US2213450A - Punch press - Google Patents

Description

Sept. 3, 1940.

G. E. MUNSCHAUER ET AL PUNCH PRESS Filed 001. 30. 1939 4 Sheets-Sheet 2 INVENTORS GEORGE E. MU/VSC'HAUER FEEDER/CK E MUA/SCHAUER 7 @4044, ATTO NEYS 5 p 1940- G. E. MUNSCHAUER ET AL 0 PUNCH PRES S Filed Oct. 50, 1939 4 Sheets-Sheet 3 INVENTO R5 FQQ 3 650265 5. MU/VSCHA 05/2 6 '5/25o52/c/z 5. MUA/SCHA (/ER ATT R N EYS Patented Sept. 3, 1940 PATENT, OFFICE \2,z13,45o\ PUNCH mass George E. Munschauer and Frederltik E. Munschaucr, Buffalo, N. Y., assignorsto Niagara Machine and Tool Works, Buffalo, N. Y.

Application October 30, 1939, Serial No. 301,964

22 Claims.

This invention relates to punching and stamping machines and has particular reference to machines of the class commonly called punch presses.

While the art with which the present invention deals is comparatively old and one in which activity has been continuous and, in fact, on an ever widening front, there has been relatively little fundamental change in the construction of presses themselves, speaking especially from the structural aspect and also with reference to the general arrangement of the operating instrumentalities of punch presses. What development has ensued has been directed chiefly to improvements in the specific construction and operation of individual elements and working units of machines of this class without substantial alteration of their cooperation or arrangement with respect to each other.

In presses of the general class into which the machine of the present invention falls, the major portion of the structural frame work of the press comprises an integral element, usually of cast iron or steel. The press of our invention has an element which corresponds in its primary function to the press frame of the prior art but in the press frame of our invention the component parts are so arranged and presented as to greatly increase the strength of the composite element and the potential stresses which may safely and efiiciently be applied without undue deflection of the various stress members.

In other words, in our new punch press, the stress elements of the frame member are so shaped and arranged that the available resisting moments at all cross sections which are stressed during operation of the press are very much higher than hasheretofore been the case with presses ofcomparable size, weight and die capacity. This signal advantage is in part attributable to the new arrangement and conformation ofstress elements as such and in part to the novel arrangement of the transmission agencies between the driving motor and the reciprocating slide of the press, ,whichnovel arrangement permits a more advantageous disposition of the stress elements. In fact, it is diflicult to state to which of the two factors named, the foregoing advantages of strength should be chiefly credited.

Referring to the novel arrangement of the transmission means, including the crank shaft and its connection with the slide, such arrangement affects potential strength of the frame structure in two ways. First, it permits the novel arrangement and shape of the stress elements themselves to be such as to afford the maximum internal resisting moment for given cross sectional areas; and second, it results in the external forces, which act against the stress elements and are engendered in the operation of the machine, being directed against the frame member in such manner as to minimize their resultant bending and twisting moments.

Another advantage resulting from the construction of the present invention is the very im- 1 portant one of increased safety of operation owing to the almost complete elimination of exposed moving parts. Further, in constructing punch presses in accordance withthe teachings of the present invention, the frames of the presses have substantially uniform metal thicknesses throughout, with the result that the danger of internal strains, which occur when relatively heavy and slowly cooling sections are combined with light and rapidly cooling sections in the same casting, is virtually abolished.

The provision of a punch press possessing the foregoing attributes and one which is inherently compact, without sacrificing anything material in the way of facility of assembly and manufacture, are among the important objects of the present invention. In the machine of the present invention, a slide is caused to reciprocate by the rotation of a crank shaft which is connected to the slide by a connecting member or pitman. The crank shaft is arranged to be selectively rotated, preferably by means of an individual electric driving motor which is housed within and supported by the frame work of the machine.

' The transmission and driving instrumentalities which are necessarily employed in transmitting rotative movement to the crank shaft and in accurately controlling and directing such rotative movements, both-as to speed and duration, are, in the case of the present invention, arranged in a wholly novel manner and so that the deflections attending the loads and shocks to which the various structural and transmission elements are subjected are very much less than in presently known and used constructions.

Further, in the utilization of the principles of the present invention, a press of given capacity as to both die space and strength may be constructed so as to require-less operating space than heretofore.

In the accompanying drawings, wherein an exemplary form of the machine of the present invention is illustrated:

Fig. 1 is a vertical cross sectional'view taken approximately on the center line of the machine and in a plane extending from the front to the rear thereof;

Fig. 2 is a front elevational ,view with portions of the upper part of the frame of the machine broken away;

Fig. 3 is a fragmentary rear view of the upper portion of the machine on a larger scale than Figs. 1 and 2;

Fig. 4 is a diagrammatic illustrtaion of suitable control mechanism for the machine; and

Fig. 5 is an enlarged fragmentary cross sectional view of one form of clutch and brake mechanism for the machine viewed as in Fig. 1.

In the illustrated embodiment we have shown a punch press of the inciinable type. While the principles of the present invention are susceptible of adaptation in punch presses of other types, the peculiar problems presented in the design and construction of inclinable presses, owing to the necessity for bodily moving and adjusting a large part of the framework of the press and the working parts carried thereby, frequently and during normal operation of the press, makes the present invention an even more valuable one when applied to the design and construction of inclinable presses.

For purposes of illustration of the principles of the present invention a specific punch press embodying those principles has been shown in the accompanying drawings and is described in detail herein but it is to be understood that nothing in this specification or in the drawings is to be taken as limiting the scope of application of the invention save as it is defined in the appended claims. In the drawings, like characters of reference denote like parts and the numeral I0 designates generally the principal structural element of the punch press.

The element so designated, which we shall refer to as the frame, preferably comprises a unitary iron or steel casting having a fiat bed portion I I upon which a die is adapted to be supported and secured, either directly or, as is more usual, with an intervening bolster plate. Upright structural members are arranged upon or adjacent the bed I I for supporting the press superstructure including the various instrumentalities which cooperate to provide a relatively movable slide for supportingand actuating the upper movable element of a die for working metal or other materials. .In the illustrated embodiment the upright structural members comprise a pair of columns I2 of hollow rectangular cross section, the columns rising from the opposite rear corners of the bed I I and being spaced from each other to permit work pieces or scrap to pass rearwardly from a die secured to the bed of the press.

