BE541186A - - Google Patents

Description

       

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  Machine for cold mechanical working of metal.



   The present invention relates to a machine for mechanical working of metal, in particular for forming hollow objects starting from blanks of metal sheets,
The term "hollow" used herein is to be understood as applying to an article of frustoconical shape, for example of shape similar to a megaphone, and extends to an object of generally hemi-spherical shape such as a cup or to a tube-shaped or generally tubular article.



  Furthermore the term applies to an article part of which has the above form. On the other hand, the term "metal foil" includes plate or sheet-like or plate-like elements, even if they are obtained by casting, forging, welding or the like.

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In general the machine of the invention relates to cold mechanical working or metal forming by means of one or more rollers. Some machines are known comprising a rotating spindle in the shape of the desired object, a rotating shank piece for clamping a flat blank against the spindle, and a roller or roller mounted on a suitable carriage.

   The carriage is moved so as to bring the roller onto the blank and, as the blank rotates, the roller is moved along the spindle to flow or displace the metal of the blank onto the spindle and form the object. In most cases, such machines form conical shaped articles with straight edges. However, when the article requires a different side contour, the machine is equipped with a guide mechanism which moves the roller in the desired direction.



   In general, the known machines have been made to meet the demands of the industry for hollow articles such as television tubes, separator discs for dairy machines, metal containers and the like. The main reason for forming such articles by cold working with a roller is to reduce the use of conventional metalworking operations such as forging, machining, welding and particularly drawing, which consume water. : nps, waste material and require expensive special tools.

   Time and price are particularly characteristic of hollow drawing operations in. which a tapered article may require half a dozen draws with intermediate stages of annealing for its forming, while in cold working with a roller the same article can be formed in a single pass of the roller along the brooch. In addition, cold working with a roller increases the resistance and the hardness of an object, which is obviously the opposite in recessed drawing.



   Industrial demand for low-cost hollow articles

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 workmanship and light weight is significant and is constantly growing. Both the military and commercial jet aircraft program has created a large demand for such parts for exhaust and tail cones. The use of conical objects as explosive charge containers for projectiles and for open hearth and blast furnaces is increasing. In addition, many stainless steel hollow articles are used as shipping containers for food and medical products.



   Currently known cold roll forming machines are not suitable for producing the hollow articles according to the mass production requirements for certain types of articles, mainly because they are not suitable for automatic operation. and due to their inability to move certain types and thicknesses of metal and alloys at high speeds.



   For this purpose, the invention relates to a machine for cold roll forming, which is automatically operated, in that an operator simply has to load and unload the blanks and press a button to turn on the machine. in action through its various operating cycles. The machine can be made fully automatic by auxiliary loading and unloading equipment which includes devices for initiating the operating cycle after the blank is engaged. The machine is capable of extremely high production speeds and can mass produce cold formed articles from virtually all various types of metals and alloys.



   While the machine tool described here is capable of automatically mass-producing the ordinary articles mentioned, it includes certain arrangements which allow the technique of cold forming to be applied in fields where it was heretofore impossible. . In other words, the ma-
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 the

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 China of the invention allows the rapid and economical forming of objects which cannot be produced by known cold forming machines and in many cases could not be formed by conventional, slow and expensive operations such as forging , intaglio drawing and machining.



   Further some of the designs included in the machine are perfectly suited, either singly or in combination, for application on other machine tools such as lathes, planers and the like, although they have exceptional and sometimes advantages. surprising in the field of cold forming for which the machine of the invention is mainly intended.



   The machine of the invention, in general, uses known elements such as a spindle, a tail or counter head piece, rollers mounted on a carriage, a guide mechanism and the like. However, in the machine these components have been refined, coordinated and made to function in ways heretofore unknown. Thanks to these modifications and to the different operation and coordination of the components, and thanks to the introduction of new features, the machine operates absolutely automatically and produces a wide variety of objects at a very high speed.



   For example, in the machine of the invention, the spindle and the carriage, including the mechanism for mounting the roller thereon, are constructed so that a blank can be worked at pressures in the region of 30 tons even @ by rotating it at speeds of the order of 2000 revolutions / minuta. This results in very high feed speeds, approaching for example 1.50 meter per minute.



   The spindle has a single hydraulic thrust bearing which allows a blank to be worked at the speeds and pressures mentioned above. This bearing is an astonishing improvement over ordinary thrust bearings of the roller and anti-friotion type and no previously known bearing could

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 withstand such loads while rotating at such speeds.



   The carriage and the mechanism for mounting the rollers on it are constructed and arranged to be of very low weight and yet capable of exerting the necessary high pressures. The carriage is movable longitudinally above a bench and the rollers movable transversely to the carriage. The arrangement of the bearings to allow such displacements not only absorbs the high pressures set in yellowish allows for a rolling sliding action which reduces frictional forces to a minimum.



   The tail piece or headstock is constructed as an integral part of the carriage but can move relative to it. Thus the carriage and tail can be moved quickly to a blank, the tail, engage the blank and tighten it on the spindle while the carriage continues to move forward, while the rollers work on the blank. The characteristics have greatly contributed to the self-control of the machine because no delay is necessary for the adjustment of the shank to the blank and its clamping and because automatic compensation is provided for any variation in thickness of the blanks to be passed.

   Further, the tail piece has a rotating head supported by a single hydraulic thrust bearing which allows high clamping pressures at the high roughing speeds mentioned above.



   The jig support device used in the machine guiding mechanism plays an important role in automation. With guiding, it is necessary that the starting point of the follower finger in relation to the template is always perfectly in line with the starting point of the working tool, that is to say rollers and this is particularly the case for precision work. Variations in the thickness of the blanks used in cold forming and due to manufacturing tolerances can be up to ¯ 10% of the thickness.

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 over-and beautiful vaiations make precision forming of.? objects impossible a. unless an adjustment is made for] ,: '4pousseur of each blank.

   This would obviously be inadmissible when the objects have to be mass produced or when
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 the machine must be automatic in the usual sense of the word. The machine of the invention automatically provides such compensation. This is done by making the jig movable with the rollers but not movable once the rollers have engaged a blank to begin work. The rollers and the jig can be brought to the blank as a unit and, when the rollers are pressed firmly against the blank in the starting position, the jig is locked on the bed. As the template is not fixed as long as the rollers are not in the starting position, the variation in thickness of the blank has no effect on the precision of the object to be formed.
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  The invention relates to a fully automatic high-energy coordinated mechanism, in which certain features are used in combination, and comprising several of the following: rollers working in pairs are coordinated with each other and with the other parts of the machine in combination.
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 being individually mounted for three different adjustment motions relative to the carriage and also being automatically coordinated with the workpiece on the spindle as they progress on their working stroke; at the same time, given the flexibility and the simplicity of the adjustment, a roller, once previously adjusted, can be fixed in position while the other is adjusted in relation to it;

   the speed of movement) - the roller along its working stroke and the speed of
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 d4placnt of the carriage carrying the rollers are cootdonn4es for slzi.1-ipt-r with different resistances of the different parts and the vitoss'3 of the carriage is itself varied in nrâdé coordination.
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 completed -aV'tc the different portions of the work ce7.e;

   for greater precision, the tailpiece that carries

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 against the. workpiece when positioned on the spindle is in elastic engagement with the carriage and the same is true of the template of the guide mechanism, the latter in turn being automatically coordinated along the rollers, relative to the workpiece, regardless of variations of the initial thickness thereof.

   From monk the finger of the guide mechanism can be coordinated with the different rollers which can be mounted on the carriage to produce different articles the blank is supported adjustable on the carriage, not only in view of the precision of its positioning relative to the spindle and to the tail piece but also to allow the use of very different debauchery.

   The positioning precision and operation of these parts are enabled by several mechanical and hydraulic components to eliminate backlashes or dead races, components including the use of high capacity antifriction bearings with prior load, between the bench and the carriage, between the carriage and roller supports and, at other points, the introduction of a compound screw device with balance of forces in the adjustment, driven by motor, working rollers, and the use of a hydraulic system to actuate and control several parts of the machine, the cylinder of this system being integrated in the carriage so as not to be affected by the relative movement of the carriage and the bench,

   and the use of the hydraulic system to provide automatic hydraulic balancing of the bearings for the absorption of the axial thrust on the spindle and the tail piece, most of the above features of the invention and others still being coordinated not only by construction but operative, several functioning according to a predetermined cycle and can be modified at will *
The invention also extends to the characteristics resulting from the following description and the appended drawings as well as to their possible combinations.

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   The description relates to embodiments of the invention given by way of examples and shown in the accompanying drawings in which: 1 a. Figure 1 is a side elevational view of a machine tool constructed in accordance with the invention, the parts being shown in the position they occupy just before the rollers begin to work the blank.



   FIG. 2 is a partial elevational view showing certain studs connected to the bench and adapted to actuate a control valve on the carriage with a view to stopping its movement * - 1a. FIG. 3 is a plan view of the machine of the invention, the parts being in the position that they cocouple just before the rollers work the blank.



   - Figure 4 is a section on an enlarged scale by 4-4 of Figure 1.



   - Figure 5 is a partial elevational view in section, the parts being in the occupied position after the rollers have finished working the blank, a formed object being shown on the tool or spindle.



   - Figure 6 is a partial plan view of -figure 5.



   - Figure 7 is an enlarged view of one of the roller supports.



   - Figure 8 is a vertical section through 8-8 of Figure 7 showing in particular the roller adjustment mechanism relative to the axis of rotation of the spindle.



   - Figure 9 is a vertical section through 9-9 of Figure 7 showing in particular the mechanism for adjusting the roller in a general direction curved with respect to the axis of rotation of the spindle.



   - Figure 10 is a vertical section through 10-10 of the, Figure 7 showing the adjustment mechanisms of a roller in

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 a direction transverse to the axis of rotation of the spindle.



   - Figure 11 is a view of certain parts of the blank support (seen from the left of Figure 1), view taken along 11-11 of Figure 12.



   - Figure 12 is a vertical section through 12-12 of Figure 11.



   - Figure 13 is a sectional plan through 13-13 of Figure 11.



   - Figure 14 is a plan section through 14-14 of Figure 15 showing the relationship between the tail piece and the carriage when the latter is at the end of its stroke towards the rear of the machine in the reserve position. , the tail piece being pushed forward but its movement being limited by a stop not shown * - figure 15 is a cross section through 15-15 of figure 17.



   - figure 16 is a partial elevational view looking to the left of figure 15 and showing a set of gears for manual control. - figure 17 is a longitudinal section of the tail piece at 17-17 of the Figure 14 and showing in particular the relationship between the carriage and the tail piece when the carriage is at the end of its forward stroke when the rollers have finished forming the object.



   - Figure 18 is a partial section enlarged by
18-18 of Figure 19 showing the bearing device for the rotary head of the tail piece.



   - Figure 18a is an enlarged partial view of certain parts of Figure 18.



   - figure 19 is a section through 19-19 of figure 18 showing how the tail piece is drilled to allow the passage of the fluid - figure 20 is an enlarged vertical section of the

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 guiding device valve.



   - Figure 21 is a longitudinal section broken through 21-21 of Figure 3, showing a mechanism for adjusting the template relative to the axis of the spindle.



   - Figure 22 is an end view looking to the left of Figure 21.



   - Figure 23 is a longitudinal sectional elevation taken along lines 23-23 of Figure 3, parts of this figure being broken away.



   - Figure 24 is a longitudinal section through the head part of the machine through 24-24 of Figure 25 showing the arrangement of the bearing and the drive mechanism of the spindle.



   Fig. 25 is a partial cross section through 25-25 of Fig. 24, showing the gear for driving the spindle.



   - Figure 26 is a longitudinal section through 26-26 of Figure 25, showing the clutch and brake mechanism of the spindle drive.



   FIG. 27 is a diagram in the direction of arrow 27-27 of FIG. 5 showing certain mechanisms for locking the control nut of the carriage when the machine is intended to be maneuvered by hand to move the carriage.



   - Figure 28 is a longitudinal section through a program valve of the hydraulic system.



   - Figures 29 to 33 are cross sections of the valve Figure 28 indicated by 29-29 to 33-33 in Figure 28.



   (Figure 34 is an end view of the program valve looking to the left of Figure 28.



   - Figure 35 is a diagram of the hydraulic control system * - Figure 36 is a diagram of the .la control system. head part of the machine.

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   - Figure 37 is a diagram showing some electric motors.



   Figure 38 is an enlarged view of the spindle bearing arrangement; Figure 39 is a diagram showing some of the variable fluid passages or recesses of the hydraulic spindle thrust bearing.



  General description of the thing
In FIG. 1, the machine comprises a longitudinal bench 1 which carries, at one end, a head piece 2 which supports in rotation and preferably drives a spindle 3.



  On the bench 1 is also mounted a carriage 4 adapted to be driven upward and backward along the axis of the bench. The carriage carries a resiliently mounted tail piece 5. The carriage also carries two roller supports 6 and 7 (figure 3) which carry the rollers 8 and 9. The roller supports are adapted to be moved outwards. and inwardly with respect to the axis of rotation of the spindle by means of a guide control mechanism 10.

   On the carriage is also mounted a debauchery support 12 adapted to carry a blank B to work (fig.l). On the east bench, also mounts a template support 14 carrying a template 16., the support being elastically engaged with the carriage except when it is blocked on the bench (fig. 3). The position of some parts when the rollers have formed a blank into an object 0 is shown in fig. 5.
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  Detail descrintion The bench -
As can be seen better fig.4 .. the bench has a cross section in H, with two side wings 18 and 20 and a transverse web 22 which extends all along the machine (fig.l and 3). All the bench elements mentioned above are made of relatively heavy rolled steel and are welded together

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 to form a single rigid structure capable of withstanding the thrusts imposed by work.



   The H-shaped arrangement creates a channel 26 which receives the lower part 28 of the carriage 4 (fig. 3 and 4). Inside the channel are mounted two vertical supports 30 and 31 each of them extending along the channel. These supports are fixed to the wings and the web by welding. Tabs 32 and 33 are fixed to the vertical .supports by means of bolts to be easily removable.



   The bottom 22 also carries a tongue 34 which extends along the channel in a manner analogous to the tongues 32 33.



  The ridges of tongue 34 are hardened and it is secured to 22 by bolts (not shown.



   Carriage
The trolley (fig. 3 and 4) has a lower part
28 which is housed in the channel 26, an upper part comprised between the transverse guide 35 for supporting the roller and a box body 36 housed to the right of the transverse guide
35 (fig. 3 below).



   The lower part 28 is U-shaped and comprises wings 37 and 38 and a bottom 39. The wings and the bottom extend longitudinally of the channel (Figs. 3 and 4). Several transverse belts 40 (fig. 23) are welded on the bottom and on the wings.



   The right side of the lower portion (fig. 4) is provided with an upper row of two self-aligning roller bearings comprising the bearings 42 and 44 (fig. 1) and a corresponding row of two lower bearings 46 and 48 These rollers are adapted to cooperate with the upper and lower surfaces of the guide tracks 33.

   Preferably, the lower row of rollers has a preloading mechanism (not shown). Likewise the other side of the

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   partial lower is provided with an upper row of two rollers 50 and 51 and a corresponding lower row of two rollers, one of which is shown in 52 fig.4, and both on the pin 23. These rollers cooperate with the track 32 and the lower torque has a preloading mechanism
The bottom 39 is provided with a row of two bearings comprising rollers 53 and 54 (Fig. 1 and 4) and a corresponding row of two rollers 55 (Fig. 4 and 23).

   These rollers cooperate with the edges of the tongue 34 and the rollers of one of the rows are provided with a preloading mechanism (not shown).



   The combined use of rolled steel plates welded together into U-shaped structures, joined together by anti-friction bearings is an important feature of the invention, particularly as an application to a machine tool which ordinarily provides for movement and sliding of a carriage on a bench by means of V-section blocks or the like. The total weight of the cart can be in the order of several thousand kilograms and the cart can however be pushed along the bench to. hand when its drive is disconnected.

   The arrangement not only provides this exceptional degree of anti-friction, but it is also able to maintain the centering of the carriage in the bed despite the very large thrust exerted due to the operating pressure which can. in some cases up to 30 tonnes.



   The cart body 36 is box-type and constructed with rolled steel plates welded together. It is fixed on the lower part 28 by welding at 36a (FIG. 23) '. As seen in fig. 4 the body portion 36 has two upwardly extending parts 56 and 57 which form a central channel inside which the tail or tailpiece 5 is mounted.

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   As seen in fig. 3 the part 56 carries the electric motors 58, 59 and 60 which are respectively connected to the pumps 58a, 59a and 60a. These respective pumps drive the hydraulic motors for the work roller supports by driving the carriage and supply the working pressure for the hydraulic system. The lower part of the body 36 acts as an oil reservoir for the pumps, the level being indicated at L (fig. 1 and 23). This part of the body may also carry an oil cooling device (not shown).



   The force for the electric motors 58, 59, 60 is provided by a trolley system which slides along the bench at a sufficient distance, the power being able to be taken for any position of the carriage along the bench. The motors are respectively connected to the trolley bars by wipers. These connections are shown schematically in fig. 37 but not indicated in detail.



   Providing the reservoir, pumps and motors of the hydraulic system on the mobile cart is an important feature of the invention. In this way flexible lines are eliminated which is desirable since such lines swell and are of relatively short service life. The swelling of the pipes does not allow precise control, as will be explained below. In addition, the use of an auxiliary oil tank is avoided, thereby reducing the area occupied by the machine.
The transverse guide 35 (fig. 3 and 23) is mounted on the lower part of the carriage.

   It has a U-shaped cross section with wings 62 and 64 and a bottom 66 which forms a U-shaped channel 68 in which the bases of the supports 6 and 7 of the working rollers 8 and 9 are arranged. As seen in fig. 4 the ends of the channel-68 are closed by end plates 65 'and 67.



  The above elements are constructed of rolled steel plates and are welded together to form a sturdy structure.

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   The transverse guide is connected to the lower part of the carriage by insertion into a recess 69 (fig. 23) hollowed out in the upper part of the bottom and receiving the bottom plate 66 of the guide structure, which is fixed to the wings 37 and 38 and to spacers 40 by welding.



   The cross guide has vertical supports
71 and 72 which extend over the entire length of the channel 68 and are welded to the wings 62 and 64 and to the bottom 66. The supports
71 and 72 respectively carry tongues or rolling plates 73 and 74 which are fixed thereto by bolts. The bearing plates 73 and 74 are tempered to provide a support surface. Another bearing guide 74a is welded to the bottom 66.



    Support, Roller - Support 6 for forming roller 8 includes side pieces 75 and 76 and a bottom piece 77 (fig. 23) and spacers 78 and 79 (fig.4). All of these components are rolled steel and welded together to form a sturdy whole.



   The side part 75 carries an upper row of self-aligning bearings 80 and 82 (fig.3) and a lower row of two pali ',,' one of which is visible at 86 (fig.23).



   These rollers are adapted to engage on the track 72 and the inner rollers are provided with a mechanism (not shown) for preloading. Likewise the room. lateral
76 carries an upper row of rollers 88 and 90 (fig.3) a lower row, one of which is visible at 92 in fig.23. These rollers cooperate with the raceway 74 and the lower rollers are provided with a mechanism for prior loading.



