1106. A nut 1124 screwed on the end of the screw 1118 maintains assembled the different parts and allows the spring -1120 to push the band 1104 towards the band 1102 to apply a controlled braking pressure.



   All the mechanisms, which are located under the table and in which heat is given off during their operation, are enclosed in a closed enclosure. The rear part of this speaker is wider than the front .; It is limited by a rear plate 1126 fixed to the rear ends of the panels 10 (FIG. 5). Side plates 1128 each cover the corresponding panel 10 and are attached to it.



  Doors 1130 are hinged to the front ends of panels 10. Each door closes the space between one of the panels and the adjacent side plate 54 of the narrow front portion of the enclosure.



   The front end thereof is covered by a front closure plate 1132, which is inclined and removable. The side plates 54 have nerves

  <Desc / Clms Page number 75>

 inclined vures 1134 (figure 16), turned inward and therefore directed towards each other. Parallel bars 1136 and 1138 (see also figure
17) extend between ribs 1134 and are permanently attached thereto. The closure plate 1132 has an upper pair and a lower pair of hooks 1140, which are fixed to this plate to cooperate with the bars 1136 and respectively.
1138, so that plate 1132 can be conveniently applied and removed.



   The back plate 1126 and the front plate 1132 are provided with louver blades 1142 and 1144 (see also figure 1), so that an air circulation is established in the direction of the arrows in figure 1, to through the closed enclosure by means of a fan 1146 mounted on the motor shaft.



   A plate 1148 constitutes an upper limit of the part of the enclosure containing the motor; this plate is supported by bars 1150, which are fixed by rivets 1152 on the side plates 54.



   Of course, the invention is not limited to the embodiment shown and described which has been given only by way of example.


    

Claims (1)

ABSTRACT The subject of the invention is a cutting press 4 comprising a slide, a table on which is mounted a movable cutting board, the slide being driven downwards, that is to say towards the cutting board, by a hydraulic device mounted below the table and four columns rigidly linked to the slide, this press being remarkable in particular, by the following characteristics considered separately or in combinations: <Desc / Clms Page number 76> 1 two massive blocks forming spacers connect the columns two by two and the hydraulic device is arranged so as to act on the columns by means of the spacer blocks, these columns, thus dragging the slide; 2 guide sleeves are mounted in the table to guide the columns; The spacer blocks extend longitudinally and are each disposed on one of two opposite sides of the press; The 4 M hydraulic device comprises upper cylinders, each of which acts on one of the spacer blocks to drive the slide down, and lower cylinders, each of which acts on one of the spacer blocks to raise the slide when the cutting operation is finished; 5 the upper cylinders are open to their. lower end and the 'lower cylinders are. open at their upper end; 6 the upper cylinders are provided with pistons which include flexible flanged sealing washers, the flange of each washer facing towards the open end of the corresponding cylinder, and resilient means for pushing the collar towards the wall of the conjugate cylinder, each flange 'serving to prevent air from passing along the piston and opposing the descent of the slide by gravity; 7 The pistons of the upper cylinders also include flexible flanged sealing washers, each flange facing away from the open end of the corresponding cylinder, to prevent hydraulic fluid from escaping along. pistons; <Desc / Clms Page number 77> 8 the hydraulic device comprises one or more cylinders, each comprising a grooved sleeve with a split ring housed in this groove, the sleeve being fixed in the press by another ring resting against the split ring; 9 those of the columns which are not connected to each other by the spacer blocks, are connected to each other by equalization devices which oblige them to move simultaneously; The equalization devices comprise two shafts each carrying two pinions and racks each carried by one of the columns and each in engagement with one of said pinions; 11) guide members are provided to force the pinions to remain in engagement with the corresponding racks; 12 the cutting board is moved in a reciprocating motion so as to come under the slide before each downstroke thereof and to withdraw. when the cutting operation is complete, and it is connected to a reciprocating mechanism by means of a rod and an adjustable fitting or coupling, the latter allowing the parts to be selectively turned. different from the cutting board under the slide for each cutting operation; 13 The rod connecting the cutting board to its drive mechanism has holes spaced longitudinally but not aligned and the coupling between the cutting board and its drive mechanism includes plunger fingers which can be selectively and individually engaged in said holes to effect the desired bond; <Desc / Clms Page number 78> 14 the cutting board coupling plungers are controlled by a cam member, which is protected by a stop device against any inadvertent movement; 150 the cutting board is moved in an alternating motion during each cutting operation so as to place itself under the slide before it descends, and to disengage after the cutting operation has been carried out , the movement of the cutting board being controlled by a "half-turn" clutch which is itself controlled by two stop lugs, these lugs being selectively controlled by two aligned solenoids whose reinforcements are connected to; a common rod which controls the positions of said lugs, a first half-turn of the clutch being produced under the action of one of the solenoids, and another half-turn being obtained under the action of the other solenolid; 16 a centering device is provided for the common control rod of the solenoids, and this device normally placed the two reinforcements for the selective operation by one or the other solenoid, with the two stop pins in active position; 17 the press comprises a shaft driven by the slide during its downward stroke and a braking mechanism constantly acting on this shaft to oppose the descent of the slide by gravity; 18 the hydraulic device being actuated by a pump intended to deliver pressurized liquid to a pressure accumulator device, the press comprises a discharge valve through which the liquid is delivered by the pump into said device. <Desc / Clms Page number 79> accumulator, a pressure duct included in this device, a pressure regulator sensitive to the pressure in this duct and comprising an adjustable spring to limit this pressure, by means of an indirect control exerted on the valve. discharge, this regulator comprising a sliding piston sensitive to the hydraulic pressure and to the pressure of the spring and capa. ble to transmit the liquid, in response to a predetermined pressure, with the residual pressure remaining after the spring pressure has been overcome, a pilot-distributor which comprises a body, comprising a bore capable of receiving the liquid transmitted by the regulator and a piston arranged in this bore and subjected to the action of the liquid transmitted by the regulator. means connecting the pressure conduit to a part of the body of the pilot distributor, the piston of this distributor comprising a channel constructed and arranged so as to allow the liquid to pass under the full pressure of the accumulator device through said body when the pilot valve is moved relative to its normal position, the relief valve comprising a body provided with a bore, and means connecting the body of the pilot valve to one end of the valve bore. discharge to subject it to the action of the liquid which has passed through the pilot valve and which is at the full pressure of the device, the discharge valve comprising a piston capable of being moved by this pressure from its position normal, and this piston comprising a lumen capable of responding to such a movement in order to divert the liquid supplied by the pump to the discharge valve so as to return it to the source in which it had been sucked by the pump; <Desc / Clms Page number 80> 19 the slider being capable of undergoing a movement of a variable amplitude at will, the cutting board coming to be placed under the slider before each cutting operation and withdrawing after the end of this operation, this withdrawal of the cutting board. cutting being controlled by an electric circuit, a switch is connected in this circuit and arranged so as to act during the upstroke of the slide to cause the withdrawal of the cutting board, this switch being controlled by a cam which passes through the switch without acting on it during the downward stroke of the slide and which actuates the switch at the start of the upward stroke of the slide, this cam being driven by a friction coupling susceptible - able to slide so that the action of the switch is independent of the amplitude of the movement of the slide; The amplitude of the movement of the cam is limited to the value necessary for the actuation of the switch; 21 the cam is connected to one of the columns by engrenages. Entrained by the movement of the slide; 22 the gears also connect two of the columns, which are not connected to each other by the spacer blocks, so that these columns move simultaneously.