The columns I2 may terminate at their lower extremities in portions which curve forwardly and come up beneath the bed and merge therewith as may be seen from an inspection of Figs. 1 and 2 of the drawings. The front walls of the hollow rectangular columns substantially meet the back edge of the die-receiving portion of the bed of the press and the back walls curve downwardly and forwardly and then forwardly and upwardly to terminate substantially at the front edge of the bed of the press. The portions of the column l2 which are disposed beneath the bed I I of the press are spaced from each other in substantially the same manner as the upright portions so that the portion of the bed I I which extends between such column portions may be provided with a suitable opening, as at I3, for the passage of blanks, scrap or work pieces or for the reception of spring pads, pressure plates or other die accessories. Maintaining lateral alignment of the upper and lower portions of each column also avoids twisting moments on the columns themselvm and limits the stresses on the columns to those due to flexure alone.

The lower portions of the columns I2 are provided with axially aligned bearings for the reception of fulcrum or pivot shafts H which are supported at their outer ends in bearings provided in a pair of base members IS. The base members I5 are each provided, preferably rearwardly of the fulcrum or pivot shaft I4, with a plurality of openings I6 spaced along a common arc struck from the center of the pivot shaft I 4. The columns I2 are provided with axially aligned openings which are spaced from the pivot shaft I l the same radial distance as the openings I8 whereby a pair of locking pins I I may be passed through the openings in the columns I2 and any aligned pair of the openings IE to secure the frame I II of the press in either a vertical or a selected inclined position.

The press illustrated is so proportioned that in its more inclined positions the lowermost portion of the frame I0 projects below the floor line and to permit full inclination a pit is formed in the floor or foundation between the base members IS in erecting the press.

At their upper ends the pair of columns I2 merge into and support a substantially rectangular or box-like housing portion 20 which is pro- 'vided with suitable means for supporting and housing the driving and controlling instrumentalities for the crank shaft of the machine and which serves structurally asa continuation of the columns I2. In the illustrated form the outer confines of the box-like housing portion coincide substantially with the outer confines of the pair of columns I 2 and form in effect an upper continuation of the columns I2 but without the space which exists between the columns below the housing portion 20. This relative conformation of the columns and the housing portion is preferred because of various considerations having to do with the structural efficiency of the machine and, as in the case of the association of the lower portions of the columns I2 with the bed II, the relative proportioning and disposition of the housing 20 and the columns I2 avoids inefficient and harmful combinations of the stresses resulting from th forces applied to these elements.

The housing portion 20 has as its components a bottom wall 2|, a top wall 22, two side walls 23 and 24, a rear wall 25, and a front wall 26, see Fig. 3. The side walls 23 and 24 and the front wall 26 extend substantially continuously from the bottom wall 2I to the top wall 22 but the rear wall 25 comprises, preferably, little more than a framing portion for receiving suitable removable closure devices whereby access may be had to the interior of the housing 20.

A vertically extending partition 28 divides the interior of the housing 20 into compartments 2! and 30, the former of which will usually be larger than the latter and is adapted to receive and house an electric driving motor 3| and suitable clutch and brake mechanism which will be hereinafter described in greater detail. The other compartment, 30, houses gearing which will also be more fully described hereinafter. A signal advantage is derived irom the provision of the two compartments 29 and 30 in that the compartment 30 may contain a plentiful supply of lubricant for the gearing therein without such lubricant interfering in any way with the operation of the electric motor-,the clutch and brake mechanism, and

other means disposed in the compartment 23.

The front wall of the housing 23 is provided on its outer or front face, and usually adjacent the lower portion thereof, with a pair of integrally formed and laterally spaced projections 33 and 34 for receiving a pair of adjustably and removably associated gibs 35 and 35 which are adapted to retain and guide a slide member or ram 31 for vertical reciprocation against the front of the housing 20. The slide member 31 is provided with suitable means for securely engaging the upper or movable element of a die. The adjustable and removable gib construction and the details of the slide are conventional and well known and since they do not directly and specifically form a part of the present invention, their details will not be further particularized herein.

Adjacent the upper portion of the outer or front face of the front wall 26 of the frame Ill there is an integrally formed projecting portion 4|! which provides a pair of spaced coaxial bearings 4| and 42 whose axes extend from front to rear of the punch press. The rear bearing 42 may in fact be said to be supported jointly in the front wall 26 of the housing 20 and in a portion of the projection 40.

The projection comprises a hollow casing having a top wall 44, side walls 45 and 46, a front wall 41, and a bottom wall 48. The rear wall of the hollow casing which comprises the projection 40 is identical with the upper portion of the front wall 26 of the housing 20. The bottom wall 48 of the projection 40 is provided with an upwardly directed approximately central formation 50 which provides a recess 5| in such bottom wall adapted to receive and provide clearance for the crank portion of a crank shaft. the upward formation 50 are spaced at all points from the interior of the top, side, front and rear walls which form the outer casing of the projection 40 so that, with reference to upward bending moments directed against the projection, considered as a cantilever beam supported upon the housing portion 22, spaced but rigidly constrained tension and compression members are provided.

The spacing of these wall portions and also the spacing of the corresponding wall portions of the casing portion 20 and the columns I2 is so proportioned throughout as to afiord substantially uniform strength. While the breadth of the entire frame is substantially uniform throughout, the depth of the cross sections, considered as beams, bears an approximate proportion to the magnitude of the moment of the external forces as such moments are increased at points more remote from the point of application of the force.

While the various portions of the frame have been shown as substantially closed hollow box sections, it will be clear that suitable provision must be made for supporting and removing cores in the course of casting the frame. This is preferably accomplished by locating core prints at points which coincide with relatively little stressed portions of the frame structure, such portions lying close to the neutral fibre of the frame, considering the various cross sections thereof as beam sections. may, after removal of the cores, be permanently closed by welding plates in or over the openings, which would be the case in the press illustrated The walls of The holes left by the core prints.

in the drawings, or the holes may be closed by removable plates or even left open. In any event the disposition of the holes is such as not to materially lessen the strength of the frame.