   The bottom part 77 carries two rows of bearings, one with the rollers 93 and 94 (fig.4 and 23) and the other with the two rollers, one of which is visible at 95. These rollers are adapted to cooperate with the raceway 74a on the base plate 66 and

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 the rollers 93 and 94 are provided with a mechanism for pre-loading.



   The support is provided with an upper plate 96 comprising a housing 97 in which the side pieces 75 and 76 and the transverse pieces 78 and 79 are housed, the upper plate being welded to these pieces.



   The structure of the support 6 of the forming roller 8 is identical to that of the support 7 for the roller 9.



   The shape of the transverse guide and the roller supports with the means for fixing these elements together is of the same type as that of the carriage and lower part of the bench.



     The anti-friction sliding qualities are valid here.



   Mechanism runs the movement of ealet brackets.



   In Figure 4 a guide screw 100 is disposed in the transverse guide and extends through each roller support. The threads 101 of the screw correspond to the nut 102 which is fixed to the transverse member 78. The threads 104 of the screw (which are in the opposite direction to the threads 101) correspond; with the threads of a nut 105 which is supported by needle bearings 106 mounted in the transverse support 107 of the roller support 7. The nut extends outward to the right and terminates in a collar 108 ', to which the wheel is attached. worm 109 using suitable bolts. The nut also carries an anti-friction bearing 111, the rings of which carry between the transverse member 107 and the worm wheel 109.

   Each of the nuts 102 and 105 is of the anti-friction ball type.



   As seen in Figure 10, the worm wheel 109 cooperates with a screw 112 which is keyed on a vertical shaft 113 supported in the top plate 114 of the cup holder 7.



  The shaft 113 is mounted as follows
The shaft 113 is supported rotating in bearings 115 mounted in the sleeve 116 which has a head 120, bolt-

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 born on the upper plate 114 by several bolts 121.



   The head 120 carries an annular group of bosses
122 which cooperate with bosses 123 on the disc 124 fixed on the shaft 113. On the top of the shaft 113 is mounted an adjusting bolt 125 and a cap 126 is disposed between the button and the disc 124. The bottom of the shaft 113 carries a collar 130 and a spring 129 is disposed between the collar 130 and the screw 112.



   It can be seen that if the knob 125 is lifted so that the bosses 122 and 123 are released, the shaft can be rotated which in turn turns the wheel 109. Adjusting the knob moves the support of the wheel. roller 7 towards the inside or the outside of the transverse guide.



   In figures 3 and 4, the end plates 65 and 67 of the transverse guide carry hydraulic motors 131 and 132. The motors are connected with the guide screw by means of couplings, one of which is designated by 133 fig.4 .



  The function of the coupling is to transmit torque from the motor to the shaft without any axial opposing force. Thus the guide screw is free to move slightly axially as regards the couplings. The motors 131 and 132 are of the standard type, being able, when not acting, to have sorotor blocked against any rotation.



   The roller supports can therefore be moved inwards and outwards in unison under the control of the motors 131 and 132. When the motors are stopped the roller holder 6 is fixed with respect to the transverse guide, while the roller support 7 can be moved inwards and outwards by means of the button 125. The operation is as follows:
The nut 102 is fixed against rotation on the roller support 6 'and the nut 105 is also fixed against rotation on the roller support 7 because of the engagement of the wheel 109

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 and screw 112 (fig. 10).

   Thus, when the engines 131 and
132 are on, the guide screw begins to turn and the nuts move or advance along the threads of the screw carrying the roller supports.



   When the motors 131 and 132 are cut off, the guide screw is fixed against any rotation. Thus, if we pull the knob 125 upwards to release the bosses 122 and 123 and that we turn it, the wheel 109 will be driven in rotation by the screw 42. This turns the nut 105 and, like the steering screw does not rotate, the nut will move on the threads, bringing with it the roller support 7 and the roller 9. The arrangement is such that the roller 9 can be adjusted with a precision of the order of two hundredths of a millimeter. The head 120 (fig. 7 and 10) is provided with a graduated scale 127 and the cap 126 is calibrated with an index which indicates the size of the adjustment.



   One of the features of the invention is the fact of having an adjustable roller support relative to the other. The roller 8 carried by the support 6 can be fixed in a predetermined radial position with respect to the axis of the spindle, and thus the roller 9 carried by the support 7 can be adjusted very precisely, of the order of a few. hundredths of a mm. in a corresponding radial position. Thus the rollers can be radially centered with precision around the axis of the spindle. This reduces the risk of unwanted forces on the spindle during work due to misalignment of the rollers. In addition this promotes the possibility for the machine to produce objects of precise dimensions.

   A mechanism is also provided for moving the roller 7 in a direction parallel to the axis of rotation of the spindle, as explained below.



   Another mounting feature of the roller brackets is that the brackets are resiliently held

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 on the cross guide. In fig. 4 the transverse guide has a vertical member 134 which is drilled at 135 to receive the guide screw 100. A central annular shoulder
136 fixed on the screw divides the opening into two parts.

   In the left section are arranged roller bearings 140 which are held against the shoulder 136 by a spring 141 bearing against the plate 142 which is bolted to the member 134. On the right side, the bearings 143 are held against the plate. 145 which is bolted to the member 134. As mentioned above the couplings which connect the steering screw to the hydraulic motors 131 and 132 allow slight axial displacement of the screw. Thus it is seen that the roller supports 6 and 7 can be moved in unison slightly forwards and backwards with respect to the transverse guide, the movement being controlled by the springs 141 and 144.



      This mounting axially .: elastic of 'the guide screw allowing a common elasticity of the roller supports is a characteristic of the invention * For example, if the two rollers are not initially perfectly aligned at the same radial distances from the axis of' spindle, there will be a slight radial thrust exerted on the spindle as the roller moves along the axis for. work on a draft. However, in the event of no adjustment, the assembly of the invention allows the rollers to center themselves relative to the spindle and the only radial force is that of the springs, which is of minimal order.



  In addition, the roller system yields elastically and follows the deformation of the spindle if it occurs, thus avoiding unwanted radial forces.



   The drive mechanism for the roller supports also includes means for compensating for the clearance between the threads of the guide screw and the nuts. This is achieved by means of a hydraulic system comprising a cylinder 146 (parallel to the screw) which is fixed in an opening 150-en

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 vertical member 134. A piston 151 is attached to the plate 152 by a bolt 153 which in turn is attached to the transverse member 78 by bolts 154. A piston 155 is likewise attached to the transverse member 107 of the wheel support 7.



  The hydraulic fluid is introduced into the chamber 156 of the cylinder at a pressure sufficient to push the pistons outward fig. 35. This tends to move the roller brackets outward. As a result, the threads of the nuts 102 and 105 engage without play with the threads of the guide screw.



   Means for mounting the rollers on the supports.



   As can be seen in Fig 3 the roller 9 is mounted on a segment-shaped block 160 which is mounted in. a segment-shaped plate 161 which in turn is mounted on the upper plate 114 of the roller support 7.



   As seen in fig. 7,8 and 9 la. table has a lower portion 162, 162 and an arcuate surface 163 carrying the roller block 160. In FIG. 7 The outer edge of the lower portion 162 carries several bolts 164 which extend through the lower portion and engage the threads in the upper plate 114. Where these bolts are. tight down without play, the table is rigidly fixed to the top plate.



   The table is adjustable relative to the upper plate by the following mechanism:
The upper plate 114 is provided with a groove 114a which extends parallel to the axis of rotation of the spindle.



  Table 161 carries a shoe 162a which extends along groove 114a and is secured to the top plate by bolts 165-165.



   As seen in fig. 8, the table carries a pin 166 which extends downwardly into an enlarged portion of the slot 114a and carries at its lower end a collar 170 which is secured to the table by bolts 171-171. A connecting rod 172 is rotatably supported on the collar by the bearings 173.

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   The connecting rod 172 extends rearwardly through the enlarged portion of the slot and is connected with the shaft 174 by the bearings 175. The shaft 174 is mounted in the bearings 176 disposed in the annular member. 180 which is rigidly connected with the top plate 114 by means of bolts 177-177 (fig. 7).



   The shaft 174 carries an adjustment knob 178 which is attached to the shaft by adjustment screws (not shown). The annular member 180 carries a group of annular bosses 181 which are adapted to mesh with an upper member. annular
183 fixed to button 178 by 'bolts. 186. The cap 185 is connected between the ring 183 and the button. The bottom of the shaft carries a collar 190 bolted to it and on which is supported a spring 191 bearing against the collar and the underside of the upper plate 114.



   In Figures 7 and 8 the lower portion 192 of the shaft is slightly off-center with respect to the axis 193 of the shaft. Knob 178 can be pulled up to disengage bosses 181 and 182 and rotate the shaft. Since the lower end of the shaft 192 is off-center, a movement will be made to the connecting rod 172 and that movement will be transmitted to the table 161. Thus, if the bolts 164 are loosened and the knob 178 , turned, the table can be moved in a direction parallel to the axis of rotation of spindle 3.



   Usually the bolts 165 which secure the table shoe 162a in the top plate slot 114a (Fig. 9) do not press the shoe enough against the slot to oppose the table movement.



   The amount of movement of the table for a complete rotation of the button 178 is very small because the eccentric is very slightly off-center. Thus the roller 7 can be adjusted in a function, parallel to the axis of rotation of the spindle with a '? qrecision of the order of a hundredth of a mm. The 180 ring is

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 provided with a graduation 194 and the cap 185 is provided with a calibrated index 195 (fig. 7) to indicate the setting value.



  This adjustment, like that described above for moving one roller radially relative to the other, is important to avoid unwanted forces on the spindle and to increase the precision of parts produced by the machine.



   The roller block 160 is mounted on the table in the following manner (fig. 7,8 and 9). The surface 163 of the table is provided with two arched slots 196 and 200. The slot 200 has an upper portion 201 and a lower portion 202, the upper portion being enlarged a little *
As shown in fig. 9 a shoe 203 is disposed within the slot 196, and is adapted to be pulled up against the sides of the slot by means of bolts 204-204, extending through the block 160. The lower portion 202 carries a shoe 205 adapted to be pulled up against the slot by bolts 206-206 (fig. 7). Thus, when the bolts 204 and 206 are locked, the roller block 160 is fixed relative to the table.



   The roller block 160 is movable for adjustment relative to the table by means of the mechanism below (fig. 7 and 9). The upper slot 201 carries a gear sector 210 which is fixed in the slot by screws 211-211. A tree '212 is mounted in block 160 and door to. its lower end a pinion 213 which meshes with the sector 210. The shaft also carries a worm wheel 220 which meshes with the screw 221 supported on the shaft 222. The outer end of the shaft carries a handwheel. hand 230.



   When the bolts 204 and 206 are loosened, the handwheel can be rotated and the roller block 160 can be moved in an arc relative to the table 161.



   The arc adjustment of the rollers described above is a characteristic of the invention. The layout allows the? -

  <Desc / Clms Page number 23>

 rollers to pivot around predetermined points relative to the spindle axis. In this way the axis of rotation of a roller can be oriented as desired with respect to the axis of rotation of the spindle. Marker means are provided to control the adjustment, for example on a graduated scale on the block with a mark on the table.

   In fig. 3 it can be seen that the pivoting of a roller does not affect its path during the forming operation * For example if, in the position shown., The roller 9 follows a certain path during the forming , the roller will always follow the marl by ,, bear if it is moved in an arc towards the center of the machine.



   The tail piece or headstock.



   This head is (fig. 4) formed by a rectangular frame 231 provided between the vertical portions 56 and 57 of the carriage body. The frame includes a bottom piece 232 and side pieces 233 and 234 with a top piece 235. The pieces
233 and 234 can be attached to the; top and bottom by means of bolts 236 and 237. The frame extends along the channel formed by the parts 56 and 57 and protrudes out of it (fig.3).



   In fig. 14, 15 and 17 the frame portion 231 which extends from the left end (fig. 14-17) almost to the. half the length in the form of a rectangular box bounded by the bottom 232, the sides 233, 234 and the top 235.



   The remaining portion of the frame. its thickened side walls (fig. 14). The thickened portion 240 of the side wall
233 is provided with two longitudinal bores forming the upper and lower cylinders C1 and C4 (fig. 4) and the thickened portion 241 of the side wall 234 is provided with two longitudinal bores forming the upper and lower cylinders C3 and C2.



   It is visible in fig. 17 that the C3 cylinders and
C2 are opposite, i.e. the left end of the cylinder

  <Desc / Clms Page number 24>

 
C3 is closed and the right end is open to receive a piston, while the left end of cylinder C2 is open to receive a piston and the right end is closed * Cylinders C1 and C4 are opposite and identical .



   Between the thickened portions 240 and 241 of the side walls is mounted a box frame 242 (fig.14) which carries an anterior head 243 and a posterior 244 .. fixed to it by welding. The front head 243 carries pistons P.1 and P.2 which are fixed to the head by bolts 245 and 246 and extend towards the rear of the machine and are axially aligned with cylinders C1 and C2.



   The rear head 244 carries pistons P.3 and P.4 which extend towards the front of the machine and are aligned with the cylinders C3 and C4. These pistons are fixed on the head in the same way as P.1 and P.2. The rear head 244 has an upwardly directed portion 250 which is adapted to abut an adjustable screw 251 on the top of the top piece or cover 235 (Fig. 23).



   From figures 4 and 23 and the details of figures 14, '15 and 16 it can be seen that the inner frame 242 and the heads
243 and 244, at the same time as the pistons which are connected to them, can slide relative to the outer frame 231 or to the carriage. The bottom 232 of the outer frame carries a longitudinal keyway 252 in which a key is disposed.
253 attached to the inner frame. This key guides the longitudinal movement of the inner frame and the heads.



   In Figure 14, cylinder C3 is provided with a cap 254 and an oil seal 255 at its left end.



   The C4 cylinder is even provided with a cap and gasket. The open end of the C3 cylinder is provided with an oil seal
256 which allows displacement of piston P.3 through it, and the open end of cylinder C4 has a seal for displacement, of piston P.4.

  <Desc / Clms Page number 25>

 



   The right end of cylinder C1 is provided with a cap 260 and seal 261 which close the cylinder, while the open end is provided with a seal 262 allowing the passage of piston P.1. Likewise for C2 with a seal allowing passage of piston P.2.



   It appears that if fluid is admitted to the cylinders C1 and C2, the pistons P1 and P2 will be moved forward, which also forces the frame 242 to move forward. In the arrangement of the hydraulic system, a holding pressure is maintained in the cylinders C1 and C2 to urge the inner frame forward. This frame carries the rotating head 270 of the tail piece. Thus the head is pushed forward or towards the workpiece head.



   The position of the head 270 can be adjusted relative to the roller carriage by the mechanism described below:
As can be seen in the upper part of fig.4, the extension 235a in the box structure of the member 235 carries a button 271 connected to a shaft 272 supported in the part 235a and carrying a worm 273. In fig. . 23 the screw 273 meshes with a wheel 274 which is carried by the shaft 275.



  At one end the shaft is supported in the bearings at. needle 276 carried by the sleeve 280 which is fixed on the part 235.



  Between the worm wheel 274 and the sleeve 280 are disposed thrust bearings 281. Another bearing 282 is disposed on the shaft 275 between the sleeve 280 and the locking nuts 283.



  The other end of shaft 275 is grooved at 284 to engage with splines 285 of screw 251. Screw 251 is screwed into part 235. If we turn knob 271, screw 251 can be moved. axially forward or backward.



    By operating the button 271, the position of the rotary head 270 with respect to the rollers can be adjusted. A graduation 287 is provided on part 235a and button 271 marks a mark 238 (fig. 17) to indicate the setting value.

  <Desc / Clms Page number 26>

 



   The relative position of the carriage and the tail piece when the carriage is at the end of its rearward travel is shown in fig. 14. The fluid supply of the cylinders C1 and C2 is connected to the discharge of a pump and the pressure pushes the pistons P.1 and P.2 forward until the stop 250 on the head 244 engages with screw 251. The fluid supply for cylinders C3 and C4 is connected with the inlet side of the same pump. As the carriage moves forward the tail piece moves with it until the rotating head 270 is held against further forward movement by its engagement with the blank carried by the spindle.

   The pressure in C1 and C2 keeps the head against the blank. When the cbariot moves forward to force the rollers to work the roughing, the cylinders C1 and C2 slide on the pistons P.1 and P.2, while the cylinders C3 and C4 move away from the pistons P. 3 and P.4. The oil displaced in cylinders C1 and C2 effects a corresponding oil pressure in cylinders C3 and C4.



   After the blank has been formed, the carriage reverses its direction, but the rotating head of the tail piece remains fixed against the blank due to the holding pressure retained in the cylinders CI and C2. When the carriage continues its return movement, the oil in cylinders C3 and, 04 is discharged and there is a corresponding oil charge in cylinders C1 and C2 the holding pressure present in cylinders C1 and C2 causing the rotating head of the tail piece to hold against the finished object until the adjusting screw 251 engages with the stopper 250. At this point the tail piece is pulled back with the carriage .

   The manner in which the oil is charged and discharged will be described below with the hydraulic control system of the truck.



   In conjunction with the function of clamping a blank 'on the. spindle by means of the rotating head 270, it should be noted that

  <Desc / Clms Page number 27>

 the pistons and cylinders providing the clamping thrust are arranged symmetrically so as to eliminate the possibility of any forces applied to the axis of rotation of the head.



   As seen in Figures 4 and 15, the piston P.1 and the cylinder C1 are in a plane containing the axis A of the inner frame 242, this axis coinciding with the axis of rotation of the head 270. The piston P .2.and the cylinder C2 are in the same plane and at the same radial distance from the axis A as Pl and Cl. The piston P.3, the cylinder C3 and the piston C4 with the cylinder C4 are likewise arranged in another plane containing the axis of rotation of the head 272.



   , The unit pressure in Cl and C2 is the same and the surfaces of the heads of the pistons P.1 and P.2 are equal - It follows that with the symmetrical arrangement, the equal forces exerted by the pistons act at the same radial distance from axis A.



   The fact that the tail piece is resiliently supported with respect to the carriage or to the rollers constitutes one of the characteristics of the invention. This arrangement allows automatic compensation for variations in the thickness of the blanks. For example, if a pass is made with a blank of 10 mm thick and a blank is presented with a greater or lesser thickness, no adjustment of the headstock is necessary for the rotary head to perform the 'tightening operation,
Further, the carriage and the headstock can be associated with each other rather than being constituted as independent parts carried by the bench. This results in several advantages.

   For example, the overall size of the machine is reduced, which is advantageous from the point of view of economy of occupied area.



  In addition, the distance between the contact surface of the rotary head and the bearings by the head can be considerably reduced.



  Thus, any unwanted axial thrust which may be imposed as a consequence of a long shaft is eliminated. In addition, the arrangement allows the rotating head to be held in the clamping position.

  <Desc / Clms Page number 28>

 against a finished object while the spindle is brought back to a standstill. It is reminded that, after the blank has been formed into a finished article, the carriage stops and moves back to the rear of the machine. During the first part of this movement the spindle and the finished object slow down their rotation. If the object is not clamped until the rotation is stopped, it may separate from the spindle and cause personal injury! or by machine.



   In addition the. arrangement allows automatic running at high speed. For example, the coordination between the carriage and the head against forces the latter to clamp the blank before the rollers start forming, without the intervention of any additional device.



   The rotary head 270 is supported as follows (Fig. 23). This head comprises a conical section 290 and a cylindrical section 291 provided with a collar 292 abutting against a shaft 293 and fixed on it by bolts 294, The shaft 293 extends rearwardly through an opening 295 provided in the head 243 and then inside the inner frame 242 where it is supported by roller bearings 296. The bearings 296 (fig. 18) are supported on the shaft by a spacer 297 which abuts on a surface 298 shaft and locknuts 300 (fig. 23) secure the bearings against axial displacement on the shaft.



   The bearings 296 support the shaft and the rotating head and provide for the absorption of radial thrusts on the head or the shaft. From Figures 18 and 23, it follows that the rings and rollers of bearings 296 are so arranged that the inner rings and rollers can move slightly axially. As a result, the shaft 293 and the inner frame 242 are axially movable with respect to each other. The purpose of this displacement will be explained with the description of the hydraulic thrust bearing which will be given later.



   It is recalled that the hydraulic pressure pushes the Inner Frame 242 forward, and consequently pushes

  <Desc / Clms Page number 29>

 
1, the shaft 293 and the rotary head 270 forward and the head remains stationary against the blank as the carriage moves forward for the forming operation. When the head is engaged with a blank on the spindle, the axial thrust is absorbed by a hydraulic thrust bearing 301 (Fig. 1 $) which has the form of an annular chamber which exerts pressure between the head.
243 of the inner frame 242 and the shaft 293.



   The chamber forms a cushion, so to speak, between the rotating head 270 and the inner frame 242 and allows the head to rotate at very high speed while exerting a clamping force of several tons. The bearing not only has tick resistance, but also friction canceling characteristics. As the fluid in the crankcase exerts pressure against shaft 293, the shaft is pushed in the direction of the forward. Roller 'type' thrust bearings 302 'are provided to limit the. axial displacement of the shaft, i.e. to the left in figure 18.



   The bearings 302 include several beautiful 303 which are arranged around an annular surface on the shaft 293. The balls are supported on each side respectively by planar surfaces on the head 243 and the spacer 297. These surfaces being planes are real thrust faces. Around the balls is arranged a ring 304 provided with a groove for the balls. The ring is arranged to fit without play on the balls so that when the latter rotate the ring rotates with them that is to say that the balls and the ring rotate as a unit at the same angular speed .



   Note that the spacer 305 and the head 243 are constructed to form an annular chamber 305 'which is wider than the. ring 304, so that the ring and balls 303 can move slightly axially with the shaft? 93, the movement to the left being limited by

  <Desc / Clms Page number 30>

 the engagement of the balls with the head 243 and the part 297 and the movement to the right being limited by the hydraulic thrust bearing 301.



   The arrangement described above has the great advantage over ordinary roller bearings that, as the balls rotate, centrifugal force tends to move them outward against a concave bearing race as well as against the cage. Thus considerable frictional forces are created which result in heating and shortening of the service life and the resistance characteristics to load and speed. On the contrary, in the device described, when the balls rotate, the centrifugal force pushes them outwards against the ring which surrounds them without play and the ring and the balls rotate together.

   Thus there is little heat generated by the relative movement of the balls and the ring. While the balls can turn on themselves during their rotation, the rate of turn is much lower than the rate of rotation. . As a result, the heat released by engagement of the balls and grooved raceway 304 is low.



   The construction of the hydraulic thrust bearing 301 is as follows (Figs. 18 and 18a). Shaft 293 has a mirror polished annular surface 306. On the head 243 is provided an annular surface 310 provided with a planar annular surface 311. This surface is also mirror polished. The head carries a second surface 312 with a polished annular surface 313. Thus, an annular chamber 314 is formed between the surfaces and the surface 306 which is disposed between two annular spaces 320 and 321.



   If hydraulic fluid is admitted to annular passage 315, it will flow into chamber 314, and thence through spaces 320 and 321, between surface 306 and surfaces 311 and 313, so that the shaft 293 and head 270 will be pushed forward. It is recalled that the pressure in the cylinders C1, C2 constantly pushes the head 243 forward. It results

  <Desc / Clms Page number 31>

 aue, when the rotary head 270 engages a blank 0 on the broch the head 270 and the shaft 293 stop but the head 243 continues to move forward and the spaces 320, 321 tend to close. . This causes an increase in pressure in the chamber.



   314. The fluid supplied to the chamber 314 is in parallel with the fluid supplied to the cylinders C1 and C2 and the unit pressure in the chamber 314 tends to rise towards the pressure in the cylinders C1 and C2, which makes open the spaces The unit pressure in the chamber 314 can never be equal to that in the cylinders due to certain drops caused by constrictions in the pipes connecting the chamber 314 with the cylinders C1 and C2. However, the annular wall surface of the chamber formed between the inner ends of the surfaces
311 and 313 is approximately double the effective area of the pistons P.l and P.2. Thus the force exerted to keep the spaces 320 and 321 open is greater than the force which tends to close them.

   Thus, the spaces remain open and the axial thrust is a.bsorbed by a fluid cushion.



   The fluid coming from the space 320 flows into the chambers through the caps 307 attached to the head 243 and from there through orifices 308 (Fig. 23) which lead it to the tank of the cart. Fluid from space 321 flows through annular chambers 309 (Figs. 18 and 23) which are in communication with orifice 308.



   The annular surface 306, the annular surfaces 311 and
313 and thrust bearing 302 are constructed such that shaft 293 is moved all the way to the left (Fig. 18). The width of the spaces 320 and 321 is between 2 and 5 hundredths of a millimeter, preferably 4 hundredths. During the forming process, the width of the space is of the order of 12 thousandths of a mm. The length of the spaces 320 and 321 measured along the surfaces 311 and-313 is also small, on the order of 0.25mm or less.



  This very short length has the effect of reducing the resistance

  <Desc / Clms Page number 32>

 due to viscosity, which is created by the flow of fluid through a space. With low viscosity resistance the efficiency of the bearing is very high, especially in comparison with a roller type thrust bearing. Furthermore, this low viscosity resistance allows the head 270 to be driven at very high rotational speeds. '
The fluid connections for supplying cylinders C1, C2, C3 and C4 and hydraulic thrust bearing 301 are as follows (Figs. 14 and 15). The side pieces 233 and
234 of the outer frame 231 are provided with vertical bores
322 and 323 and. horizontal communication bores 324 and 325 opening respectively into cylinders C1 and C2.

   The ends of bores 324 and 325 'have plugs 324' and 325 '. The lower ends of the bores 322 and 323 opening into the body of the carriage are connected with the discharge side of the feed pump of the carriage.



   Cylinders C3 and C4 are connected with like bores 326 and 327 (Fig. 14) which are interconnected with the supply side of the pump of the cart.



   From Figures 14 and 18 the piston P1 has a longitudinal bore 328 which is aligned with a horizontal bore
329 (Fig. 19) of head 243. Bore 329 is in communication with passage 315 and carries a throttle valve 330 which is screwed into bore at 331 whereby the valve can be adjusted. . A plug 332 is provided to close the bore.



   Fluid in cylinder C1 can flow through bores 328, 329, passage 315 and into the annular chamber
314 of thrust bearing 301. The unit pressure drops between cylinder C1 and chamber 314 and can be adjusted by axial displacement of valve 330.



   One of the first purposes of the valve is to restrict the flow. fluid to such an extent that the unit pressure in the cylinders C1 C2 is maintained above a certain

  <Desc / Clms Page number 33>

 desired limit, and also to prevent large amounts of oil from flowing through the hydraulic bearing when the head is not against the blank or finished article.



   Providing these bores avoids flexible pipes.



   Rough support:
The blank support 12 is mounted on the carriage (fig.ll,
12 and 13). The side piece 62 of the roller support guide 35 (Figs. 3 and 23) carries a vertical plate 341 which abuts against the bottom 39 of the lower part of the carriage. The plate 341 is fixed to the part 62 by several bolts 342 (FIG. 13) and carries a guide 343 of octagonal section fixed by bolts 344. The guide is provided with two bores 345, 346 forming opposed cylinders.



  The cylinder 345 is closed at its upper end at 350 (fig. 11) and the cylinder 346 is closed at its lower end at 351 (fig, 11).



   A frame 352 is slidably mounted on the guide 343 and carries an upper plate 353 which carries a piston 354 fixed to it by bolts 355, the piston being adapted to travel the cylinder 346. The piston 354 (fig. It) is at bottom of stroke in the cylinder. The lower end of the frame carries a plate 356 and a piston 360 is fixed to the plate by screw 361. The piston 360 slides in the cylinder 345 and in FIG. 11, it is at the bottom of the cylinder.



   The actual V-shaped bracket 12 (Fig. 11) comprises a back plate 362 extending downwardly towards the bottom plate 356 at a distance therefrom. The back plate 362 has a vertical key 362 'which slides into the groove 352'. It is held against the frame by an outer plate 363 which is attached to the bottom plate 356 by screws 364 and a hand adjusting nut 365 which has a shoulder 366 bearing against the outer plate 363 and a middle portion 367 which retains. through openings 368 in the plates 362 and 363 and mesh with the thread of the frame 352. When the nut

  <Desc / Clms Page number 34>

 is moved away from frame 352, plate 362 can be moved up and down by the adjustment mechanism described below.



   The back plate 362 carries a V-block 369 and an outer plate 370 attached to this block. The outer plate 370 and the back plate 362 are separated by the V-block, so as to accommodate blanks of varying thickness. In addition, the V-shape of the block adapts to blanks in the form of a disc or of a rectangular or square shape.



   , Vertical adjustment of the holder is provided by means of the mechanism. visible in the right part of fig. 11.



  An L-shaped console 371 is attached to the frame 352 and an ear 372 is attached to the backplate 362. The ear has a set screw 373 that freely engages an opening in the arm. The upper part of the screw 373 carries a collar 374 on which the ear 372 bears and the lower part of the screw is screwed into a thread of the console 371. Thus, when the nut 365 is moved back as 'said above ;, the: screw 373' can be turned to move the blank support towards the. up and down.



     The 'frame 352 which carries' the blank holder 12 is adapted to be moved up and down by the fluid in cylinders 345 and 346. As fluid is introduced into cylinder 345, piston 360 moves down, which moves the frame and roughing support down. If, fluid is introduced into cylinder 346, piston 354 is moved upward carrying the blank holder.



   The blank support forming an integral part of a mobile carriage is a characteristic of the invention.



   This has many advantages. For example if using pins of various lengths it is not necessary to make an adjustment of the roughing support in one direction along the longitudinal axis of the bed for the support to hold a roughing correctly in relation to the head of the spindle * In addition,

  <Desc / Clms Page number 35>

 the hydraulic system for moving the roughing support up and down can be an integral part of the carriage, this yes has many advantages.



   Template support.



   The side piece 20 (fig. 1 and 4) of the bench is provided with two longitudinal guides 376 and 377 inside which is mounted a longitudinal slide 380 which extends at the rear in the guides to a point in rear of the carriage in 380a (fig. 1); on this slide 380 are fixed two uprights 381 and 382 with U-section.



   The post 381 includes wings 383, 384 and a front face 385, the wings being fixed to the slider 380 by welding.



  The wings and the core are connected together by an upper part 386.



   The post 382 comprises wings 390, 391 and a front web 392. Fenders are welded to the slider 380, and connected together with the web by a 'top piece, 393., Provided (fig. 21)' with a tail. dovetail 39.4.



   In fig. 3 the template 16 is carried by an arm, 395 pivotally fixed at 396 on another arm 395 'pivotally mounted on the upright 381 at 396'. The adjustment of the arm 395 around the pivot 396 serves for the coarse adjustment of the jig relative to the axis of rotation of the spindle, while the fine adjustment is made by pivoting the arm 395 'around the spindle. 'pivot) 396'.



   The precise adjustment is carried out as follows: the upright 381 comprises a cylindrical member 397 with a shoulder 400 yes carries bolts 401 for fixing to the upper part 386 of the upright 381. The cylindrical member 397 carries a pillar roller 402 whose outer cage is housed in an opening of the arm 395 '. The cap 403 which is bolted to the cylindrical member 397 by bolts 404 secures the bearings and the arm to the cylindrical member. -
The 395 'arm is adapted to be moved around the pivot

  <Desc / Clms Page number 36>

 396 'by the following mechanism. The end of the arm is provided with a cylindrical extension 406 on which is mounted a roller bearing 407 carried by a sleeve 410.

   On the bottom of the sleeve 410 is a spindle 411 which carries a roller bearing 412 whose outer cage is provided with a casing 413 fixedly mounted in the slider neck 414 which is dovetailed into part 394 of the part upper 393 of post 382.



  The inner portion 415du slider has a threaded opening 416 and carries a screw 420 fixed to an adjustment knob 421 (Fig. 22) carried by bearing 422 in a bracket 423 carried by the front member 392 of the upright 382.



   If we turn the knob 421, the arm 395 ′ rotates around. of 396 'because the slide 414, being moved, carries with it the spindle 411 which turns relative to the slide by means of the bearing 412, while the extension 406 of the arm moves inward or outward of the slide as allowed by step 407.



   The console 423 is provided with a graduated scale 427 and the button 421 with a mark which indicates the setting of the template with respect to the axis of rotation of the spindle.



   The coarse adjustment is made around the pivot 396 as follows: On the end of the arm 395 ′ is mounted a shaft 427 fixed to the arm by screws 425. The shaft 424 carries the arm 395, the opening 427 constituting a housing for the free passage of the arm. The shaft 424 has a shoulder on which is mounted a disc 430 by screw 431. The periphery of the disc 430 is provided with bosses'432. Surrounding the disaue 430 is a ring 430 'also carrying bosses 434 which' mesh with bosses 432.

   An adjustment knob 433 is screwed onto the shaft 424 and carries a shoulder 433 'which bears on the top of the ring 430'. The disc 430 is remote from the knob 433 as indicated at 435.



   By loosening the adjustment knob 433, the arm 395 can be rotated around the shaft 424 and fixed in one position.

  <Desc / Clms Page number 37>

 any tion. When turning the knob down to fix the adjustment, the position of arm 395 is not changed because the knob bears on ring 430 ', which is non-rotating due to engagement of bosses 432 and 434. The disc 430 which carries the bosses 432 is fixed relative to the arm 395 'by means of the shaft and the screws 431 and 425.



   The ring 430 'is provided with a graduation 440 (fig. 3) and the arm 395 with a mark 441 to control the fit of the jig with respect to the axis of rotation of the spindle.



   As said above, the template support is adapted to be held elastically relative to the carriage by the following mechanism:
In Figures 1, 4 and 5, the post 381 carries a cylinder 442 extending through an opening 443. The cylinder of the outer threads 444 bears the nuts 445 and 446 for securing the cylinder to the post. Welded to the main carps of the truck is a bracket 448 which carries the piston 449 with one end disposed in a chamber 450. The piston is secured to the console 448 by clamp and bolts 451 and 452.

   The console 448 has a vertical bore 453 yes communicating with the chamber 450 and is closed at its top by the cap 454. A horizontal bore 455 is also provided in the console and its. Extends into the body of the cart to be connected to certain hydraulic mechanism described later. The horizontal bore 455 is closed at its outer end by a cap 456 (fig. 1). The piston 449 is also provided with a bore 460 which communicates with the chamber 450.



   When fluid under pressure is introduced into cylinder 442, it tends to move to the left (fig. 1 and 5) and causes stop 461 mounted on post 382 to abut against bracket 448 as shown in fig. 1. The stop 461 takes the form of an adjustable screw in the upright 382. When the stops are engaged (fig. 1) the relative positions between the jig and the chardot can be adjusted.

  <Desc / Clms Page number 38>

 



   As the carriage and jig are held in engagement (under the effect of fluid pressure in cylinder 442 and screw stop 461 against consle 448) the carriage moves along the bench. dragged the jig with him. However, if the template is blocked relative to the wobbly carriage can move relative to the template. The jig is locked on the bench by mechanism 459 (fig. 1 and 4) as follows:
One of the locking mechanisms is shown in fig. 4, where it is seen that the side piece 20 of the bench carries a cylinder 462 which extends back inside the channel of the bench through an opening 463 in the support 31.

   The cylinder carries a piston 464 which is urged outward toward the slider 380 by the spring 465 bearing against a cap 466. Fluid is introduced into the cylinder through the ports 470. Several of these locking mechanisms 459 are provided on the same. along the bench as shown in fig. 1.



   Usually the springs push the pistons outwardly against the slide 380 with a small force such that the slide is free to move. However, if pressurized fluid is introduced into the cylinders, the pistons forcefully press against the slide. and block the slide and the jig on the bench.



     The jig is shown to be locked on the bed just after the rotating head 290, the counterhead and / or the rollers 8 and 9 have engaged a blank on the spindle - When setting the machine for a forming operation , a sample blank B is placed in the blank holder 12 and the carriage is moved forward and the rollers are adjusted to engage the blank in predetermined positions relative to the axis of the spindle .

   This is the starting position for the dirt forming operation. The jig is then precisely adjusted to match this starting position,
It is visible that after the rollers and the jig

  <Desc / Clms Page number 39>

 have been adjusted, the units will always follow the same travel paths when the cart is brought to a ladder for drilling. As the jig is not blocked on the bed until the rollers have engaged the blank, the alignment of the starting position of the rollers and the template will remain correct regardless of the variation in thickness of the blanks to be worked.



   The preceding arrangement is characteristic of the invention. In the vast majority of cases, the edges of the finished article must be kept within very tight tolerances, thus any variation in the thickness of a blank to be passed, relative to the thickness of the blank used for the initial adjustment, without the device of the invention would require an adjustment of the rollers and of the template. This is obviously unfavorable. The device of the invention overcomes this difficulty and ensures the desired precision even at high speed running and lends itself particularly well to automatic walking.



   Template follower valve. -
In fig. 20 the. valve 471 includes a main body
473 connected to a bracket 472 (fig. 5) supported by the upper plate 114 of the roller support 7, The body carries two fluid conduits 474 and 475 yes are interconnected with the body
36 of the carriage by telescopic tubes (not shown) and then connected respectively to the drive motors 132 and 131 of the roller supports. The telescopic tubes allow movement of the valve inward and outward with the roller support 7 and the tubes, being rigid, eliminate the need for flexible lines.



   A fluid connection 476 is connected to a trigger finger valve 480 through line 481 and through line
482 to a pilot valve for withdrawing the roller support, the role of which will be specified later. The pilot valve is mounted in the body of the carriage and the trigger valve is mounted on the top plate of the roller support 7 (fig. 4). The pipeline /

  <Desc / Clms Page number 40>

 483 connects the valve 471 to the tank of the cart which is also connected to the trigger valve 480, by a pipe 484. The pipes 482 and 483 are connected by telescopic tubes.