Adjacent the bottom of the projection 40 and at opposite sides of the recess 5|, front and rear, are the bearings 4| and 42 respectively, previously referred to. It will be noted from an inspection of Fig-1 that each of the bearings 4i and 42 is of substantial length and is supported and directly backed at each of its ends by either an inner or an outer wall portion of the projection 40. It will be further noted that each such backing wall portion extends directly vertically to the point where it merges with one of the spaced top wall portions and the rigidity and efllciency of this arrangement will be apparent.

The front bearing 4| includes a cylindrical bearing block 52 which is removably associated with the lower forward portion of the projection 49. This end may be accomplished by providing an arcuate or circular openingor recess 53 in the projection 4|]. The cylindrical bearing block may conveniently be held against accidental removal by screws 54 which pass through an annular flange 55 formed on the cylindrical bearing block and engage in the projection 40. This construction of the front bearing 4| permits ready removal or assembly of the bearing block 52 in the process of erecting or dismantling a punch press.

A crank shaft 50 for effecting reciprocation of the slide 31 has journal portions 6| and 62 which are supported in the bearings 4| and 42 respectively and intermediate such journal portions the crank shaft is provided with a crank 63, the crank pin of which engages rotatably with one end of a connecting member or pitman 64. The other end of the connecting member 64 is engaged with the slide 31 by means of a ball and socket joint designated generally 65 and which permits the connecting member 64 to incline freely with respect to the slide 31 as the opposite end of the connecting member is caused to revolve with the crank pin.

The details of the connecting member and of its connection with the crank 63 and the slide 31 respectively are not new excepting in that the plane of rotation of the crank 53 is at right angles to the plane of rotation of cranks as conventionally found in machines of the kind under consideration and consequently the axis of the crank shaft runs from front to rear of the machine generally and of the slide in particular.

Referring now to the means for rotating the crank shaft 6!! and for controlling its rotation, special attention is directed to Fig. l where the electric driving motor 3| is shown disposed in the housing 20 with its rotor shaft extending in a direction parallel to the extent of the crank shaft 60. In the present instance, the motor is mounted against the inner face of the side wall 23 and if desired the mounting of the motor may be such as to permit bodily adjustment of the motor to effect adjustment of the tension in a driving belt or chain associated therewith.

Such an arrangement is shown in Fig. 3 where a plate 10, to which the motor 3| is secured, is hinged to the wall 23 as at 1|. The edge of the plate 10 which is opposite the hinged mounting 1| is movable toward and away from the wall 23 to alter the radial disposition of the motor shaft and adjusted position thereof is secured by means of a screw 12 which is pivotally anchored to the wall 23 and projects provided in the front wall 26 and the partition 28 for the reception of the journal portions of the countershaft I5.

Referring to the end of the shaft I5 which it has been stated-is journaled in the closure means associated with the rear wall 25, attention is directed chiefly to Figs. 1 and 5. The opening in the rear wall 25 which has been hereinbefore described is provided with a composite closure comprising a lower member I6 of relatively rigid construction and an upper member 11 which need not be of such rigid construction since its only function is to close the upper portion of the opening. The lower member 16 is arranged to support a bearing for the end of the shaft I5 and,

referring to Fig. 5, such bearing is shown at I8 as being secured to a boss I9 formed on the closure member I8 by means of screws 80. The bearing I8 performs the further function of providing distributing means for a hydraulic system in a manner which will hereinafter appear.

The countershaft I5 is provided for the purpose of transmitting rotary motion from the motor 3| to the crank shaft 60 and, more particularly, for rendering ready and effective the accurate control of such transmission of motion. The countershaft I5 serves further to support a flywheel 8|, the function of which in a machine of the class under consideration is so well known as not to require mention. The flywheel is rotatably mounted upon the countershaft I5 and is in alignment with a pulley 82 which is fixed to the shaft of the motor 3| for driving engagement therewith through the medium of a plurality of belts 83.

To the side of the flywheel 8| there is rigidly secured an annular clutch element 84 which is internally splined for driving engagement with a pair of driving clutch discs 85 as appears at 88 in Fig. 3. A cooperating clutch element in the form of an externally splined collar 8! is fixed to the countershaft I5 as by the key 88 which appears in Fig. 5 and a plurality of driven clutch discs 88, in the present instance three, are internally splined for driving engagement with the collar 81. It will be noted that the driving and driven clutch discs 85 and 89, respectively, are alternately arranged in a conventional manner and if desired friction discs 90, secured to either the driving or the driven clutch discs, may be interposed. I

The end discs in the series so formed, in the present instance the two outer discs 89, are preferably provided with annular projections 8| which provide thrust faces for applying an axial compressive force against the series of clutch discs to establish driving engagement between the flywheel 8| and the countershaft I5. On one side, the left hand side as seen in Fig. 5, the series of clutch discs is provided with a relatively rigid abutment which comprises a collar or disc 92 which is disposed upon the countershaft I5 against a shoulder which is formed by an enlargement 93 of the countershaft I5. The collar 92 is externally threaded for engagement with an internally threaded collar or disc 94 which bears directly against the annular projection 9| of the left hand clutch disc 89. Adjustment of the abutment so formed is afforded by reason of the screw thread engagement between the collars 92 and 94 and adjusted position thereof is maintained by a pin 85 which enters one of a number of circumferentially spaced notches 98 disposed about the periphery of the collar 92. The pin 95 is carried in an opening in the collar 84 and is adapted to be manually withdrawn from engagement with a notch 96 against the resistance of a coil spring 91 which is disposed thereabout when it is desired to adjust the position of the abutment formed by the collars 92 and 84.