   Inside the main body 473 is mounted an upper disc 485 bolted to the body at 486. Below this disc is mounted a spacer 490 and a lower disc 491, which are bolted at 492. to the disc. superior. The upper disc 485, the part 490 and the lower disc 491 form a
 EMI40.1
 cylindrical chamber 493 in which the slide 495 is mounted.



   Before going any further, it is necessary to describe the various fluid passages formed by the above elements. The
 EMI40.2
 body 473 has an annular passage 496 which communicates with the link 4,1,4 through the passage 500. The upper disc 485 has an annular passage 501 which communicates with the passage 496 via the link 502 . The 'slider 495' has an annular passage
 EMI40.3
 503 which communicates with the'passag.e 5Dé dris. 1é 'o, r s z:

  73 .par.l, a link 505. 'The -p-, ssage 504, is co'nné'eté.a, e the pipe 476 by connection 5061, E a.'. '', ', E te passage 501 (which co'nim'unîque', with., Has qanali sation- 474) is separated! passage 503 (which. is in communication with the '. valve
 EMI40.4
 with trigger and pilot operated valve) -by an annular 6'-d 1, normally open.



   The lower disc 491 has an annular passage 510 communicating via connection 511 with annular passage 512 in body 473. Passage 512 communicates with line 475 via connection 513.



   The passage 510 (which is in communication with the other side of the roller support motors) is separated from the passage 503
 EMI40.5
 (yes is in communication with the trigger valve and the pilot valve) through an annular space G 2, normally closed.



   The slider 495 is supported by a spring 514 bearing on the cover 515 which is bolted at 516 to the body. In addition, slide 495 is mounted on roller bearings 520

  <Desc / Clms Page number 41>

 and 521 yes align the slider on the axis of the chamber 493 etper put the displacement of the slider in the direction of the rise and the descent. The slider has a central bore comprising an upper portion 522 and lower 523, the the lower bore being of smaller diameter and carrying a ball 524. Oil passage holes are provided at 525 in the bottom of the slide.

   A shaft 526 extends upward through the bore
522, supported at its lower end on the ball 524 by a conical opening 530. The shaft 526 is threaded and carries a nut
531 which supports a hemispherical organ or ball 532 which carries. against a cap 533 screwed onto the upper disc 485. The cap has a conical opening 534 in which is disposed the conical member 535 which is part of the spherical member or ball.
532.



   The ball 532 has a vertical slot 527 in which is disposed a pin 528 fixed to the upper disc 485. The pin keeps the ball against rotation about its vertical axis but allows it to rotate both in the plane of the drawing. and in a direction perpendicular to this plane.



   On the top of the conical member 535 is mounted an enneua 536 which carries knurls 537 and annular friction discs 538 are disposed between the ring and the top of the conical member. Inside the ring is a socket 539 and another socket 540 is disposed, on top of the ring 536 and the socket 539. In FIG. The shaft 526 extends upwardly through the ball 532, the taper member 535 and the bush 539. The upper portion of the shaft is threaded and carries a cylindrical member 541. The finger 10 has an upper port. conical 542, an intermediate disc-shaped portion 543 which bears on the cylindrical member 541 and a lower portion 544 which is screwed into the member 541.

   Shaft 526 has a central opening 545 which carries a spring 546 urging a plunger 547 against the portion

  <Desc / Clms Page number 42>

 lower 544 of the finger 10. This device absorbs the play.
514 has a bore 548 which carries a pin 549 which extends through an opening 550 of the ring 536.



   If the ring 536 is rotated, the spindle 549 'causes the cylindrical member 541 to rotate as well, and so, by its mounting. screwed, to move up and down on the shaft
526 by moving finger 10 up and down. Thus, the finger 10 can be adjusted to any vertical position relative to the gauge 16. When the finger has been so adjusted, the adjustment is maintained by the action of the friction discs 538.



   The conical portion 542 is arranged so that its radius (R) brought into coincidence with the template 16 corresponds to the radius of curvature of the working surface of the type of roller chosen. Thus, when choosing a particular type of roller for the job, finger 10 can be adjusted to correspond with its radius to the radius of curvature of the roller. Locating means (not shown) are provided to determine the above setting.



   This promotes the precision with which the tracer mechanism controls the movement of the rollers.



   The marker valve supplies the fluid to the motors 131 and 132 of the roller supports as follows:
The spring 514 is suitable for pushing the slide
495 upwards which, through ball 524 and rod 526, pushes ball 532 against cap 533. As the roller support 7 is moved forward by the carriage, the finger 10 and, the shaft
526 will be deflected from their vertical position and the ball 532 'will rotate, on the surface 533' of the cap 533. This moves the ball 524 slightly downward bringing with it the slide.
495. When the finger assumes the vertical position, the spring pushes the slider to its original position.



   In a normal operation the parts are arranged so that the recess G 1 remains slightly open. This causes fluid to flow from line 474 through

  <Desc / Clms Page number 43>

 the various communications to line 476. this has the effect of operating the roller support motors 131 and 132 in such a direction that they move inward. If the finger 10 is moved, the slide moves downward to close the recess Gl and open the recess G2. This causes the motors to drive the roller brackets outward. The recess G1 is very narrow, on the order of a few hundredths of a mm, so that very slight movement of the finger 10 causes the desired effect on the motors.



   Manual control of the roller supports.



   While the operation of the roller supports is ordinarily controlled by the movement imparted to finger 10 by jig 16, the supports may be caused to move inward or outward by movement of finger 10 at the hub. of a cam controlled by hand. The mechanism (fig. 3, 4, 16 and 23) is as follows: according to fig. 3, 4, 15 and 16, the body of the chariot carries two handwheels 571 and, 572. The flywheel 571 is mounted on a shaft 573 carried by the upper portion 57 and carries fixed on it a pinion 574. The pinion 574 meshes with an idle wheel 575 carried by the portion 57 which in turn meshes with another idle wheel 576 which is also carried by the portion 57.

   This latter wheel meshes with a pinion 577 carried on one end of the transversai shaft 580 supported by bearings in the side walls of the carriage body. Flywheel 572 is attached to the other end of shaft 580.



   According to fig. The shaft 580 carries a nut 581 which is secured to a slider 582 transversely adapted to move along the wall of the carriage body. The slider carries an arm 583 which has a triangular-shaped horizontal stop 584 attached to one end (elevation view f, 8. 15 and 16 and in plan Fig. 3).



   If one of the handwheels 571 or 572 is turned the nut 581 is caused to move along the shaft carrying with it the

  <Desc / Clms Page number 44>

 slide 582, arm 583 and stopper 584. The gears cause this stopper to be moved outward regardless of the handwheel moved clockwise.



   The provision of a cam actuated by hand to control the position of the roller supports is a feature of the invention and has several advantages. For example the finger and the plotter can be moved so that the jig can be adjusted and set without moving the roller supports, which would be the case if the finger were kept in engagement with the jig. In addition, the control is used when it is desired to form objects with parallel sides - In this case it is possible to remove the jig and keep the roller at a fixed distance from the axis of the spindle by moving the marker finger with the stop 584 until the rollers have reached the desired position.



   Mechanical operation of the trolley and by hand (fig. 23 and 27).



   The carriage is adapted to be moved by a screw 585 which extends along the bench under the carriage and which is supported at the rear end by a thrust bearing 586. The screw extends through the bench and in the head piece (fig. 23.) where it is supported by a thrust bearing 590 and a needle bearing 591 'carried by the console 592 fixed by bolts 593 on the head. The screw also carries the thrust bearing 594, the assembly being pulled and applied by the nuts 595. The outer end of the screw carries a toothed ring 596 fixed to the shaft by bolts 600. The crown carries a brake drum 601 for the guide screw, brake designated by 602.



   The brake 602 is adapted to be actuated during the mechanical and automatic operation of the machine to prevent the screw from rotating, while for the manual operation the brake is released so that the. steering screw is free to turn.



   The guide screw is interconnected with the carriage as follows (fig.? 3). Support 603 is fixed on the

  <Desc / Clms Page number 45>

 carriage at its upper and lower ends in 604 and 605.



   The screw carries a nut 606 rotatably mounted in the bracket 603 by a needle bearing-610 and the thrust bearings 611 and 612, these being secured by locknuts 613. A pinion 614 is also attached to the. nut 606 and meshes with a pinion 615 carried by the support 603, the pinion 615 meshes with a pinion
616 attached to the motor shaft 620.



   When running with the motor, the carriage is moved as follows. The hydraulic system is such that when the motor 620 is on, the brake of the. guide screw 602 prevents screw 585 from turning. The running of the motor 620 causes the rotation of the pinion 614 and of the nut 606. Consequently the carriage moves along the guide screw, the direction of movement depending on the direction of rotation of the motor 620. This non-rotation of the screw while running with the motor is important because there is no whipping of the screw which would cause non-uniform feed and low frequency vibrations of the rollers damaging the surface of the object.



   When walking by hand, the gears connecting the motor 620 and the nut 606 are blocked so that the nut cannot turn (fig. 27). An upright 587, fixed to the carriage by means not shown, carries an arm 588 which carries a pivoting lever 589. The lower end of the lever carries a toothed stop 607 which is slidably supported on the cohsole 587.



   The upper end of the lever is connected with a rod 608 attached to piston 609 mounted in cylinder 617. Fluid for cylinder 617 comes through line 617 'of control mechanism 619 described later. A tension spring 618 is provided. mounted between console 587 and lever 589 and acts to pull stopper 607 to the left.



   The hydraulic system of the machine is arranged so that during automatic operation the unit pressure in cylinder 617 is low enough that spring 618 pulls stopper 607 out of engagement with pinion 614.

  <Desc / Clms Page number 46>

 



   During manual operation the unit pressure in the cylinder 617 is large enough to overcome the spring tension and the stopper is moved into engagement with the pinion 614. Since the pinion 614 is jammed, the nut 606 cannot rotate.



  With the nut secured against rotation, it is evident that, if the guide screw is rotated, the nut and carriage will move along the bed, the direction depending on the direction of rotation of the screw. The means for manually controlling the rotation of the screw are those described below:
A console 621 (fig. 23) is carried by the head piece. This console fixes a cylindrical member 622 which 'carries bearings 623 and 624 supporting the shaft 625 in rotation. At its upper end the shaft carries a. bevel gear 626 '' which meshes with another bevel gear 630. As seen in fig. 1, the pinion 630 is attached to a shaft 631 which is / attached to a handwheel 632.

   The lower end of shaft 625 carries a pinion 632 which meshes with the ring gear. 596. ' Thus, when the handwheel 632 is rotated, the carriage can be moved on the bench.



   Head piece.



   The description is given by means of figs. 24, 25, 26, 38 and 39.



   As seen in fig. 24, the head piece comprises a frame 634, the face of which bears an insert 635 which is bolted to the frame by bolts 636. The ball bearings 640 are mounted on the insert 635 and its bearings carry spindle shaft 641. The spindle shaft is tapered at 642 and nuts 643 pull the bearing up against the shaft and against a thrust ring 644 against a seat 645. The seat is provided with grooves. The oil 646 and a cap 650 covers these grooves, being secured in the part by bolts 651. The bores 652 are oil passages.

   On the shaft 641 is mounted a spindle holder 653 tooth the conical inner part corresponds to a cone on

  <Desc / Clms Page number 47>

 the shaft 641 indicated at 654, the support being fixed to the shaft by bolts 655. The bolts-656 fix the pin 3 to the support 653.



  * In the description, the word spindle applies to the whole spindle, support and shaft.



   A similar bearing is provided at the other end of the shaft at 657. The bearings 640 and 657 support the rotating spindle and absorb the thrust forces. The bearing 640 allows the spindle to move axially, the rollers roll in grooves on the inner ring but on a flat surface in the outer ring. The same is true for stage 657.



   The purpose of this axial displacement will be explained in connection with the bearing. 660 which absorbs the axial loads on the spindle.



   For driving the spindle, a gear 661 is supported on a conical portion 662 of the shaft 641 with near it a ring 663. Near the ring is mounted a spacer 664 which also serves as a. rotating part on roller bearing 665
Against part 664 abuts another ring 666 and a small drive gear 670 is mounted on the shaft against part 666.



   Nut 641 'tightly tightened on the shaft pulls the above parts upward over taper portion 662 and secures pinions 661 and 670 to the shaft, these being keyable.



   Pinions 661 and 670 may alternatively engage with pinions 671 and 672 mounted on a shaft 673, one end of which is supported on the head by a bearing 674 and the other is supported by a bearing 675 mounted in the bracket. 676 on supports 680 (fig. 25). The pinions 671 and 672 can be slid axially on the shaft by a conventional mechanism, not shown.



   The outer end of the shaft 673 carries two pinions 681 and 682 adapted to engage alternately with the pinions 683 and 684 mounted on a shaft 685 carried by the console 686. The pinions 683 and 684 are axially sliding on the shaft . On the other end of the shaft 685 are mounted pinions 690 and 691 sliding axially by a mechanism not shown for

  <Desc / Clms Page number 48>

 be able to engage alternately with the drive pinions 692 and 693 adepts to be driven by an electric motor 694 by a mechanism described below.



   The spindle can thus be rotated at different speeds. A control arm or button 696 (freeze 1) is provided on the head, by means of which the operator can set the desired speed. The button controls a sta.ndard gear change mechanism, not shown.



   The gear drive mechanism 692 and 693 comprises an automatic clutch 704 and a brake 704 '. The rater 694 is provided with a pulley 700 which drives by belt 701 a pulley 702 on the shaft 703 carried in the head by the bearing 703 '.



  The drum 705 (fig. 26) of the clutch 704 is keyed on the shaft 703. It is of the disc type with several friction discs 706 keyed on the drum axially and several intermediate discs 710 keyed axially on a shaft hollow 711 coaxial with 703. The hollow shaft 711 carries the pinions 692 and 693 at its right end and on its left end is fixed a rear clutch plate 712. Around the hollow shaft 711 and between the clutch 704 and the brake 704 'is a sliding sleeve 713, the left end of which engages the hub of the clutch plate 714, while its right end engages the hub of a pla.aue 715 of the brake.

   The brake comprises several friction discs: 716 keyed axially on the hub of the plate 715, several disnues 720 keyed axially on a cylindrical member '721 mounted in a bracket 723 fixed on the support 680, a bearing cap 722 for the hollow shaft 711 and a rear plate 725 between the cap 722 and the friction disaues. The cap 722 and the sleeve 721 are fixed to the console 723 by bolts 724.



   Another shaft 703 "is disposed inside the hollow shaft 711 and carries two nuts 726. A spring 730 surrounds the shaft 703" and acts between the collars 726 and the end of the hollow shaft 711. A spacer sleeve 731 is provided between the collars

  <Desc / Clms Page number 49>

 anda piston 732 is mounted in cylinder 733. The cylinder is fixed to the frame of the head 634 and is provided with a fluid connection 734 with its chamber 735. The hollow shaft 711 has a shoulder
711 'which engages with cap 722.



   Shaft 703 "carries a pin 717 which extends outwardly through slots 718 in hollow shaft 711 for connection with sleeve 713.



   The operation of the clutch and the brake is as follows: When the. machine is on standby, the fluid in the chamber 735 is such that the piston 732 will be moved in the cylinder by the spring 730. Under these conditions the spring 730 reacts from the stepped end 711 'of the hollow shaft 711 to push the shaft 703 "and the piston 732 to the right. This movement of the shaft 703" to the right is transmitted to the sleeve 713 by the spindle 717 and consequently the brake presses the brake plates together and against the back plate 725, to apply the brake. This movement of the sleeve 713 to the right also releases the plate 714 and the discs 706 and 710 from the clutch which is thus disengaged.



   If pressurized fluid is introduced into chamber 735, piston 732 moves to the left along with shaft 703 "and sleeve 713. This movement causes clutch plate 714 to press disks together. against the other and against the back plate 712 to engage the clutch At the same time the plate 715 and the discs 716 and 720 of the brake are released so that the brake is released.



   When the clutch is disengaged, no torque is transmitted from shaft 703 to drive gears 692 and 693, and with the brake applied, the spindle, if it turns, will slow down and stop. When the clutch is engaged and the brake released, torque from shaft 703 drives the gears to rotate and the spindle.

  <Desc / Clms Page number 50>

 rotates at a speed chosen by the selection of the above-mentioned mechanism.



   The hydraulic thrust bearing for the spindle is constructed as follows (fig. 24). The frame 634 carries a fairly massive support 736 'extending transversely which carries a cylindrical insert 740. This part presents a valve mechanism 741 which will be described in correspondence with FIG. 38.



    . ' Room 740 has a cylindrical chamber 742 of which each. end wears a cap 743 and 744 fixed by bolts 745, 746.



   The bonnet 743 has a passage 750 and the bonnet 744 a passage 751 which are of the same size and, coaxial with the axis of the chamber 742. '
Inside the chamber 742 is mounted an axial slide 752 with collars 753 and 754 of the same dimensions. The slider is mounted in the chamber on 755.756 ball bearings which center it and allow it to move freely back and forth to the right and left along a fixed axis.



   The cylindrical extension 763 of the slide is slightly larger in diameter than the passage 750 so that if the slide is moved all the way to the left, the passage is closed.



   End 763 is provided with a mirror polished surface and the surrounding surface 764 is provided with passage 750 as well. Thus a polished surface 764 lies opposite a polished annular surface f
764 'on extension 763.,
The cylindrical extension 765 of the right end of the slider, which is the same dimensions as 763, also has a polished surface as well as the annular surface 771 around the passage 751 in the cap 744. Thus the two polished surfaces
770 and 771 face each other.



   The surfaces 764 and 764 'are shown on a larger scale in fig. 39. We see that they form a free gap G3, while the surfaces 770 and 771 leave an gap G4. The dimensions W1 and W2 of the two surfaces 764 and 764 'are equal

  <Desc / Clms Page number 51>

 and the outer circumferences L1 and L2 are equal as are the inner circumferences L3 and L4.

   The surfaces 770 and 771 'are arranged in the same way. The length of the interval G3 (equal for W1 and W2) is equal to that of G4. The length of each gap is kept as small as possible, that is to say -at least- so large that the extensions 763 and 765 do not protrude into the passages 750 and 751. The axial length of the slide 752 and the axial length of the chamber 742 are chosen such that, when the slide is centered in the chamber, the size of each of the intervals G3 and G4 is of the order of 2 tenths to 2.5 tenths of a mm.



   The part 740 (fig. 24) is in itself a large ring surrounding the shaft 641 and has at its left end two annular shoulders, the end faces of which are close to corresponding shoulders of the pinion 670, but axially distant from it (fig. 38). '
The outer peripheral shoulder of part 740 is provided with a polished surface 772 as well as the corresponding shoulder of pinion 670 at 773. These surfaces reserve an annular gap G5 (Fig. 39). The inner shoulder of part 740 has a polished surface 774, as does pinion 670, surfaces 774 and 775 leaving a gap G6.

   The dimensions W3, and W4 of the surfaces 773 and 772 (fig. 39) are equal as are W5 and W6 for the surfaces 775 and 774 and the circumferences of these surfaces are equal in 772 and 773 d as in 774 and 775 .



   The other end of the insert is provided with an annular outer surface '780 cooperating with a surface 781 of the pinion 661 with a gap G7. The surfaces 782, 783 form on the right an interval G8. The lengths of 05, G6, G7 and G8 are all on the order of 2.5 tenths of a mm.



   , 6 It is recalled that the bearings 640 and 657 allow the spindle a certain axial displacement. The elements described above are arranged such that when the gears 670 and 661 are

  <Desc / Clms Page number 52>

 centered relative to the part 740, the intervals G5 and G8 each have a width of 2.5 to 5 hundredths of a mm and preferably 4 hundredths of film.



   Pinion 670 has an annular groove 789 formed therein which is in connection with gaps G5 and G6. The surface of this groove is equal to that of the groove 785 in the pinion 661 cooperating with G7 and G8. The grooves 784 and 785 constitute fluid chambers.



   The operation of the hydraulic thrust bearing is as follows:
The bearing is provided for when there is no load., There is an equal flow of fluid through G5-G6 and G7-G8, this distribution of the fluid being regulated automatically by the shapes and tolerances of the rooms. Under load, the flow of fluid automatically increases towards intervals which tend to close in proportion to the applied load,
When there is no load the arrangement of the parts is as follows: Connection 762 is connected to the discharge side of the service pump of the head 901 (fig. 36) and this pump operates to deliver a positive current of fluid.

   From 762 the fluid is separated and passes on the left through the gap 760, the chamber 790 (formed by the outer surface of the extension 763 and the inner wall of the chamber. 742), the gap G3, the passage 750, the. chamber 784 and gaps G5 and 6. On the right side the fluid passes through gap 761, chamber 791, gap G5, passage 751, chamber 785 and exits through gaps G7 and G8.



   The pressure drops across the corresponding gaps on the left side and the right side will be the same.



  Thus the force acting on the surfaces A1 and A2 will be the same.



  The force acting on A3 and A4 will be the same and the slide 752 will be centered in the chamber 742. The unit pressures in the chambers 784-and 785 will be the same and the force exerted will be centered.

  <Desc / Clms Page number 53>

 gears 670 and 661 around part 740.



   The slide and pinions will remain centered until the spindle is subjected to axial thrust and the device will then operate under load as follows:
When the forming operation begins, an axial thrust is exerted on the spindle and the pinions 661 and 670 tend to move to the left of Figs. 24 and 38, which tends to close the intervals G7, G8 and to open the intervals G5, G6. Yes
G7 and G8 fully shut off the fluid from 762 will flow to the left through gap 760, chamber 790, passage 750, chamber 784 and exit through gaps G5 and G6.

   Also the gear 661 engages against the part 740 and there is no more fluid bearing. - This does not happen because the fluid flow on the right side is increased and the gaps G7 and G8 remain open, the value of the fluid flow is a function of the thrust on the spindle as (follows:
The tendency of G7., G8 to close causes an increase in the unit pressure in chamber 7 $ 5 and passage 751 and the tendency of G5 and G6 to open causes a decrease in unit pressure in the chamber. 784 and passage 750.

   The unit pressure in the passage 750 acts on the end surface A3 and the pressure of the passage 751 acts on the end surface A4. As a result, a greater force tends to move the slide 752 to the left which tends to close G3 ′ and open G4. Thus the flow of fluid to the left is reduced and that to the right is increased and the intervals G7, G8 remain open.

   The magnitude of the displacement of the slide to the left is a function of the thrust tending to close the intervals G7, G8, because the more these intervals close, the greater is the unit pressure in the chamber 785 and the passages 751 and the greater is the ... force tending to move the slide 752 to the left:
On operation, the unit pressure in chamber 791

  <Desc / Clms Page number 54>

 may be less than that in 790 due to the drop in the gaps' .7 61 and 760 which tends to move the slider to the right- However, the end surfaces A3 and A4 and consequently the forces exerted on those - these act as controls.



   The sensitivity of the device, i.e. the speed with which the bearing will act to establish the pressure opposite the axial thrust, depends on the speed at which the slide responds to increase the flow of the fluid. It is a function of the resistance of the gaps 760 and 761 and also a function of the ratio of the end surfaces (A4, A2) to the intermediate surfaces (A3, A1).

   In general this relation is as follows: the lower the resistance of the gaps 760 and 761, the greater the value of the end surfaces relative to the intermediate surfaces, and the greater the speed of response. from the slider to the increase in fluid flow through G7 and G8 and the increase in pressure opposite to the axial thrust. These factors can be changed proportionally to achieve the desired sensitivity, but still arranged so that the slide moves to increase the flow of fluid through the gaps which tend to close.



   As said above, the size of the intervals G7 and G8 can be about 4 hundredths of a mm under zero load conditions. Under these conditions the pressure drop across each gap is very low, which is advantageous from a low power loss point of view. One of the important factors of the device is that when gaps tend to close under axial thrust, the pressure drop increases to a high value at an extremely rapid rate. One of the important advantages is that, with a maximum thrust of 30 tons, the total plastic axial displacement of the spindle is only of the order of 13 thousandths of a mm.

  <Desc / Clms Page number 55>

 



   As mentioned above the length of the intervals
G5, G6 and G7, G8 is 2.5 * hundredths of a mm or less. This short length has little effect on the pressure drop across 1-gap but has a very large effect of reducing resistance - due to the viscosity caused by the fluid flow through a gap and the displacements. relative of the constituent surfaces of the interval. With low viscosity resistance,
The efficiency of the bearing is very high especially compared to a usual roller bearing or thrust bearing. Furthermore, the low viscosity resistance enables the spindle to be rotated at very, high speeds without appreciable loss of power.



   It should be emphasized that the described hydraulic thrust bearing operates in a similar way if the direction of the axial thrust is reversed, for example when the machine is used such that the rollers move rearward during forming. Further in such a case the thrust may be greater in one direction than the other and therefore the chambers 784 and 785 may be of different relative dimensions. With such modifications the bearing operates in the same way as described.

   In addition it is emphasized that if the machine is used so that the axial thrust on the spindle is exerted in only one direction. The above hydraulic bearing can be replaced by a bearing similar to that described for the rotating head of the tail piece.



   The roller bearing 665 plays an important role in the device of the hydraulic bearing. It rotatably supports the spindle shaft at a point between bearings 640 and 657 and reduces the tendency of the shaft to bend. If this deformation were sufficiently large, it could deform the chamber 742 and compromise the operation of the slide 752. Note that the bearing 665 and the spacers 663 and 666 are available. <sés to allow axial displacement of the shaft. In some

  <Desc / Clms Page number 56>

 In these applications, the bearing 665 would be the main bearing for supporting the rotation of a shaft.



   In fig. 24 are provided some oil channels. Fluid from intervals G5 and G6 is received through annular slots 792 and 793 of part 741. Fluid from G7 and G8 is received in slots 794 'and 795. They communicate with channels 797 going to one. tank.



   The hydraulic bearing can be modified in the following direction: For example, it is not necessary to provide the mechanism for separating the average fluid stream of the intervals 760, 761. The central portion of the slide, instead of having collars 753, 754 connected by an intermediate portion 754, may be replaced by a solid cylindrical portion which fits neatly into chamber 742. Fluid connections may be provided for chambers 790 and 791 connected on each side. an externally mounted current divider valve which, in turn, is connected with the. source of pressure.



   The hydraulic bearing can also be modified by replacing the pinions 670 and 661 with discs which have corresponding chambers and polished surfaces. The discs may be mounted on the shaft to be rotatable with it, but not necessarily so as to achieve drive engagement.



  In this case, independent gears are to be provided at other points on the shaft.



   It is recalled that the various surfaces forming the various intervals have been defined as having polished faces.



  The mirror-polished surface finish is preferable because, for example, these surfaces have less tendency to offer viscosity resistance; however, in some cases it is possible to be satisfied with surfaces with a less fine polish.



   The hydraulic thrust bearing for the spindle constitutes a feature of the invention. It allows to rotate the

  <Desc / Clms Page number 57>

 spindle at at least 2000 revolutions per minute even though an axial thrust of the order of 30 tonnes is exerted on it. No known roller bearing can absorb such a load by rotating at such a speed. In metal forming operations of the kind described herein, high roller or forming speeds with high spindle speeds are very favorable, especially from the point of view of mass production on the machine.



   Electric and hydraulic circuits. Machine running.



   Electrical Circuits: Power for the various motors is supplied by a three phase bus bar system extending along the bench. The circuit diagram is given in fig. 37.



   The bar system being 900 ,, - the right part of the dotted lines represents the carriage part and the left part represents the head part part. The electric motors 58, 59 and 60 are connected with the bars by, wipers and are adapted to drive the roller supports, the feed pump 'Sa, the carriage drive pump 59a and the carriage service pump 60a. ,
On the left side, the spindle drive motor 694 is connected directly with the bars. As already mentioned, this motor drives the spindle rotation.



  In addition it operates the service pump of the head piece 901.



  This pump is not shown in, freezes 24 and 25, but. it is connected with the motor shaft 694 by a standard coupling.



   The busbar system is supplied with power through a standard magnetic starter 902 with control boot 903 with "Start" button 904 and "Stop" button 905, control lamp 906. This box is mounted on the head as shown in fig. 1.



   The hydraulic circuit of the head part is shown

  <Desc / Clms Page number 58>

 tee in fig. 36. When the operator has pushed the "Start 'button 904 the discharge side of the pump 901 sends the pressurized fluid into the hydraulic bearing of the head piece 660 through the connections 762. The inlet of the pump 901 is connected to a tank 901 '.



   The pressurized fluid is also sent through lines 910 and 911 to the gear slide selector valve 912 which can be positioned by means of the button 696 (fig.l) on the head. This valve activates the speed change (fig. 24 and 25) to turn the spindle at the desired speed.



   The pressurized fluid is also sent through lines 910 and -913 to the automatic or manual work selector valve, which can be actuated by the control button 912 on the head (fig.1).



   The valve 914 has a plug 915 connected to the button 912, an annular passage 916 communicating with the pipe 913, an axial orifice 920, connected to the casing sump at 921 and a radial orifice 922. The pipe 923 coming from the passage 916 of the , valve is connected to line 924 and line 925 which are respectively connected with guide screw brake 602 and control mechanism 619 '.



   The brake 602 comprises a drum, 601 connected (fig. 23) with the guide screw of the carriage 585 and the cylinder 926 is connected with the pipe 924. Inside the cylinder are provided two pistons 930 and 931 which are respectively connected to the brake shoes 932 and 933 which are preferably of the automatic type. Springs 934, 935 normally push the pistons towards the center of the cylinder to release the brake. When the valve 904 is in the automatic position, (position shown in fig.) The rotor 915 connects the discharge 901 of the. pump to the brake supply line 923 and the brake shoes are tight against the brake drum. Thus the guide screw of the carriage is blocked.



   When valve 914 is in the manual position (turn-

  <Desc / Clms Page number 59>

 Born from 90 in the indirect direction, the rotor 915 connects the pipe 923 with the reservoir. Thus the springs in the brake cylinder push the pistons towards the center and the brake does not engage the drum. Thus the guide screw of the carriage is free to turn.



   The control mechanism 619 'comprises an arm 936' which is keyed to a splined shaft 940 which extends from the head piece in the carriage (fig. 4) and which is fixed axially in the base so that the carriage can move forward, and backward on this tree. In the carriage the shaft 940 is connected together with the control mechanism 619 (fig. 27). Tension spring 941 pushes the arm down. On the end of the arm 936 is a rod 942 connected with the piston 943 in the cylinder 944 which is supplied with fluid from there. pipeline 925.



   When the selector valve 914 is at the. in the manual position, the cylinder 944 is therefore connected to the reservoir and the spring pulls the arm 936 downward to rotate the shaft 940 in the forward direction. When valve 914; is in the automatic position, the discharge of pump 901 is connected with cylinder 944, causing piston 943 and arm 936 to move upward and shaft 940 to rotate in. the indirect direction. The effect of the rotation of the shaft 940 is explained below with the aid of fig. 27. The control mechanism 619 comprises a valve 945 with a plug 946 wedged on the shaft 940.



  The valve has two annular passages 9,50, and 951. Port and line 952 are connected to the / discharge of the cart service pump 60a (Fig. 35). Port and line 953 are also connected to this discharge but at such a point that the unit pressure is lower than in port 952.



  Port 954 is connected to line 617 '.



   '' When valve 914 (fig. 36) is on automatic,
 EMI59.1
 1 "shaft 940 is driven in an indirect direction ost In boinreiii 946 of the valve 945 is moved to the position shown. Thus the

  <Desc / Clms Page number 60>

   cylinder 617 is connected to port 953 and spring 618 pulls stopper 607 out of engagement with pinion 614 so that carriage drive nut 606 can rotate with the unit pressure in cylinder 617 being sufficiently low so that the spring 618 can do so.



  When the. valve 914 is in the manual position, the shaft 940 is turned in the forward direction and the plug 946 connects the port 952 with the cylinder 617, this yes brings the toothed stopper 607 into engagement with the gear 614 and prevents the carriage drive nut 606 (fig. 2.3) e turn, the unit pressure in cylinder 617 being high enough to overcome the effect of spring 618.



  It should be noted that the unit pressures of the fluid at ports 952 and 953 are hereinafter referred to as "operating pressure" and "sub-operating" respectively, the second being lower than the first, e.



  To summarize the above: - If button 912 is on. '' the automatic position the steering screw. 585 of the carriage is locked against rotation while the carriage nut is free to rotate so that the running of the motor 620 drives the carriage.



  If button 912 is in the manual position, guide screw 585 is free to rotate, while nut 606 is locked against rotation. An operation of the handwheel 632 will move the carriage.



  When the head service pump 901 is running, oil is also supplied through line 910 to the jig clamping pin drive valve 961. The valve is adapted to be actuated by the up and down movement of the blank holder 12 and the role of the valve is to actuate the spindle clutch 704 and the spindle brake 704 'at the same time as the locking or tightening mechanism of the template 459.

  <Desc / Clms Page number 61>

      



   Valve 961 has a plug 962 connected to a splined shaft 963 (Figs. 4 and 11) which extends from the head into the carriage where it is assembled to the blank support. The shaft is fixed axially so that the carriage can move relative to it.



   As can be seen in fig. 11, the shaft carries a stopper 964 which is adapted to be engaged by the L-shaped member 371 on the vertically movable frame 352 of the blank support. The L-shaped member 371, in fig. 11, has moved stopper 964 down and rotates the shaft in an indirect direction. When the roughing support is in the. upper position, the stopper 964 also moves upwards as will be explained with reference to fig. 36. When the stopper 964 moves upwards, the shaft 963 is obviously driven in rotation '' in the direct direction.



    In Fig. 36, the plug 962 provides an arm 965 which is normally biased upward by a tension spring 966 against a stopper 970. Thus, when the L-shaped piece, 371 (Fig. 11) is moved towards up., the shaft is rotated in the direct direction by the action of the transfer 966 (fig. 36) and the plug 962 is in the position shown.



     The plug 962 has an annular chamber 971 and a radial opening 972 which are connected to the reservoir by a link.



  973. When the su or is in the 'UP position, the valve 962 connects between them the cylinder of the mechanism' clutch 'and brake'733 and the reservoir, through lines 974, 975 and 470' and 734 '. 'is recalled that, when the pressure is removed in the cylinder 733, the brake is engaged and the clutch is inoperative to transmit the torque and the spindle does not turn. The locking cylinders of the jig 462 are also connected to the tank through ports 470 and line 470 'etc.

   and it is recalled that, when the pressure is removed in these cylinder heads, the jig support is free to move while sinking on the bench, when the blank support is in the DOWN position,

  <Desc / Clms Page number 62>

 the plug 962 interconnects the discharge side of the head service pump 901 with the brake clutch mechanism 733 and with the jig locking cylinders 462. The unit pressure in cylinder 733 forces the brake to release and the clutch to engage. Thus the spindle is driven to turn. The unitary pressure in the cylinders 462 locks the jig support on the bench.



   To sum up: In the event that the roughing support is on UP the clutch 704 is released and the brake 704 'applied so that the spindle does not turn and the locking devices 459 allow movement, of the gauge along the bench. If the roughing support is on 'LOW', the clutch 704 is engaged and 1 the brake: .70 ± 'released, de' causes the spindle to turn
 EMI62.1
 and the devices; de verrau.llag, e 459 block.the.jig support on the bench.
 EMI62.2
 



  Valve 'arôra..Yume ..,' ..; . : Before describing the hydraulics .... - =. Î ',; ¯, 1' 1. ,, '. 1. <[1 of the carriage, it is preferable to erect the construction of the program valve 800 '(fig. 28 to 34). It is mounted on the body portion of the carriage and its role is to transfer the pressurized fluid to the various valves which, in their entirety, actuate or condition the action of certain components of the machine. The valve is adapted to be marked in various positions for which certain operations are carried out.



   Valve 800 has a frame 801 which is supported on a bracket 802 mounted in body portion 36 of the carriage. ”Frame 801 carries three annular grooves 803, 804, 805 connected to lines 806, 810 and 811, respectively. The frame also has a bore 812 connected to the pipe 813.



  Inside the frame is fixedly mounted a sleeve 814 which can be fixed to the body by tight fitting.



   The sleeve is provided with several orifices arranged
 EMI62.3
 in aes planes spaces axially a, b, .2., ç1, (fi, z. 23). In the

  <Desc / Clms Page number 63>

 plane a (fig. 30) the orifices are also distant 821, 822,
823 and 824 and all communicate with the groove 803. The orifices in plane b (fig. 31) are arranged retort in plane a in
825, 826, 830 and 831. All are in communication with throat 804.



   In plane c (fig. 32) the orifices 832, 833, 834, 835 are also distant but offset with respect to the orifices in planes a and b. The latter communicate with the groove 805. In the plane d (fig. 33) the sleeve has an annular chamber 836 and a single orifice 840.



   Inside the sleeve is mounted a plug 841 with several orifices in each of the planes a, b ,, c, d, and several axially extending orifices. In each plane, the orifices are divided into four segments, each having an identinue arrangement of the orifices. The bushel is adapted to turn in stages following a segment so as each time to provide the energy or the. withdraw to fluid lines 806, 810 and 811, then moved to the next segment where lines 806, 810 and 811 are similarly assigned. As each of the segments is identical, it suffices to describe only one of them in planes a, b, c and d.

   By providing for a duplication of the segments, the pressures are balanced and the thrust required for the ratchet is reduced. actuating the valve *
In plane a, the plug has radial orifices 842, 843, 844 and 845. In plane b, the plug has radial orifices 864, 850 and a tangential slot 851 in communication with orifice 850. In plane c the plug has radial orifices 852 and 853 and a tangential slot 854 in communication with 853. Therefore the plane of the plug has radial orifices 855 and 856 ..



   The plug 841 has an axially extending orifice 860 which, in plane a, is in communication with the orifice 842 and in the pand d, with the orifice 855. The orifice 860 has a cap 860 'which closes a end (fig. 28). Another

  <Desc / Clms Page number 64>

 axial orifice 861 is, in plane a, in communication with 843, in plane b with 846, in plane ± with 852, and in plane d with 856. The orifice 861 has a closing cap, not shown analogous to 860.



   It should be noted that line 813 is connected to the discharge side of the trolley pump 60a (fig. 35).