Before describing the means for acting upon the other end of the series of clutch discs to establish driving engagement between the flywheel 8| and the countershaft I5 reference will be had to a somewhat similarly arranged and cooperating brake assembly for preventing rotary movement of the countershaft I5 whenever the clutch mechanism just described is in a disengaged state. The brake mechanism comprises a rigid annular ring I which may conveniently be formed as an integral part of the frame I0 of the press. The ring I00 'has an internally splined opening which corresponds in function to the internally splined opening of the clutch element 84 and likewise provides locking engagement with a pair of externally splined brake discs I 0| Disposed alternately between the discs I0| are internally splined brake discs I02 which engage an externally splined collar I03 which is secured to the countershaft as by the key I04.

As in the case of the clutch mechanism, the end clutch discs I02 are provided with outwardly directed annular projections I which provide thrust faces for engagement by means which clamp across the series of brake discs to frictionally lock the countershaft I5 to the rigidly stationary frame portion I00 and thereby prevent rotary movement of the countershaft when such clamping means are operative. In the present embodiment abutment means, which are relatively stationary with respect to the countershaft I5, are provided for engagement with the series of discs at one side of the discs. Such abutment means are similar in construction to the abutment means which are associated with the clutch discs 85 and 89 and are preferably disposed at the right hand side of the series of brake discs as viewed in Fig. 5, that is, on the side of the brake discs which is remote from the clutch mechanism previously described.

The abutment for the brake discs comprises a collar I 08 which is disposed upon the countershaft I5 against a securing collar I 09 which is threaded to the shaft. The collar I08 is externally threaded to receive an internally threaded collar III which bears directly against the annular projection I05 of the right hand brake disc I02. Adjustment of the abutment is effected as in the case of the clutch mechanism, by means of the screw thread engagement between the collars I08 and III and adjustment is maintained in a similar manner by means of a. yieldably releasable pin II2 which may be engaged with any one of a series of notches provided about the periphery of the inner collar I08.

The clutch mechanism and the brake mechanism are spaced along the countershaft I5 to permit the interposition of clutch and brake operat ing means and in the present instance such means are combined in a single movable member, preferably in the form of a cylinder or drum I I4 having closed ends H5 and H8. The drum 9| of the clutch mechanism to a positionwhere the end wall H6 is disposed against the projec- 1 a simultaneous engagement of the other.

balanced out within the combined mechanism H4 is disposed about a circular member Ila whose periphery bears against the inner peripheral wall of the drum H4 and the member H8 is fixed to the countershaft whereby the drum I I4 is positioned for axial sliding movement along the countershaft I5 and between the clutch and brake mechanism. a

The drum H4 is also fixed for rotation with the countershaft I5 by reason of the fact that the axial opening in the end member II6 thereof is formed to engage the splined periphery of the collar I03, although the drum H4 is arranged to have free axial movement with respect to the collars 81 and I03. Axial movement of the drum H4 is limited in both directions by abutment of the ends IIS and H6 of the drum with the inwardly directed annular projections 9I and I05 of the clutch and brake mechanism respectively. Y

The aidal dimension of the drum and the distance between the inner annular projections 9| and I05 of the clutch and brake mechanism are so proportioned that relatively little movement of the drum brings it from a position where the end wall H5 is disposed against the projection tion I05 of the brake mechanism and in these opposite positions the clutch and brake mechanisms are respectively rendered operative.

The movement of the drum I I4 from one of its extreme positions .to another is quickly and forcibly effected and, by means which will presently bedescribed, the drum serves to bear against either the discs of the clutch mechanism or the discs of the brake mechanism in such manner as to press the discs against their associated abutment and cause the shaft to be frictionally locked to the flywheel 8| or the stationary ring I00 as the case may be.

Owing to the shortness and therapidity of the movement of the drum II4 it might be said that as a practical matter the disengagement of either the clutch or the brake is accompanied by In order that frictional engagement between the several discs of either the clutch or brake mechanism may be broken quickly upon movement of the drum I I4 to disengaging position, coil springs I I9 are provided for engaging the inner sides of the opposite end discs to spread the discs when pressure is removed from them.

Means for causing the drum II4 to be moved as indicated above and for causing pressure to be exerted thereagainst sumcient to maintain driving and braking engagement of the clutch and brake discs respectively for predetermined periods of time will now be described. It may be noted first, however, that the circular member H8 is securely held against axial movement upon the countershaft I5. This may be accomplished by providing collars I which occupy the entire space between the circular member I I 8 and the collars 81 and I03. It will be noted that the outer ends of the collars 81 and I03 abut the collars 92 and I08 respectively and that when the threaded collar I09 is tightened on the shaft I5 the entire series of collars, together with the circular member H8, is clamped firmly between the enlargement 93 of the shaft I5 and the threaded collar I09. A locking collar I2l for the collar I09 may be employed.

By reason of this arrangement of the several collars all axial forces which result from operation of the clutch and brake m are and there is no resultant thrust of the countershaft I5 against the faces of its bearings in the frame of the machine. All of the reactions engendered by the thrust of the clutching and braking actions take the form of direct axial stress in the portion of the countershaft I5 which lies between the enlargement 93 and the collar I09.

The .circular member II8 has 'spaced thereabout a plurality of cylindrical openings for the reception of pistons I22. While the number of openings may be varied to suit requirements, the form of clutch and brake mechanism illustrated in the accompanying drawings contemplates the provision of three such openings spaced equidistant from each other and at the same distance from the .axis of the member H8. The openings extend parallel to the axis of the counter* shaft I5 and they are all closed at one end as by the cap I23 shown in Fig. 5 to provide fluid chambers between the closed ends of the opening and the ends of the associated pistons I22.

The opposite ends of the several pistons I22 are adapted, when fluid pressure is introduced into the fluid chambers referred to, to bear against the interior of the end closure member H5 of the drum H4. Resilient means are provided for normally urging the drum II I. toward the brake mechanismand suchmeans are conveniently found in springs I25 which are disposed in openings I26 formed in the circular member II8, the openings being preferably of the same number as the pistons I22 and spaced about the member H8 in staggered relation with respect to the pistons I22.

with the end closure portion II6 thereof against I the projecting annular portion I05 of the inner brake disc I02. The pressure of the springs I25 normally produces suflicient force to brake the drive shaft and to frictionally lock it in a stopped position. When this is the case the left hand clutch discs 89 and 90 are spread apart by the springs H9 and rotary movement of the flywheel is not transmitted to the countershaft I5 by the clutch mechanism.

For operating the press when desired, means are provided for exerting a predetermined fluid pressure in the fluid chambers of the circular member I I8 and this pressure is suiflcient to overcome the combined resilient urge of the springs I25 and consequently the" pistons move to the left in their chambers as seen in Fig. 5. The left hand ends of the pistons bear against the inner wall of the end closure member 5 of the drum II 4 and move the drum into position where the member II5 of the drum acts against the seriesof clutch discs 85 and 89 to produce frictional clutching action and consequent driving connection between the flywheel 8| and the couning therefrom. The radiating passages I3I have continuations I32 formed in the circular mem with an axial bore I30 and passages I3I radiat-' member adjacent the right hand end thereof as viewed in Fig. 5.

Means for connecting the axial bore I with a source 01' fluid pressure are associated with the bearing 18 for the countershatt and in the preferred form the bearing 18 includes a hollow cylindrical member I having anti-friction bearings I38, which may be of the tapered roller bearing type, mounted in its opposite ends and disposed about the countershait in such manner as to leave an annular space defined by the exterior oi-the countershaft 15, the interior of the cylindrical member I 35, and the anti-friction bearings I36. The space so defined is provided at each end, that is, against each of the bearings I36, with suitable packing as indicated at I31 in Fig. 5. Intermediate the packing the countershaft has a radial bore I38 extending between the axial bore I30 and the remaining space about the countershaft 15 between the packings I31.

A fluid conduit I39 leads to the cylindrical member I35, see Fig. 3, and a passage I40 is formed in the cylindrical member to communicate between the conduit I39 and the-space inside the cylindrical member. It will be clear from the foregoing that the conduit I39 is in constant and free fluid communication with the fluid chambers adjacent the pistons I22 in the circular member I I8 through the passage I40, the radial passage I38, the axial bore I30, and the passages I3I and I32.

We turnnow to a description of the combined manual and automaticmeans for controlling the flow of fluid to the clutch and, brake operating mechanism. Fig. 4 is a schematic view showing the electrical circuits, and fluid conduits which cooperate to effect such control and the numeral I designates a fluid pump which may be provided with an individual electrical driving motor I46. The pump I45 and the motor I46 therefor appear in their assembled positions in Fig. 3.

Suitable fluid circuits are-associated with the pump I45 so that the pump and motor may operate continuously when the press is injuse, electrically controlled by-pass valves being provided for rendering the fluid pressure generated by the pumpoperative to engage the clutch mechanism or inoperative, in which case the spring means I25 engage the brake mechanism. When the press is in use but not executing a punching stroke, that is, when the driving motor for the press is rotating but the clutch mechanism is not engaged, the pump I 45 withdraws fluid from a reservoir I41 through a conduit I48 and returns thefluid so withdrawn directly tothe reservoir through the conduit I49, this being the path of least resistance to fluid flow.

A valve I50 is interposed in the conduit I49 anda spring I5I, which is conflned in a valve casing I52 with the valve I50, normally retains the valve in the position illustrated in Fig. 4

whereby fluid in the conduit I49. may flow freely through thepassage I53 in the valve I50. An armature or core I54 is connected to the valve I50 and an electro-magnet or solenoid I55 is arranged so that energization of the windings thereof attracts the core I54 and moves the valve into a position where it prevents direct flow of fluid in the conduit I49. When direct fiowof fluid back to the reservoir is prevented in this manner the fluid from the output side of the pump I45 flows in a branch conduit I56 which leads directly to the fluid chambers of the clutch and brake operating mechanism. That is to say, it connects with the conduit I39, previously described in connection with the construction of the countershaft bearing 18. The fluid chambers of the circular member II8 are represented by the schematic element I51 01' Fig. 4.

A pressure relief device is shown at I58 in Fig. 4 and this device may comprise a chamber having a floating piston I59 normally urged to a predetermined position by a spring I60. A conduit I 6I extends from an intermediate point along the conduit I56 to the chamber of the device I58. When the pressure in the working chambers of the clutch and brake mechanism, shown at I51 in Fig. 4, exceeds a predetermined amount the piston I59 of the device I58 is moved, against the resistance of the spring I60, to a position where it uncovers a port I63 and the port I63 has connection with the conduit I49-by means of a conduit I64.

It will be clear from the foregoing that when the electro-magnet I55 is energized passage of fluid through the conduit I49 is prevented and that consequently the continuing operation of the pump I 45 builds up pressurein the conduit I56 and the fluid chambers I51 01' the clutch operating mechanism until such pressure reaches a predetermined degree whereupon further increase in pressure is prevented by by-passage of fluid from the conduit I56 to the reservoir I41 through the conduit I6I, the device I58, the conduit. I 4, and the conduit I49.

When the electro-magnet I55 is de-energized the spring I5I moves the valve I50 to its illustrated position whereupon flow through the conduit I49 is re-establishcd. The output of the pump I45 is then returned directly to the reservoir I41 and, further, the action of the spring elements I25 of the clutch operating mechanism causes the drum II4 to be moved to the right as seen in Fig. 5 with the result that the fluid in the working chambers referred to as I51, in the schematic showing of Fig. 4, is expressed therefrom and returned to the reservoir through the conduits I56 (I38) and I49.

Suitable electrical circuits are provided for energizing the electro-magnet I55 andsuch circuits are arranged for operation by a combination of manual and automatic means. It is desired that operation of the press be manually initiated and that operation thereof continue until the manual operating pressure or force is released, with the qualification that after the manual operating force is released it is desired that the press, if a certain portion of a stroke has been executed, continue the'ensuing stroke and stop only when it reaches the end of a complete stroke, usually with the slide of the press in its uppermost position.

The energy for activating-the electro-magnet may be derived, as in the present instance, from the circuit which activates the motor I46 of the pump I45. Such circuit is shown at I10 and is controlled by a switch I1I. Actually, the circuit I10 will usually be combined with the circuit tor the main driving motor 3I of the machine in such manner that manipulation of a single switch closes and opens the circuits of both of the motors 3| and I46 and such arrangement is schemataically indicated in Fig. 4' where the main driving motor of the machine is designated 3|.