  The fluid in this pipe is at operating pressure. Thus, in the position of the plug 841 shown (which is the "Stand-by" position of the machine) the fluid at the operating pressure is supplied through the orifice 840 into the annular chamber 836 through the orifices 8? 5 'and 856 towards the axial orifices 860 and 861.



  The orifice 860 then supplies the fluid at the operating pressure to the. line 806 through radial ports 842, 821, and chamber 803.



   The wood'seau 841 has a central orifice 862 which, in the plane a, communicates with the radial orifices 844 and 845, in the plane b with 850, in the plane c with 853. The orifice 862 is connected by the pipe 862 'to the discharge side of pump 60a (fig. 35) but at such a point that the unit pressure in port 862 is less than that of line 813. Fluid in port is at "underoperating pressure. "mentioned above. The coupling allows the plug 841 to be rotated.



   Line 810 is, in the valve position shown, connected with suboperating pressure through annular chamber 804 (see drawing b) port 826, slot 851, and port 850. Line 811 is also connected with suboperating pressure through annular chamber 805 (see drawing ±), port 833, slot 854 and port 853.



   The bushel is adapted to be moved or positioned from there. position shown (plane a for example) where orifice 842 is in communication with orifice 821 (position # 1) towards position # 2 in which orifice 843 is in communication.

  <Desc / Clms Page number 65>

 cation with port 821; then towards the. position # 3 where 844 communicates with 821 and then position # 4 where 845 communicates with 821. The effect of this positioning is to control the fluid in pipes 806, 810 and 811 so that it is at the pres - operative or sub-operative zone according to a predetermined sequence.



   The sequence is chosen according to the following table:
 EMI65.1
 
 <tb> Position <SEP> Pipe <SEP> 806. <SEP> 810. <SEP> 811
 <tb>
 <tb> 1 <SEP> x <SEP> 0 <SEP> 0, <SEP>
 <tb>
 <tb> 2 ' <SEP> x <SEP> x <SEP> 0
 <tb>
 <tb> 3 <SEP> 0 <SEP> 0 <SEP> x
 <tb>
 <tb> 4 <SEP> 0 <SEP> 0 <SEP> 0
 <tb>
 x representing the operating pressure
0 La. suboperative pressure.



   The plug 841 is adapted to be alternately positioned by the ratchet mechanisms 863 and 864 mounted on the opposite sides of the plug. Each of these mechanisms is of identical construction. The mechanism 863 for example mounted on the right side of the valve comprises a wheel. roch, and 865 wedged on the bushel in 866. An arm 870 carrying a spring finger 871 adapted to engage in the teeth of the: wheel is mounted rotating on, the bushel 841. The arm 870 is provided with a stop 872 which relates to a piston 873 carried by the cylinder 874. The stopper is maintained in engagement with the piston by a spring 875 mounted between the cylinder and the arm.

   Line 893 is adapted to supply the operating pressure in the chamber 876 of the cylinder, which causes 1 displacement of the piston upwards to rotate the arm 87) and the finger 871 which, in turn, turns the ratchet wheel and the bushel. When the operating pressure in chamber 8 @ 6 is removed, i.e. changed to under-operating pressure, the spring 875 causes the arm 870 and the finger 871 to move back to their position against the next tooth of the ratchet wheel. It should be noted that the wheel has sixteen teeth of

  <Desc / Clms Page number 66>

   so that the plug is positioned four times for every 90 turn as mentioned above.



   Line 893 'on mechanism $ 64 is also supplied with operating or suboperating pressure, the effect being to move plug 841 in a manner analogous to mechanism 863.



  The manner in which the pipes 893 and 893 'are arranged and conditioned will be briefly described below.



   Hydraulic circuits of the truck.



   These circuits will be described with the operating mode of the machine with reference to fig. 35.



   It is assumed that the "Start 904" button on the head has been pressed, that the button 912 is in the automatic position, and that the button 696 has been pressed to choose the desired speed.



   The hydraulic circuits of the truck include two circulation systems supplied by an independent system which also supplies the fluid which actuates certain valves and certain components of the machine.



   One of the circulation systems is for driving the rollers inward and outward and generally comprises the roller support feed pump 58a which is of the constant displacement type, the motors 131 and 132 for supports 6 and 7 and the plotter valve 471. The other circulation system is for driving the carriage and the rollers forwards and backwards and comprises: the feed pump of the carriage 59a which is of the constant pressure variable displacement type, the stop valve 1031, the direction valve 1034 and the feed motor of the carriage 620.



   The independent system is supplied by the carriage operating pressure pump 60a which is of the constant displacement type. The fluid from this pump performs various different functions which are briefly described below.

  <Desc / Clms Page number 67>

 



   The inlet side of the pump is connected to a filter
1000 yes is connected to the tank 1001. The tank is placed in the body portion of the carriage, the oil level being indicated by the letter L fig. 23. The discharge side of the pump is connected to line 1002. Fluid from line 1002 passes through valve 1002 ', through general circuit 1006, and thence through restriction 1008 to reservoir 1001. There is a pressure drop across circuit 1006 and the pressure at point 1007 just before restriction 1008 is a little lower than the pressure in line 1002.

   In the description, the pressure in line 1002 and the lines connected to it will be referred to as the "operating" pressure and the pressure at point 1007 and in the connected lines will be referred to as "sub-operating pressure". The purpose of valve 1002 'is to maintain the operating pressure in line 1002 at an essentially constant value (besides, to create a pressure drop, as mentioned above, circuit 1006 performs other functions which will be described later).



   Various valves of the machine are adapted to be alternately connected with the pressure line 1002, or the suboperating pressure point 1007. For example, when the chamber 1031c of the direction valve 1031 is connected with the point 1007, the The valve is positioned such that the carriage moves in a backward direction and, when the valve is connected to the operating pressure line 1002, the valve is positioned to drive the machine in the forward direction.



   As mentioned above, another function of the working pressure system of the truck is to replace the two independent circulation circuits. For example the system supplied by the feed pump of the roller supports 58a is

  <Desc / Clms Page number 68>

 short circuit through valves 1104 which are connected to pipes 1010., 1009 and point 1007.



   Another function of the carriage working pressure system is to provide energy to the hydraulic means to maintain the carriage and jig in resilient engagement and also to supply energy to the hydraulic means to disengage the latch in the locking mechanism. 'drive the roller supports.

   As seen in Fig. '35., Carriage piston 449 is connected with suboperative pressure line 1010 so that cylinder 442 moves to engage adjustable stop 461 with arm '448. Rear set of roller brackets 146 is connected to suboperating pressure line 1009 and pistons 151 and 155 are pushed outward to resume play as already described.



  The under-operating pressure is sufficient to perform these functions.



   Machine in standby position:
The machine is supposed to start from the "Standby" position.



  At this moment, the carriage is fully backward, the program valve is in position 4, the blank support 12 is in the "UP" position, the roller supports 6 and 7 are fully backward. 'interior and the bearing of the head or part. tail is under pressure. The manner in which the above occurs will be described below. Although the spindle does not turn, the hydraulic spindle bearing is under pressure, the jig support is resiliently engaged with the carriage and the roller support locking means are under pressure.



     Action on the push button: On. then places a blank on the blank support 12 and the operator acts on the push button 1020 which actuates the program valve from position 4 to position 1, The slide 1018a is moved downwards against the spring 1018b and the press - operational signal is transmitted from line 1005, 1015 and 1021

  <Desc / Clms Page number 69>

 across the. valve 1018 to line 893 and the ratchet mechanism moves the program valve plug to position 1
In this position line 806 is at operating pressure, while lines 810 and 811 are at under-operating pressure.

   After the button 1020 has been released by the operator, the spring 1018b pushes the slider 10.18a back to the position shown when the chamber 1018c is at suboperating pressure, through the lines 1022, the valve 1023 and the valve. Line 1024 which is connected with the suboperating line 1010 ..



   Pressure operating in line 806 and under-operating in 810 and 811 causes the carriage to move forward,.



   Moving the carriage forward:
The operating pressure from line 806 is transmitted through line 1025, roller support limit valve 1026, line 1030 ,, 'to stop valve 1031. The function of the stop valve is to control the pressure. The fluid flow from the cart feed pump 59a to the cart feed motor 620, transmitting the operating pressure to the chamber 1031c causes the slider 1031a to move downward against the spring 1031b. Thus, the fluid from the discharge side of the feed pump 59a is transmitted through the line 1032 through the valve 1031 to the line 1033 connected with the direction valve 1034.

   The administration side of the. pump 59a is also connected through the direction valve, line 1035, stop valve 1031 and line 1036.



   Now returning to the program valve, operating pressure is transmitted to line 1040 from 806 to steering valve 1034. The operating pressure in chamber 1034c causes slider 1034a to move down against spring 1034b. Thus the fluid is transmitted from the line 1033 through the valve 1034 to the line 1041 connected with

  <Desc / Clms Page number 70>

 the feed motor to cart 620. Fluid is also transmitted from line 1036 through 1042, the direction valve 1034 to line 1043 yes is connected to motor 620.

   Thus the feed motor of the carriage is caused to rotate and move the carriage forward.



   The way the. carriage feed pump 59a is controlled is explained below, but first it is useful to clarify that the lines 1041 and 1043 are connected to check valves 1044, 1045, each being connected to a line 1046 which is connected through line 1050 to suboperating pressure line 1010.



  Likewise the inlet and outlet sides of pump 59a are connected by check valves 1052 and 1052 'with the suboperating pressure line 1010. These circuits are priming circuits.



   The feed pump 59a is of the constant pressure, variable flow type, preferably of the eccentric plunger type. In order to keep the unit pressure of the pump constant under the various operating conditions of the machine, it is expected that the flow rate of the pump can be changed automatically. This movement is controlled by the movement of the arm 1053 and, in the position of the arm shown, the pump delivers the maximum amount of fluid. If the arm is turned to the left (dotted position) the flow rate is zero. Further rotation of the arm to the left causes the pump to reverse direction, the discharge 1032 becoming the inlet and the inlet 1035 becoming the discharge.



   The arm is connected with the 1054 and 1056 control units, They are cylinders and pistons, the pistons of which are connected with the 1053 arm and the relative pressures of the cylinders control the position of the arm, The unit pressure in the unit 1056 tends to rotate arm 1053 to the right, while unit pressure in 1054 tends to rotate it to the left.

  <Desc / Clms Page number 71>

 



   Control unit 1054 operates by the pressure of pump 59a, the cylinder being connected with line 1055 which is connected with line 1032. Control unit 1056 is operated from pressure from the charjot pump
60a by circuit 1006.



   Line 1060 coming from 1 - '' control unit 1056 is connected to one side of the control valve. pressure 1061 yes is adjustable so that the unit pressure in the control unit 1056 can be set to a desired value. Control valve 1061 operates as follows
The operating pressure line 1002 supplies the
 EMI71.1
 fluid to the flow-dividing valve 1057 yes is ,, - adjustable in such a way, the flow to its outlet ports 1062 and 1063 is distributed in the desired manner..La ', orie lb62: -is connected; at. control valve), 106ifl.p, to '1. , é, ar.sat.'ori'.106 :.



  The other exit 1063 is 'com1ecÉ'àe with. Ltne,' ri, nne de det.ente 1065. Par la ca.n.llsatibn z066 1a ',' va'nrié 1ti65'estl'c, ofinecte rvec. .â by pipe 1066 and 1 ± nrie '1065 is c; ohn'ecte with. pipe 1064 by a pipe l6'70t .. The' expansion valve is also. connected by 1071, with a ', chamber The annular orifice of the timed shut-off valve 1072. The annular orifice of this valve is connected by 1073 with the line 1064.

   The annular port c of the time delay valve is connected with the suboperating pressure point 1007 through line '1074. The low pressure side of the control valve 1061 is connected through lines 1075 and 1074 at this point. collection of pressure.



   The cut-off valve has a slide 1072a, a
 EMI71.2
 refFort 1072b and a c.hp ,, ibre lo7? c. 1 chAù1bre @ 3t connected by pipe 1076 an adjustable timed valve 1080. The other side of the v-qitnp fiepo, ae is connected by ainalisption 1081 and 1.082 to the cant.iaIor 10 rie the vqniip prof / r'fie. Lorpoue the fat ^ arerne valve is in pc: i .n # 1 the c c, .i.ra; ort A10 oet h the sub-operating name, nlnsi the rFàs3ort 1.2b tar..rn the OQu11n3eHH 1, or / 2a

  <Desc / Clms Page number 72>

 in the position shown.



   ,
The current divider valve 1057 is set as such. so that more fluid flows through outlet 1062 and through 1063. Fluid from 1062 flows through. line 1064, the pressure control valve 1061 and from there to the tank via lines 1075, 1074 and the restriction
1008. Fluid from 1063 flows through 1066, pressure relief valve 1065, line 1071, cut-off valve 1072 and from there to reservoir through 1074 and restriction 1008.



   Thus it can be seen that only part of the fluid flowing in the working pressure line 1002 (which is supplied mounted by the trolley pump 60a) passes through the pressure control valve 1061 and that the current division is controlled by the adjustment of valve 1061., a certain unit pressure being established in) pipe 1060 and 7:

  Control unit 1056. As the carriage moves forward from the "Standby" position there is little resistance offered and the above described elements are arranged such that the pressure The unit in the control unit 1056 is greater than that in the unit 1054. Thus the arm 1053 is turned to the right causing the maximum flow rate of the pump 59a and the carriage moves forward at high speed.



  Control valve 1061 is; connected with a button which controls it 1083 (fig. 1) and the pressure setting is indicated by the reference 1084 which can be calibrated in power, for example in tons. The speed with which the trolley moves can be observed on flow meter 1085 which can be calibrated in cm per minute for example *; The function of the self-timer 1080 '1072 can be explained self-timer 1080 and the timer 1072 will be explained briefly. -
Note that line 1055 from the discharge side of the carriage feed pump 59a supplies fluid to the hydraulic tailpiece thrust bearing.

  <Desc / Clms Page number 73>

 



   The bearing bears numbers marked corresponding to those used for the description of FIGS. 18 and 19.



   Line 1055 from the discharge side of the cart feed pump 59a also feeds liquid to cylinders C1 and C2 and forces pistons P1 and P2 to move tail piece stopper 250 against the screw or carriage stopper
251. Cylinders C3 and C4 are connected with the inlet side of the cart feed pump 59a through lines 1087, and 1051.



   As said above, moving the carriage forward causes the tail piece, jig, rollers, blank holder and blank to move forward as well, these elements moving as a unitary whole.



   In the following description, it will be assumed that the rollers and the tail piece have been adjusted so that after the blank has contacted the spindle, the tail piece and the rollers simultaneously come into contact with the spindle. contact with the blank.



  After that, the forward movement of the carriage is stopped.



  Since the tail piece is adjustable longitudinally with respect to the carriage or rollers, the tail piece can be arranged such that either the rollers or the tail piece first come into contact with the blank.



   When the charot has stopped, the hydraulic system works so as to automatically operate the machine for the forming work, as follows:
With the carriage stopped, 1 press in the pipe. The dump 1032 of the cart feed pump is immediately increased and this causes the controller 1054 to push the pump control arm 1053 slightly beyond the dotted position. Thus the pumping direction is momentarily reversed and the pressure in 1035 rises, while it falls in 1032.

   The pressure differences due to the overturning of the pump actuate the operation control valve 1023 because

  <Desc / Clms Page number 74>

 the chamber 1023b is connected to 1035 by the pipe 1105 and the chamber 1023c is connected to the pipe 1032 by the intermediary of the pipe 1106. The pressure difference triggers the slide 1023a downwards this yes has the effect of actuating the pushbutton valve 1018 because moving the slide down connects working pressure line 1003 with line 1022 yes is connected with chamber 1018c of the pushbutton valve.



   It should be noted that reversing the pump 59a causes the cart feed motor 620 to reverse and the cart tends to slowly move backward. As said above, the reversal is only momentary because the control unit 1056 returns the pump so as to start moving the carriage forward. The above movements are only very small and the carriage comes to a stop. With the control devices-1054 and 1056 keeping the pump near 'its zero position but they are sufficient to prevent leaks in the' system, for example through the gaps in the hydraulic tailpiece bearing.



   Also it is to be noted that after valve 1023 has been actuated, slide 1023a moves to the position shown in the drawing because the pressure in line 1032 is at the discharge pressure and the line 1035 is at inlet pressure. '
While the carriage comes to a stop, the. push-button valve a. actuated which brings program valve 800 to position # 2. This is done as follows:

   
The operating pressure is transmitted to the. push-button valve chamber 1018c and this pressure moves slider 1018a down against spring 1018b. The operating pressure of the carriage is transmitted from line 1005 through 1015, 1021, valve 1018 and line 893 to the ratchet mechanism of the program valve which moves to position the valve on # 2.

  <Desc / Clms Page number 75>

 



   After action of the push-button valve the spring 1018b pushes the slider upwards to the position of the drawing because the pressure in the chamber 1018c is again the under-operating pressure due to the return of the slider 1023a to its position starting point.)
When the program valve has been positioned on # 2, line 806 remains at operating pressure. The pipeline
810 changes from sub-operating pressure to operating pressure and line 811 remains at sub-operating pressure, The operating pressure in 810 is transmitted to the blank support valve 1086 through line 1082. The operating pressure in the chamber 1086e causes slider 1086a to move downward against spring 1086b.

   The blank support cylinder 346 is then connected with / the under-draft pressure is then under-operating pressure through line 1090, valve 1086, line
1090 ', the line 1093, which is connected with the under-operating line 1010' The blank support cylinder 345 is connected with the operating pressure, through the check valve 1091, the valve 1086 and the working pressure line 1004 The support moves down quickly because the. restriction 1092, is bypassed.

   The above connections cause the blank holder to move downward and stay there as long as the operating pressure is maintained in chamber 1086c. As the blank holder moves downward the blank holder moves downward. blank remains clamped between the spindle and the rollers and the tail trap.



   As has been explained in connection with fig. 36, the movement of the blank supports to the LOW position causes the jig locking device 459 to act on the bed. In addition, as said about fig. 36, the movement of the blank support in the DOWN position, causes the release of the brake 704 'and the engagement of the clutch 704. At this moment the spindle begins to turn this yes causes the rotation of the blank,

  <Desc / Clms Page number 76>

 pebbles and tail piece.



   It is recalled that the control units 1054 and 1056 keep the pump 59a near the zero flow point when the carriage and the rollers are immobilized against the blank. As the blank and the rollers begin to rotate, the resistance offered by the blank to forward movement begins to decrease. The system provided for the 1054 and 1056 control devices makes
 EMI76.1
 these automatically adjust the flow rate of pump 59a to allow the carriage and rollers to begin moving forward for the forming work.