One of the terminals of the electro-magnet I55 is connected directly to one side of the main circuit I10 by a conductor I13 and the other side of the electro-magnet has a conductor I 14 which diverges into conductors I15 and I16 which extend in shunt relation to each other, then again converge as at I11 and connect with the other side of the main circuit I10. One of the shunt :circuits H6 is providedwith spaced manually operator, in having one hand oneach of the push buttons, cannot have either hand in a position where it is likely to be injured. The switches I18 are. of a type which is in circuit closing position only as'long as the push button is held depressed by the operator, removal of manual pressure from the push button resulting immediately in the opening. of the circuit controlled thereby. i

The shunt circuit I16 which extends about the push-button switches I18 is provided with a ro+ tary limit switch having normally spaced contacts I19 and a circuit-closing cam I801. The cam I 88 is rotated at the same speed as the crank -shaft of the press and, after a cycle of operation of the press has been begun by depression of the push buttons of the switches I18 by the operator, and after such operation has proceeded for a predetermined portion of its cycle, the cam has rotated to a point where the raised portion thereof closes the switch by moving one of the spaced contacts I19 against the other. After this point has been reached the operator may release the push buttons of the switches I18 since the electro-magnetic circuit will remain closed through the shunt circuit I15. When the endof an operating cycle is reached the cam, which travels at the same angular speed as the crank shaft, reaches a position where 'it releases the contact I19 which resiliently opens the circuit I16 and results, as will be apparent from the foregoing, in substantially simultaneously disconnecting the clutch mechanism and setting is also provided at the top of the chamber 38 to permit introduction of the gear I86'and a suitable cover I90 may be provided therefor.

The casing of the rotary limit switch which includes the contacts I19 and the cam I89 for controlling the contacts is shown in outline at I92 in Figs. 1 and 3. A sprocket I93 is provided on the shaft of the limit switch which controls the movements of the cam I88 which is disposed. within the casing I 92. A corresponding sprocket I94 is provided upon a reduced extension of the crank shaft which extends through the partition 28 into the chamber portion 29 and a chain I95 connects the sprockets. To facilitate assembly the partition 28 is provided with a removable plate I96 which is adapted to receive and provide bearing for the crank shaft 60 at its rear end. An anti-friction bearing I91 is preferably disposed between the journal portion of the crank shaft 60 at this point and the shaft supporting portion of the removable plate I96. By this construction it will be noted that the crank shaft has substantial bearing support difront wall of said casing portion for supporting and guiding the same, a crank shaft for reciprocatingsaid slide, said frame member having a die-receiving bed disposed below said slide and spaced from said casing portion and connecting means extending between said casing portion and saidbed, said frame member also having a forward extension at its front wall above said slide supporting and guiding means top and side walls of said extension forming forward extensions of. the top and side walls of said casingportion and the bottom wall of said extension being formed to receive and provide bearings for said crank shaft, said last mentioned top and bottom walls cooperating to provide spaced stress-receiving structural ele-' ments.,

2. In a punch press. ,a 'framemember comprising a substantially rectangular casing portion having front, rear and side walls, a reciprocable slide and means at the outside of the front wall of said casing portion for supporting and guiding the same, said frame member having a diereceiving bed disposed below said slide and a forward extension at its front wall and above said slide, a bearing element provided at the forward portion of said extension and an aligned coaxial bearing element in the front wallof said casing portion, a crank shaft.

journaled in said bearings and having a crank therebetween for connection with said slide to actuate the latter, transmission means in said casing portion for actuating said crank shaft, said crank shaft extending through said front wall to the interior of said casing portion for engagement with said transmission means.

3. In a punch press, a framemember comprising a hollow substantially rectangular-casing portion, a reciprocable slide and means at the outside of the front wall of said casing portion for supporting and guiding the same, said frame member having a die-receiving bed disposed below said slide and a forward extension at its front wall and above said slide, a bearing element provided at the forward portion of said extension and an aligned coaxial bearing element spaced rearwardly of the first bearing element, a crank shaft joumaled in said bearings and having a crank therebetween for connection with said slide to reciprocate the latter, transmission means in said casing portion for actuating said crank shaft, said crank shaft having a rear portion extending through said front wall to the interior of said casing portion for engagement with said transmission means.

4. In a punch press, a frame member compris ing a substantially rectangular casing portion having front, side and top walls, a reciprocable slide and means at the outside of the front wall of said casing portion for supporting and guiding the same, said frame member having a diereceiving bed disposed below said slide and a forward extension at its front walland above said slide, said forward extension comprising side, top and bottom walls with said side and top walls formin g forwarcl extensions of the side and top walls of said' casing portion, a bearing element associated with the bottom wall of said forward extension adjac'entthe forward portion thereof and a second bearing element spaced rearwardly of said first bearing element and in axial alignment therewith, a crank shaft journaled in said bearing elements and having a crank therebetween, and transmission means housed in said casing portion for actuating said crank shaft, said crank shaft extending through said front wall into said casing portion for engagement with said transmission means.

5. In a punch press, a frame member comprising a substantially rectangular casing portion having front, side and top walls, a reciprocable slide and means at the outside of the front wall of said casing portion for supporting and guiding the same, a crank shaft for reciprocating said slide, said frame member having a die-receiving bed below said slide and spaced from said casing portion and connecting means extending between said casing portion and said bed, said connecting means including a pair of spaced vertically extending column portions of hollow substantially rectangular cross section, each of said column portions being disposed with its outer side wall forming substantially a downward continuation of a side wall of said casing portion, said frame member also having a forward extension at its front wall above said slide supporting and guiding means and comprising side, top and bottom walls, the top and side walls of said extension forming forward continuations of the top and side walls of said casing portion and the bottom wall of said extension being formed to receive and provide bearings for said crank shaft.

6. In a punch press, a frame member comprising a substantially rectangular casing portion having front, side and top walls, a reciprocable slide and means at the outside of the front wall of said casing portion for supporting and guiding the same, a crank shaft for reciprocating said slide, said frame member having a die-receiving bed disposed below said slide, said frame member also having a forward extension at its front wall above said slide supporting and guiding means and comprising a hollow substantially rectangular element having spaced top and bottom walls and spaced side walls, said bottom wall being formed to receive and support said crank shaft.

7. In a punch press, a frame member comprising a substantially rectangular casing portion having front, side and top walls, a reciprocable slide and means at the outside of the front wall of said casing portion for supporting and guiding the same, and a crank shaft for reciprocating said slide, said frame member having a die-receiving bed disposed below said slide, said frame member also having a forward extension at its front wall above said slide supporting and guiding means and comprising a hollow substantially rectangular element having spaced top and bottom walls and spaced side walls, said bottom wall being formed to receive and support said crankshaft and the top and side walls of said forward extension being arranged to form substantially forward continuations of the top and side walls respectively of said casing portion.

8. In a punch press, a frame member comprising a main frame portion, a reciprocable slide and means at the front of said main frame portion for supporting and guiding the slide, and a crank shaft having a crank for reciprocating said slide, said frame member having a die-receiving bed disposed below said slide, said main frame portion having a forward extension at its front side above said slide supporting and guiding means and comprising a hollow substantially rectangular element having spaced top and bottom walls and spaced side walls, a recess in said bottom wall for receiving and housing the crank portion of said crank shaft, a bearing disposed at the forward portion of said bottom wall and adjacent said recess and a second bearing coaxial therewith and disposed at the rear portion of said bottom wall adjacent said recess and adjacent the main frame portion, said crank shaft being adapted to be journaled in said bearings.

9. In a punch press, a frame member comprising a casing portion, a slide and means at the front of said casing portion for supporting and guiding said slide, said frame member having a die-receiving bed disposed below said slide and a forward projection at the front of the casing portion of said frame member and above said slide, a crank shaft journaled in said forward projection with a portion thereof extending rearwardly into the interior of said casing portion, a countershaft journaled within said casing portion with its axis extending parallel to the axis of the crank shaft and drive means engaging between said crank shaft and said countershaft, means for imparting rotary motion to said countershaft, and clutch means associated with said countershaft between said last mentioned means and said crank shaft driving means for eil'ecting connection and disconnection between said means for selectively imparting rotary mo tion to said crank shaft.

10. In a punch press, a frame member comprising a casing portion, a slide and means at the front of said casing portion for supporting and guiding said slide, said frame member having a die-receiving bed disposed below said slide and a forward projection at the front of the casing portion of said frame member and above transmission means connecting said motor and said flywheel, and clutch means actuable to engage and disengage said flywheel and said countershaft for joint rotation and relative rotation respectively.

11. In a punch press, a frame member comprising a casing portion, a slide and means at the front of said casing portion for supporting and guiding-said slide, said frame member having a die-receiving bed disposed below said slide and a forward projection at the front of the casing portion of said frame member and above said slide, a lateral partition forming forward and rear compartments in the interior of said casing portion, a crank shaft journaled in said forward projection with a portion thereof extending rearwardly into the forward compartment of said casingportion, a countershaft journaled in said casing portion and having a portion thereof disposed in said forward compartment and another portion thereof disposed in said rear compartment, a driving connection between said countershaft and said crank shaft in said forward compartment, and means engageable with said countershaft in said rear compartment for effecting rotation thereof.

12. Ina punch press, aframe member comprising a casin Prtion, a slide and means at the front of said casing portion for supporting and guiding said slide, said frame member having a die-receiving bed disposed below said slide and a forward projection at the front of the casing portion of said frame member and above said slide, a lateral partition forming forward and rear compartments in the interior of said casing portion, a crank shaft journaled in said forward projection with a portion thereof extending rearwardly into the forward compartment of the casing portion, a countershaft extending parallel to said crank shaft and journaled in said casing portion with a portion thereof disposed in said forward compartment and a portion thereof disposed in said rear compartment, a permanent drivingconnection between said countershaft and said crank shaft in said forward compartment, drive means in said rear compartment adapted to rotate substantially continuously, and clutch means between said drive means and said countershaft for selectively establishing driving engagement therebetween.

13. In a punch press. a frame member comprising a casing portion, a slide and means at the front of said casing portion for supporting and guiding said slide, said frame member having a die-receiving bed disposed below said slide and a forward projection at the front of the casing portion of said frame member and above said slide, a crank shaft journaled in said forward projection and having a portion thereof extending into the interior of said casing 'portion, a countershaft extending parallel to said crank shaft and journaled in said casing portion, a permanent driving connection between said countershaft and said crank shaft in the interior of said casing portion, drive means in said casing portion adapted to rotate substantially continuously, and clutch means between said drive means and said countershaft for selectively establishing driving engagement therebetween.

14. In a punch press, a frame member comprising a casing portion, a slide and means at the front of said casing portion for supporting and guiding said slide, said frame member having a die-receiving bed disposed below said slide and a forward projection at the front of the casing portion of said frame member and above said slide, a lateral partition forming forward and rear compartments in the interior of said casing portion, a crank shaft jormaled in said forward projection with a portion thereof extending rearwardly into the forward compartment of the casing portion, a countershaft extending parallel to said crank shaft and journaled in said casing portion with a portion thereof disposed in said forward compartment and a portion thereof disposed in said rear compartment, a permanent driving connection between said countershaft and said crank shaft in said forward compartment-a flywheel mounted upon said countershaft in said rear compartment and normally free to rotate with respect thereto, drive means engageable with said flywheel for imparting substantially continuous rotary movement thereto, and releasable means for locking said flywheel to said countershaft for imparting rotary movement to the latter.

15. In a punch press, a frame member comprising a casing portion, a slide and means at the front of said casing portion for supporting and guiding said slide, said frame member having a die-receiving bed disposed below said slide and a forward projection at the front of the casing portion of said frame member and above said slide, a crankshaft journaled in said forward projection with a portion thereof extending rearwardly into the interior of the casing portion, a countershaft journaled in said casing portion and extending parallel to said crank shaft, a permanent driving connection between said countershaft and said crank shaft in the interior of said casing, a flywheel mounted upon said countershaft and normally free to rotate with respect thereto, drive means engageable with said flywheel for imparting substantially continuous rotary movement thereto, and releasable means for locking said flywheel to said countershaft for imparting rotary movement to the latter.