   The carriage and rollers first move forward at slow speed for a predetermined distance and then at a speed depending on the resistance offered. If the resistance is low, the advancement is great 'and. if the resistance is great the advancement is weak.
 EMI76.2
 



  'It has been found that the alet, 5,' is' moved forward at slow speed during 1. prti, on ihtial of.operation 1 ;, .. ...,, j; j '';. 'For forming the Tisq 4p ,, d: ç, cracks * in the blanks are practically eliminated. Usually speed thirty is maintained on a
 EMI76.3
 distance equal to the original blank thickness or until the material has been moved enough to be applied firmly to the working surface of the spindle. - This slow starting speed is obtained as follows;

   
During the time when the carriage and the rollers move at high speed until they come to a stop against the blank, only part of the fluid coming from the line 1002 at operating pressure has passed through the pressure control valve 1061 which establishes a certain unit pressure in the control device 1056. During the first part of the forming operation, the pressure in the device 1056 is maintained over a certain distance, as said above, and, like the resistance offered by the forming operation. The roughing is a little high due to the fact that the spindle increases its speed, the rollers move upward at a slow speed.

  <Desc / Clms Page number 77>

 



  After a predetermined interval all the fluid coming from the working pressure line 1002, has passed through the control valve 1061, which causes a pressure increase in the control unit 1056.



   Celp tends to move the arm 1053 of the pump 59a to increase its flow rate and increase the forward movement speed given the resistance offered. Incidentally, the resistance offered by the blank generally depends on the speed of rotation of the blank, on the. nature of its material, its original thickness and the percentage reduction adopted. Transmission of all fluid from line 1002 through control valve 1061 is accomplished by means of delay device 1080 and delay valve 1072 as explained below.



   It is recalled that, when the program valve is positioned on # 2, line 810 is at. operating pressure. It is transmitted in lines 1082 and 1081 to the time device 1080 which is adjustable so that the amount of fluid passing can be controlled. Time device 1080 is connected with valve 1072 through line 1076 and the operating pressure in valve chamber 1072c causes slider 107'2a to begin to move to the left center spring 1072b.

   The time device 1080 constitutes a restriction and limits the rate of passage of the fluid to the chamber 1072c and therefore the slider 1072a moves slowly against the spring 1072b. The orifice. ±. of the cut-off valve begins to be covered by the slide so as to cut off the passage of fluid from line 1071 to tap point 1007. When port C is covered, port b begins to be uncovered and it y, fluid flow from 1071 to 1073, so the total amount of fluid from the operating pressure line 1002 flows through the pressure control valve 1061 and causes the unit pressure to rise

  <Desc / Clms Page number 78>

 in the control device 1056.



   This pressure in 1056 is maintained as long as the. line 810 of the valve, the program is at operating pressure.



   The 1061 control valve is adjustable. The adjustment of the valve will determine the initial forces pushing against the workpiece and for any given force (as indicated in item 1084) a certain forward speed will be reached. By adjusting valve 1061, the forward speed can be varied.



   When the carriage moves forward and the jig is blocked on the bench, the finger 10 is lowered. This has the effect that the roller supports are moved so that the rollers follow the path controlled by the jig. The track marker mechanism influences the movement of supports 6 and 7 as follows:
The tracer mechanism is arranged so that the finger 10 always takes a position of equilibrium against the jig. The discharge side of the roller support feed pump 58a is connected by 1093 with a current dividing valve 1094, connected to motors 131 and 132 by lines 1095 and '1096.



  The function of valve 1094 is to keep the flow rate in lines 1095 and 1096 equal regardless of the unit pressure in the lines. This mode of action is well known.



     Ires pipes 1095 and 1096 are connected, with the valve 471 by the pipes 475 and 474. It is recalled that, when the finger 10 is not lowered, the valve is requested in such a way that the interval G1 is normally open and gap G2 normally closed, so fluid from line 1095 flows through motors 131 and 132, thence through line 1096, line 474, gap G1 , the valve 471, the pipes 481 and 482, through the pilot valve of the roller supports 1100, the pipe

  <Desc / Clms Page number 79>

 
1101 and returns to the inlet side of feed pump 58a through line 1102.



   When the fluid flows in the direction described above, the motors 131 and 132 act to drive the supports 6 and
7 inward until the plotter finger 10 is in contact with the jig 16. At this time the finger is moved and the gap Gl is closed and the gap G2 open. This has the effect of tending to move the roller supports outwards as follows:
With the interval Gl closed and G2 open, the fluid passes through the motors in the opposite direction, that is to say from 1096 through the motor then 1095, 475, G2, 431, 481, 482; 1100th 1101 and return to the admission side through 1102.



   With the movement of the supports outwards, the finger begins to leave the jig and assumes its tilted position.



   The motors 131 and 132 are again reversed and move the supports and the finger inward. The plotter valve 471 is arranged, and particularly the G1 and G2 intervals, so that an equilibrium condition is reached and the plotter finger remains in contact with the ga.barit.



   When the rollers are stopped against the blank as described above, the marker finger assumes a starting position against the jig (fig. 3) in accordance with the operations explained above. When the carriage begins to move towards the jig. 'forward, the marker finger also begins to move forward and, since the template is fixed, the finger is moved. As a result, the rollers begin to move outward, but as soon as this occurs, the movement of the finger is suppressed and the rollers tend to move back inward. The above movements are obviously extremely small and in practice a condition of equilibrium is established such that the marker finger follows the contour of the jig while the carriage continues to move forward.

   The rollers are obviously moved so

  <Desc / Clms Page number 80>

 so that they also follow paths identical to that of the template. At the end of the forming operation, the rollers are in the position shown in fig. 5 and 6.



   With respect to the pilot valve 1100, it should be noted that the valve has a slide 1100a, a spring 1100b, and a chamber 1100c. The chamber is connected with the operative pressure through line 1097 yes is connected with the line
811 of the. program valve 800. Thus the spring 1100b forces the slide 1100a in the position shown.



   The pressure in line 481, due to the fluid passage described above, is not sufficient to actuate control trigger finger 480. Its operation will be described later.



   In fig. 2 a front catch 1012 and a rear catch 1014 are mounted on a guide track 1013 placed on the side 26 of the bench. The tocs are adapted to actuate the. carriage limit valve 1011 and stop the carriage at the front and rear end of the machine. (In fig 2 the carriage is in the bare position in fig 2 and consequently the limit valve
1011 is at a point between the tocs.). Each of the tocs is adjustable along the way so that the. Stroke length of the carriage can be adjusted forward and backward. The stops 1013 'are mounted on the track so that the toces cannot be set beyond the extreme limits of the machine.



   The forward catch is set on the bed so that the forward stroke of the carriage and rollers is stopped when the blank has. been formed into the desired object. The limit valve 1011 then comes into contact with the front fuse 1014., Lorsoue the limit valve 1011.contacts the front fuse, the slide 1011a is moved against the spring lOllb. The program valve is then placed on # 3 because the ratchet mechanism 863 is supplied with operating pressure from the pipelines ''
893 ', 1017, valve 1011 line 1016 and 1015 which is connected

  <Desc / Clms Page number 81>

 to line 10.05 at operating pressure.



     When the program valve is positioned on # 3, lines 806 and 810 go from operating pressure to under-operating pressure and line 811 goes from under-operating pressure to operating pressure. The following actions result.



   The underoperating pressure in line 806 is transmitted to shut-off valve 1031 which immobilizes the carriage. The chamber 1032c of the valve is in communication with the. pipeline
806 via line 1030, the roller bearing limit valve
1026 and 19 line 1025. The spring 1031b pushes the slide upward in the position shown and the flow of fluid is stopped in the direction of the valve 1034 and the carriage advance motor 620. Thus the carriage cannot more move forward. The pump 59a returns to zero flow in the manner already described. The suboperating pressure in line 806 is also communicated to the direction valve.

   The chamber 1034c of this valve is in communication with the line 806 through the line 1040. The spring 1034b moves the slider upward to the position shown. Thus when the stop valve 1031 is actuated again, the fluid coming from the discharge side of the pump 59a is transmitted to the line 1043 and the motor 620 will act to move the carriage towards the rear of the machine.



   When the forming operation is completed, the rollers are moved to their outermost position and remain in this position when the carriage goes backwards. The reason for this is to keep the rollers and supports away from the object mounted on the spindle. This rearward movement is operated by the click control 480 which moves the marker finger 10 as follows:
The operating pressure in line 811 is transmitted through line 1097 to the pilot valve 1100 for the withdrawal of

  <Desc / Clms Page number 82>

 roller support. The operating pressure in the chamber 1100c causes the slider 1100a to move to the left against the spring 1100b.

   Moving the slider to the left stops the flow of fluid from line 482 to line 1101 and transfers the flow of liquid from 482 to restriction 1120. The pressure in 482 is increased and reaches the pressure in 481. which increases the pressure in chamber 480c and moves stopper 480a outward to engage with cylindrical member 541 (Fig. 20) and lower the valve. The manner in which lowering the valve causes the roller supports to move outward has been explained previously.



   When the roller supports have moved to a predetermined position the charlot begins to move rearward and the stroke of the supports is stopped. These operations are controlled by the roller support limit valve 1026.



   The valve 1026 is mounted on the guide 35 (Fig. 3) and, when the support 6 meets the slide 1026a of the valve, the slide is moved to the left against the spring 1026b.



   The limit valve 1026 acts first to start the movement of the carriage backwards by actuating the stop valve 1031 as follows: As the slide 1026a moves to the left, the operating pressure in the line 1005 is on. communication via 1121., the limit valve 1026 and line 1030, with the shut-off valve. The operating pressure in chamber 1031c. causes the slide 1031a to move downwards and feed the fluid. towards the valve 1034. It is recalled that the direction valve has already been positioned to send the fluid to the motor 620 so as to move the carriage backwards.



   With regard to the movement of the carriage backwards it should be noted that the underoperating pressure in 810 of the program valve is transmitted to the delay cut-off valve 1072 through 1082 and 1081. The underoperating pressure in the chamber 1072e of this valve allows the slide 1072a to be moved

  <Desc / Clms Page number 83>

 by spring 1072b to right 1 - Liquid flow through 1073 is shut off and diverted by valve to point 1005 and liquid flow through pressure control valve
1061 is reduced. The pump 59a will be at its maximum output, and since there is little resistance to displacement, the carriage is pulled back at high speed.



   The second action of the linite 1026 valve is to stop the travel of the roller supports and keep them stationary as follows:
Further movement of slider 1026a to the left connects line 1122 with 1123. Line 1122 is connected to line 1096 and 1123 is connected to. 482. Thus with the link between 1122 and 1123, the motors 131 and 132 are short-circuited and the movement of the supports towards the outside is stopped. It should be noted that the brackets cannot move inward, as the plotter valve is moved by the finger click control, The brackets remain in their position when the carriage moves backward.



   Regarding the program valve, it is recalled that in position # 3, line 810 is at the suboperating pressure, which is transmitted to the blank support valve 1086 by line 1082. The pressure under- operating in the chamber 1086c allows the spring 1086b to move the slider 1086a upwards in the position shown. Rough support cylinder 346 is thus connected with operating pressure through line 1090, valve 1086, and operating pressure line 1004. Cylinder 345 is connected with operating pressure through restriction 1092. , valve 1086 and line 1093 which is connected with suboperating line 1010.

   Since the discharge from cylinder 345 passes through the restriction. 1092, the roughing support moves upwards at a slow speed. The reason for this

  <Desc / Clms Page number 84>

 Slow rise of the media is that the media has not come up before the carriage is far enough rearward so that the media is clear of the spindle.



   As the blank holder rises, the jig clamps 459 are released and the holder can slide freely on the bed. The under-operating pressure in cylinder 442 causes the carrier to rise toward the carriage until stopper 461 engages carriage stopper 448. '.



   As the blank support rises, clutch 704 is disengaged, brake 704 'is engaged, and the spindle slows down and stops.



   As the carriage moves towards the rear of the machine the carriage screw or 'stopper 251' engages the stopper 250 on the tail piece and the latter is pulled rearward with the carriage.



   The carriage will continue to move rearward until the carriage limit valve 1011 contacts the rear latch 1012. The action of the limit valve 1011 causes the program valve to be set to. 4 as follows:
Slider 1011a is moved upward against spring 1011b and the operating pressure from -1005 is connected through 1015, 1016 '., Valve 1011, 1017 and 893' to ratchet mechanism 863. '
When the program valve is on 4, lines 806 and 810 remain at underoperating pressure, while line 811 changes from operating pressure to underoperating pressure.

   As a result, the roller supports move inward and the carriage is stopped.



   With line 811 at suboperating pressure, the pilot valve for removing the roller supports 1100 is actuated. Line 811 is connected by line
1097 with the, chamber 1100c and the outlet pressure per'net

  <Desc / Clms Page number 85>

 the spring 1100a to move the slider 1100a to the right.



   Thus the flow of fluid through restriction 1120 is transferred to line 1101 and the pressure in the control chamber of the click finger 480c allows the spring
480b to move slide 480a to the left away from the bout marker valve. As the plotter valve is no longer influenced, the bias allows the roller supports to move inward as already described.



   As soon as the roller support 6 moves away from the limit valve 1026, the spring 1026b pushes the slide 1026a to the right and at this moment the connection between 1122 and 1123 is removed and the motors 131 and 132 are no longer short-circuited. . Thus the roller supports are free to move outward when they are made to do so by the plotter mechanism.



   Further movement of slider 1026a to the right actuates stop valve 1031 which stops the rearward movement of the carriage. It is recalled that, when the slide 1026a was actuated to the left, the operating pressure was established in the chamber 1031c of the stop valve. However, when the slider 1026a moves to the right, the line 1030 which is connected with the chamber 1031e of the stop valve, is connected with the line, 1025 which is at operating pressure because it is connected with the line. 806 program valve.

   Thus the pressure, under-operating in the chamber 1031c allows the spring 1031b to move the slider 1013 la upwards to cut off the power supply to the direction valve and the motor 620, with the carriage, is put on the line. 'stop.



   The suboperating pressure in line 806 is also connected by 1040 with the direction valve 1034.



  The pressure in 1 chamber 1034c allows the spring 1034b

  <Desc / Clms Page number 86>

 to move the slider 1034a upwards in the position shown and the direction valve is thus positioned to transfer the fluid to the motor 620 to drive the carriage forward when the stop valve is actuated.



   With the . above operations the machine is in the "HOLD" position. The finished object is removed from the spindle and replaced with another blank.



   It is to stir that removed it from the finished object and the. placing of another blank can be done by automatic devices, especially when the machine is used for automatic series production. Likewise, it is obvious that the insertion of a new blank in the support can by itself cause the start of operation of the machine instead of an action by the operator on the "Start" button. For example a switch to be actuated by the insertion of the blank can be arranged in the support, and cause the action of the delay mechanism which in turn acts on a solenoid to trigger the push-button slide 1018a.



   As has been described, the carriage and the rollers are moved forward by a system with constant pressure and variable flow. Providing a constant drive and feed pressure rather than a constant feed rate has various advantages. '
One of 'most important is that the feed rate varies with the resistance of the workpiece- For example', if the resistance offered by the workpiece is low, the feed rate is made automatically larger and vice versa. This automatic variation of the forward speed is important because in the case of high resistance too high a small speed will cause tearing of the blank.

  <Desc / Clms Page number 87>

 



   When certain metals and shapes of blanks are used, or with certain forces of the object to be formed, the resistance offered by the log may be greater during the first part of the forming operation and become. 'lower with the end of the operation. Thus, by automatically increasing the forward speed, the speed of the operation can be increased. Likewise, it is often desirable to force hollow objects made of two different types of metals eg with steel near the narrow end and copper near the mouth. The resistance offered by copper being lower than for steel, it is advantageous that the forward speed changes automatically.



   Another advantage is that the overall speed of machine operation is considerably increased. For example, when the carriage goes forward towards the spindle from its "HOLD" position, it is moving at a high speed. Likewise, a high speed of movement is obtained when the carriage is brought back at the end of the operation. If a constant forward speed were used, the carriage would obviously move forward and backward at that particular chosen speed. In the case of constant forward speed, a mechanism can be provided which changes the speed at the particular instants mentioned above.

   However, such a mechanism requires an adjustment relative to the bench so that 1 ,. correct speed is applied to the correct part of the cycle.



   Another advantage of the constant pressure supply is that the machine is made particularly suitable for automation. For example, when the carriage and rollers move forward from the "WAIT" posttion to reach the blank, the change from fast approach speed to trivnil advance speed is caused automatically.

  <Desc / Clms Page number 88>

   pulling. In fact, stopping the rollers against the Draft itself initiates the operating cycle.



   Another advantage is that the forward speed can be adjusted with a simple button. Over the full range of work variation for which the machine is designed, adjusting the feed rate does not affect the ability of the system to move the carriage at a rapid feed rate during the forming operation. is not in progress.