16. In a punch press, a frame member comprising a hollow casing portion, a reciprocable slide and means at the outside of the front wall of said casing portion for supporting and guiding the same, said frame memberhaving a diereceiving bed disposed below said slide and a forward extension at its front wall and above said slide, a bearing element provided at the forward portion of-said extension and an aligned coaxial bearing element spaced rearwardly of the first bearing element, a crank shaft journaled in said bearings and having a crank. therebetween for connection with said slide to reciprocate the latter, said first bearing element being removably associated with said extension to facilitate assembly and disassembly of said crank shaft, transmission means in said casing portion for actuating said crank shaft, said crank shaft having a rear portion extending through said front wall to the interior of said casing portion for engagement with said transmission means.

17. In a punch press, a. frame member-comprising a hollow casing portion, a slide and means at the front of said casing portion for supporting and'guiding said slide, said'frame member having a die-receiving bed disposed below said slide and a forward projection at the front of the casing portion of said frame member and above said slide, a lateral partition forming forward and rear compartments in the interior of said casing portion, a crank shaft journaled in said forward projection with a portion thereof extending rearwardly into the forward compartment of said casing portion, bearing means associated with said partition for receiving and supporting the rear terminal portion of said crank shaft, a countershaft journaled in said casing portion and-having a portion thereof disposed in said forward compartment and another portion thereof disposed in said rear compartment, 9. driving connection between said countershaft and said crank shaft in said forward compartment, and means engageable with said countershaft in said rear compartment for effecting rotation thereof. V

18. In a punch press, a frame member comprising a hollow casing portion, a reciprocable slide and means at the outside of the front wall of said casing portion for supporting and guiding the same, said frame member having a die-re ceiving bed disposed below. said slide and a forward extension ,at its front wall and above said slide, a bearing'element provided at the forward portion of said extension and an aligned coaxial bearing element spaced rearwardly of the first bearing element, a crank shaft journaled in said bearings and having a crank therebetween for connection with the slide to reciprocate the latter, transmission means in said casing portion for actuating said crank shaft, said crank shaft havforming forward and rear compartments in the interior of said casing portion, a reciprocable slide and means at the outside of thefront wall of the casing portion for supporting and guiding the same, said frame member having a die-receiving bed disposed below said slide and a forward extension at its front wall and above said slide, a bearing element provided at the forward portion of said extension and an aligned coaxial bearing element spaced rearwardly of the first bearing element, a crank shaft journaled in said bearings and having a crank therebetween for connection with the slide to reciprocate the latter, said crank shaft having a portion thereof extending rearwardly into the forward compartment of the casing portion, bearing means associated with said partition for receiving and supporting the rear terminal portion of said crank shaft, a countershaft journaled in said casing portion and having a portion thereof disposed in saidforward compartment and another portion thereof disposed in said rear compartment, a driving connection between said countershaft and said crank shaft in said forward compartment, and means engageable with said countershaft in said rear compartment for effecting rotation thereof.

20. In a punch press, a frame member comprising a hollow casing portion, a slide and means at the front of said casing portion for supporting and guiding said slide, said frame member having a die-receiving bed disposed below said slide and a forward projection at the front of the casing portion of said frame member and above said slide, a lateral partition forming forward and rear compartments in the interior of said casing portion, a crank shaft journaled in said forward projection with a portion thereof extending rearwardly into the forward compartment of the casing portion, a countershaft extending parallel to said crankshaft and having a portion thereof disposed in said forward compartment andanother portion thereof disposed in said rear compartment, aligned coaxial bearings formed in the front and rear walls of said casing portion and in said partition, said countershaft being journaled at its front and rear ends and intermediate thereof in the bearings; in the front and rear of the casing and in the partition respectively, a driving connection between said countershaft and said crank shaft in said forward compartment, and means in said rear compartment for engagement with said countershaft to rotate the same.

21. In a punch press, a frame member comprising a hollow casing portion, a reciprocable slide and means at the outside of the front wall aarasso of said casing portion for supporting. and guiding the same, said frame member having a diereceiving bed disposed below said slide and a forward extension at its front wall and above said slide, a lateral partition forming forward and rear compartments in the interior of said casing portion, a crank shaft journaled in said forward projection with a portion thereof extending rearwardly into the forward compartment of said casing portion, bearing means associated with said partition for receiving and supporting the rear terminal portion of said crank shaft, a

countershaft extending parallel to said crank shaft and having a portion thereof disposed in said forward compartment and another portion thereof disposed in said rear compartment, aligned coaxial bearings formed in the front and rear walls of said casing portion and in said partition, said countershaft being journaled at its front and rear ends and intermediate thereof in the bearings in the front and rear of the casing and in the partition respectively, a driving connection between said countershaft and said crank shaft in said forward compartment, and means in'said rear compartment for engagement with said countershaft to rotate the same.

22. In a punch press, a frame member comprising a hollow casing portion, a lateral partition forming forward and rear compartments in the interior of said casing portion, a reciprocable slide and means at the outside of the front wall of said casing portion for supporting and guiding the same, said frame member having a die-receiving bed disposed below said slide and a forward extension at its front wall and above said slide, a bearing'element provided at the forward portion of said extension and an aligned coaxial bearing element spaced rearwardly of the first bearing element, a crank shaft journaled in said bearings and having a crank therebetween for connection with the slide to reciprocate the lat- .crank shaft and having a portion thereof disposed in said forward compartment and another portion thereof disposed in said rear compartment, alingned coaxial bearings formed in the front and rear walls of said casing portion and in said partition, said countershaft being journaled at its front and rear ends and intermediate thereof! in the bearings in the front and rear of the casing and in the partition respectively, a driving connection between said countershaft 1 and said chank shaft in said forward compartment, and means in said rear compartment for engagement with said countershaft to rotate the same.

' GEORGE E. MUNSCHAUER.

FREDERICK E. MUNSCHAUER.

Images