    

Claims (1)

CLAIMS 1.- Machine for cold mechanical working of metal, characterized in that it comprises a head piece mounted on an elongated bench and means for rotatingly mounting on this head a spindle suitable for supporting a blank to be worked, means for supporting one or more tools which can be moved both in a direction parallel and in a direction transverse to the axis of rotation of the spindle, a head or tail piece slidably mounted on the bed and adapted to be elastically engage with the tool holder, means being provided to move the tool holder and the headstock simultaneously or independently of each other. 2.- Machine according to claim 1, characterized in that a carriage is slidably mounted on the bench and can move in a direction parallel to the axis of rotation of the spindle, the tool support means comprising said carriage and one or more tool supports movable transversely to the carriage, the headstock being adapted to elastically engage with the carriage. 3. - Machine according to claim 2, characterized in that the head against is elastically supported by the carriage, the elasticity being exerted in a direction along the axis of the spindle. 4.- Machine according to claim 3, characterized in that hydraulically actuated means are provided to imprint its movements to the carriage and to the elements which it carries and to cause independent movements of the counter-head and / or tool holders. 5. - Machine according to one that conqu e of claims 2 to 4, characterized in that a jig is mounted so as to <Desc / Clms Page number 90> elastically engage with the carriage in order to be sliding or fixed relative to the bench. 6.- Machine according to claim 5, characterized in that the jig is disposed on a sliding support mounted on the bench and connections are arranged between the carriage and said support acting so that the support moves with the carriage or is fixed on the bench while the cart is moving. 7.- Machine according to any one of the preceding claims, characterized in that the tool support comprises two roller supports. 8.- Machine according to any one of claims 2 to 7, characterized in that it comprises a support for the positioning of a blank before its engagement with the counterhead, said support being mounted on the carriage. so that it can be moved in relation to it. 9.-. Machine according to claims 2 and 5, characterized in that the tool support member (s) move under the control of a guide or marker mechanism comprising a control finger engaging with the jig. 10. - Machine according to claim 2 or 4, characterized in that it comprises means for hydraulic action by pressurized fluid comprising a hydraulic motor and a pump mounted on the carriage to move the latter along the bench. , a second motor and pump assembly mounted on the carriage for moving the tool support (s) and a pressurized fluid reservoir mounted on the carriage and having connections to each of the hydraulic assemblies. 11. Machine according to claims 8 and 10, characterized in that a third pressurized fluid assembly is mounted on the carriage to act on the blank support, this assembly being connected to the reservoir. 12. - Machine according to claim 10 or 11, character- <Desc / Clms Page number 91> This is because the first hydraulic assembly is adapted to exert a constant unit pressure to move the carriage, said pressure being able to be adjusted to different values. 13.- Machine according to claim 12, characterized in that the first hydraulic assembly is adjustable so that the unit pressure can be adjusted to different values. 14. Machine according to claim 12 or 13, characterized in that it comprises a delay mechanism associated with the first hydraulic assembly with a view to being actuated for a predetermined length of time and for a predetermined position of the carriage. on the bench. 15.- Machine according to claims 7 and 11, characterized in that it comprises a fourth hydraulic assembly connected between the carriage and the template support to ensure elastic engagement between them and a fifth assembly connected between the carriage and the headstock with a view to their elastic engagement, these two assemblies each being connected with the first hydraulic assembly. 16.- Machine according to claim 2, 4 or 10, charac- terized in that it comprises a control mechanism which ensures the following sequence of operations: actuate the workpiece support to position a blank, supported on it by. in a predetermined manner with respect to the axis of rotation of the spindle, actuate the tool supports and the counterhead to move them towards the head piece for the engagement of the tools with the blank and the clamping the workpiece on the spindle, causing the machine and the workpiece to rotate and actuating the tool holders to move them in a direction having components both parallel and transverse to the axis in view perform a blank forming operation. <Desc / Clms Page number 92> 17.- Machine according to claim 16, characterized in that the control mechanism comprises a time-delayed device for controlling the speed of movement of the tools, or rollers during this operation, the speed being initially slow and then relatively greater. 18.- Machine according to claims 8 and 16, characterized in that the control mechanism acts so that the workpiece support positions a blank in a predetermined manner with respect to the axis of rotation of the spindle, before causing the tool supports and the headstock to move towards the head. 19. Machine according to claims 5 and 16, characterized in that the control mechanism causes the movement of the jig support parallel to the spindle axis when the tool supports move towards their engagement with the blank. , the jig support then remaining fixed relative to the tool supports and to the blank before the rotation of the spindle and the blank is actuated. 20. - Machine according to any one of claims 16 to 19, characterized in that the control mechanism causes the simultaneous movement of the carriage and the head against for clamping the blank on the head and causes the displacement sup - additional to the carriage parallel to the axis, then actuates the mechanism which controls the movement of the tool supports while the counterhead is engaged with the blank, all to ensure the shaping of the part. 21. - Machine according to claims 16 to 19, charac- terized in that the control mechanism establishes the following sequence of operations: causing the positioning of a blank in a predetermined manner with respect to the axis, cause the movement of the carriage, the counterhead and the jig parallel to the axis in order to fix the blank on the spindle, cause the jig to lock on the bench at a determined point in relation to the engagement position of the blank and the spindle, cause the rotation <Desc / Clms Page number 93> of the spindle, the blank and the rollers, cause the carriage to move further parallel to the axis and activate the mechanism for controlling the movement of the tool supports while the counterhead is engaged with the blank . 22. - Machine according to claims 7 and 9, charac- terized in that each roller support is adapted to receive one or more rollers, each roller having a working area defined by a curved surface of revolution and the control finger being a conical member movable with the support and axially adjustable, different portions of its conical face being selectable engaging with the jig, the selected portion having a radius equal to the radius of the surface of the roller mounted on the support. 23.- Machine according to claims 2 and 7, characterized in that it comprises two roller supports mounted on the carriage for displacement transverse to the axis of the spindle and sliding displacement along the axis of the spindle. bench, one guide screw being rotatably supported by the carriage and extending through each support, the screw having a set of right-hand threads and a set of left-hand threads, two nuts being carried by both supports and respectively engaging these threads, and means for rotating the screw so as to move the supports in opposite directions relative to the carriage. 24.- Machine according to claim 23, characterized in that it comprises a mechanism for resiliently positioning the screw relative to the carriage. 25.- Machine according to claim 23, characterized in that one of the nuts is adapted to be alternately kept fixed relative to its support or to be rotated relative to it. 26.- Machine according to claim 25, characterized in that the nut carries a worm wheel and the support carries a worm engaged with the wheel. <Desc / Clms Page number 94> 27.- Machine according to claim 23, characterized in that the screw is driven in rotation by two motors actively mounted on opposite sides of the carriage and each connected with the screw for its drive. 28.- Machine according to claims 24 and 27, characterized in that the connections between the motors and the screw allow axial movement thereof. 29.- Machine according to claim 27, characterized in that one of the nuts is adapted to be maintmu fixed relative to its support 'or to rotate relative to it. 30.- Machine according to claims 24 and 28, characterized in that it comprises means connected to the screw between the threads and with the carriage, for resiliently positioning the screw relative to the carriage, these means comprising a mounted collar. on the screw, roller bearings arranged on opposite sides of the collar and a spring mounted between each bearing and the carriage. 31. Machine according to claim 2 or 4, characterized in that the carriage is mounted on an elongate support having a general ton of a U-shaped channel, each side of the channel having a tongue extending therein. and the bottom a tongue extends upwards .. the carriage having a U-shaped lower portion engaged in this channel, each side carrying two rows of roller bearings cooperating with the upper and lower surfaces! tongues and the bottom having two rows of roller bearings cooperating with the respective edges of the upwardly extending tongue. . 32.- Machine according to claim 31, characterized in that. each side and the bottom of the lower portion of the carriage consists of a rolled steel plate assembled to the bottom by probing and comprising several spacers ?! in rolled steel plates welded on the bottom and sides. <Desc / Clms Page number 95> 33. - Machine according to claim 31, characterized in. that one of the rows of bearings on the sides of the carriage and on the bottom is provided to be adjustable with prior load. 34. Machine according to claim 2, 4 or 31, characterized in that the carriage comprises an elongated upper portion with a U-section, each side of the U having an inwardly extending tongue and the bottom of the U having an upwardly extending tongue and the tool supports are carried by a second carriage in this upper portion, the carriage having a U-section, each side carrying two rows of roller bearings cooperating with the upper and lower surfaces of the corresponding tongues extending inwardly and the bottom of the U having two rows of roller bearings cooperating with the respective edges of the tongue extending upward. 35.- Machine according to claim 34, characterized in that the sides' and the bottom of the upper portion and the sides and the bottom of the second carriage are constructed of rolled steel plates, the sides and the respective bottom being assembled by welding. 36.- Machine according to claim 34, characterized in that it comprises a spacer adjacent to the opposite openings of the upper portion, and a spacer between the sides of the second carriage. 37.- Machine according to claim 9, characterized in that it comprises a mechanism connected with the carriage and able to engage as desired with the control finger of the plotter mechanism in order to maintain the tool supports in one or more positions relative to the axis of the bench. 38. - Machine according to claim 37, characterized in that the mechanism comprises two handwheels arranged on opposite sides of the carriage, a stop for engaging the control finger, adapted to move transversely to the axis and -means connecting the handwheels and said stopper so that <Desc / Clms Page number 96> the rotation of one of the handwheels in the same angular direction moves the stopper in the same transverse direction. 39. - Machine according to claims 2 and 5, characterized in that it comprises stops on the carriage and on the jig support and a mechanism for urging the stops to come into elastic engagement to cause simultaneous movement. the carriage and the template, 40.- Machine according to claim 39, characterized in that it comprises a mechanism which can be actuated as desired, to prevent the carriage and the support from moving simultaneously. 41.- Machine according to claim 39, characterized in that one of the stops is adjustable. ' 42.- Machine according to claim 39, characterized in that the mechanism comprises a hydraulic cylinder fixed to the support and a piston sliding in the cylinder and fixed on said carriage. 43.- Machine according to claim 42, characterized in that the cylinder extends parallel to the longitudinal axis of the bench, and the piston is provided with an axial fluid passage- 44.- Machine according to claim 5, characterized in that the template support comprises a main carriage connected to the bench, a first adjustable arm carried by this frame, a pivoting connection between the arm and the frame., A suitable adjustment means to rotate the arm by moving it relative to the axis of rotation of the spindle, a second adjustment arm carried by the first on a pivot, the second arm being movable relative to the axis of rotation of the spindle. brooch. 45.- Machine according to claim 44, characterized in that the first adjustment arm carries a cylindrical extension and the adjustment means comprise a housing sliding on this extension and a slide carried by the frame with a pivoting connection between the slide and the housing and means for moving the slide. <Desc / Clms Page number 97> 46. - Machine according to claim 44, characterized in that the pivoting connection between the first and the second arm comprises: a shaft fixed to the first arm and passing through the second arm, a ring fixed to the shaft and engaging the second arm, the periphery of the ring bearing bosses, a second ring surrounding the first and carrying bosses to engage with the first, the second ring being engaged with the second arm and being of greater thickness than the first main ring and a nut screwed onto the shaft, which when tightened causes the engagement of the second ring to clamp the second arm between the ring and the first arm. 47. - Machine according to claim 7, characterized in that the roller support comprises roller mounting means connected with the support; a first mechanism ensuring the movement of the mounting means of the roller relative to the support in an arcuate direction relative to the axis, and a second mechanism ensuring the movement of the mounting means relative to the support and parallel to the axis. 48.- Machine according to claim 47, characterized in that the second mechanism comprises an eccentric connected with the roller support, a spindle connected with the assembly member of the roller and a connecting bar mounted between this spindle and the eccentric . 49.- Machine according to claim 47, characterized in that the roller mounting member comprises a plate having several arcuate slots and a sliding block mounted in these slots and the first mechanism comprises a toothed sector for moving the block in them. slits. 50.- Machine according to claim 49, characterized in that the block has two shoes respectively arranged in the arcuate slots, the toothed sector being carried by another of these slots and, the pinion being operable by hand and connected with the <Desc / Clms Page number 98> block and engaging the sector such that it moves the next block in an arc relative to the plate. 51.- Machine according to claim 50, characterized in that it comprises a longitudinal slot in an upper plate of the carriage, a shoe carried by the plate and deposited in this slot, a spindle carried by the plate, a connected control rod with this spindle and an eccentric mounted on the upper plate and connected with this rod. 52.- Machine according to claim 51, characterized in that a spring is mounted between the upper plate and the eccentric, bosses connected to this plate and bosses connected to the eccentric cooperating with each other. 53.- Machine according to claim 2 or 4, characterized in that it comprises drive means which can be actuated at will to move the carriage along the axis of the bench, drive means by hand. ., for the same purpose and a selector mechanism to activate one or the other of these drive modes. 54 ,,. Machine according to Claim 53, characterized in that it comprises a guide screw rotatably supported in the bed and fixed against displacement with respect to the longitudinal axis and adapted to be rotated or fixed against rotation, a drive motor being mounted on the carriage, a nut mounted on the screw being adapted to be driven in rotation by the motor to turn the screw, means being operable at will to block the screw against rotation and a hand drive system being connected with the screw and adapted to make it rotate, means being connected with the motor and actuable at will to lock the nut against rotation. 55. - Machine according to claim 54, characterized in that it comprises a hand drive shaft mounted on a casing connected to the bench and supporting the spindle, a gear on the screw being engaged with this shaft, a first brake effective if <Desc / Clms Page number 99> the motor is actuated to engage the gear which prevents rotation of the screw and a second effective brake if the motor is inoperative and which blocks the nut against rotation. 56 * - Machine according to claim 8, characterized in that the support for the positioning of the blank comprises a block fixed on the carriage, having a pair of opposed cylinders, a supported frame sliding on the block and having a pair pistons adapted respectively to slide in the cylinders and means connected to the frame and adapted to hold a blank to work. 57. - Machine according to claim 56, characterized in that the blank support means comprise an upper section in the form of a V and a lower section connected with the frame by a key and a groove, means for vertically adjusting the support relative to the frame and further comprises means for locking the support on the frame in each adjustment position. 58.- Machine according to claim 2 or 4, characterized in that the counterhead is rotatably supported by the carriage and a pressurized fluid device ensures the relative displacement of the carriage and the counterhead along the axis of the bench, this movement being elastic with respect to the headstock. 59.- Machine according to claim 58, characterized in that it comprises a mechanism for adjusting the position of the head against the carriage. 60 .. Machine according to claim 58, characterized in that it comprises a second hydraulic device comprising a chamber with an axial thrust bearing between the head and the carriage. 61.- Machine according to claim 58, characterized in that the counter-head is carried by a frame carried in the carriage 62.- Machine according to claim 61, characterized <Desc / Clms Page number 100> in that it comprises a mechanism varying the axial position of the frame relative to the carriage. 63.- Machine according to claim 61; characterized in that it comprises a pair of opposed pistons and cylinders connected between the carriage and the counter-head piece and adapted to elastically hold the carriage and the counter-head, in position relative to each other, a fluid connection being provided between the chamber and the cylinders. 64.- Machine according to claim 63, characterized in that the fluid connection between the chamber and the cylinders comprises a throttling member. 65.- Machine according to claim 63, characterized in that it comprises a first pair of cylinders connected with the carriage, a second pair of cylinders opposite to the first and connected with the carriage, a first pair of pistons connected with the frame and cooperating with the first cylinders and a second pair of pistons connected with the frame and cooperating with the second cylinders, the fluid pressure supplied to the cylinders moving the frame towards the spindle. 66.- Machine according to claim 65, characterized in that the first and the second pair 'of cylinders are arranged so that a plane passing through the axes of the first and a plane passing through the axes of the second intersect between them , 67.- Machine according to claim 62, characterized in that the adjustment mechanism comprises a shaft carrying an adjustment knob mounted on the carriage, a worm on this shaft, a second shaft mounted to rotate on the carriage and extending along the axis, the second shaft carrying splines at one end, a screw wheel on this second shaft meshing with the worm, a threaded sleeve on the carriage and having splines engaging with those of the shaft and a stop carried by the frame and engaging with the sleeve. <Desc / Clms Page number 101> 68.- Machine according to claim 65, characterized in that the frame comprises two heads and an intermediate body having an axial opening receiving the head against, the first pair of pistons being mounted on one of these heads and the second pair on the other, all pistons extending parallel to the axis of the opening. 69.- Machine according to claims 64 and 68, characterized in that the fluid chamber is constructed between the counterhead and one of the heads, fluid connections being provided between said chamber and the first pair of pistons, these connections comprising the throttle organ. , 70. - Machine according to claim 58, characterized in that the fluid pressure device is connected with the carriage and with the counter-head and adapted to urge the oontre-head towards the spindle when the carriage moves along the bench in away from the spindle, and to cause the carriage to move towards the spindle when the head is engaged with the blank. 71.- Machine according to claim 1 or 4, characterized in that the spindle shaft and the counterhead shaft are rotatably mounted in supports t one of them is provided with a bearing Axially thrust hydraulic system comprising an annular fluid passage disposed around the shaft and formed between the support and a ring movable axially with the shaft, and means supplying a flow of pressurized fluid through this passage whereby the pressurized fluid in the passage absorbs the axial thrust. 72.- Machine according to claim 71, characterized in that annular fluid passages are arranged around the spindle and formed between the support and the annular member, and an annular fluid chamber interconnects these passages, this chamber having from connections to be placed under the pressure of the fluid, <Desc / Clms Page number 102> 73.- Machine followed claim 72, characterized in that the annular members-comprise a radial surface ,, having two annular surfaces facing each other with another pair of annular surfaces provided on the support to form a pair of connected annular gaps. between them by the fluid chamber. 74.- Machine according to claim 71, 72 or 73, characterized in that the annular passage has a radial width which does not exceed 5 hundredths of a mm. 75.- Machine according to any one of claims 71 to 74, characterized in that the annular member comprises a di sque fixed on the spindle. 76. - Machine according to claims 72 and 75, charac- terized in that the fluid chamber is formed in the disc. 77.- Machine according to any one of claims 71 to 76, characterized in that the spindle is supported by roller bearings adapted to allow rotation and axial displacement of the spindle. 78. - Machine according to any one of claims 71 to 77, characterized in that the hydraulic thrust bearing for the headstock comprises two annular passages, one on each opposite side of the support and annular members associated with each. on opposite sides, the pressurized fluid supply member being arranged to supply a flow of fluid to the passages on the opposite sides and means being provided to control the flow of fluid through these passages according to the demand. direction of axial thrust on the spindle. 79. Machine according to claims 72 and 78, characterized in that it comprises a pair of annular passages on each side of the support and a pair of annular chambers one on each side, each chamber connecting the pair of passages on each side. the respective side of the support and the fluid flow control member comprising a mechanism operable when the thrust? <Desc / Clms Page number 103> axial is exerted on the spindle by the operation of the machine to send fluid into the chamber whose pressure increases due to this thrust and in proportion to its magnitude. 80. Machine followed claims 75 and 78, characterized in that, A pair of discs are attached to the spindle, one on each side of the support and one or both discs are seen with teeth to drive the spindle. brooch. 81.- Machine according to claim 79, characterized in that the fluid pressure mechanism comprises an intermediate chamber along the support and enclosing a slide having its ends cooperating with the annular surfaces of the support defining an opening 4 each longitudinal end of the intermediate chamber for communication of the fluid pressure, to the adjacent annular chamber, said slider being arranged in the intermediate chamber in such a way that it moves in response to the axial thrust in s 'away from the fluid inlet opening into the adjacent annular chamber to absorb the axial thrust. 82.- Machine according to claim 81, characterized in that the slide carries two spaced apart collars defining a middle portion and end portions in the intermediate chamber, the outer surfaces of the collars being sufficiently spaced from the wall. of the chamber to allow communication between the middle portion and the end portions, a fluid connection being provided in the support and opening into the middle portion. 83.- Machine according to claim 82, characterized in that the slide has a cylindrical end portion projecting each of the collars in the responsive end portion of the intermediate chamber, this end portion of the slide having an end face which cooperates with the adjacent surface annun area of the support. <Desc / Clms Page number 104> 84.- Machine according to claim 82, characterized in that the end surfaces of the middle portion of the chamber are larger than the neighboring ends of the adjacent end portions of the intermediate chamber. 85.- Machine according to any one of claims 71 to 84, characterized in that the opposing surfaces defining a fluid passage are mirror polished. 86.- Machine according to any one of claims 81 to 85, characterized in that the slide is mounted in roller bearings. 87. = Machine comprising a hydraulic thrust bearing for a spindle, characterized in that it comprises an annular passage for the fluid, formed around the spindle and formed between the support and an annular member movable axially with the spindle. , means, being provided for causing a flow of pressurized fluid through said passage so that the fluid in the passage absorbs the axial thrust. 88. - Machine comprising an elongated bench, a carriage sliding on the bench and adapted to move along the longitudinal axis between stops, characterized in that the carriage comprises a template support slidably mounted on the bench and carrying stopper members and a mechanism for bringing these stops into resilient engagement to produce simultaneous movement of the carriage and the jig support. 89. - Machine comprising an elongated bench and a carriage mounted to slide on the bench and adapted to move along the longitudinal axis of the bench, characterized in that it comprises a counterhead carried by the carriage and hydraulic devices to move the carriage and the headstock in a direction parallel to the axis, the headstock yielding elastically during this relative movement. <Desc / Clms Page number 105> 90.- Machine tool characterized in that it comprises two tools, for example a spindle and a roller, adapted to engage with a blank to perform at least one working operation of forming the blank, a mechanism ensuring the relative displacement between the tools for the operation, means acting when a blank to be worked has been engaged with one of the tools to determine the starting point of the forming operation and a mechanism for controlling the displacement relating above comprising a regulating member, for example a template, connected with these means to be automatically positioned for the forming operation.