CA1083949A - Cylinder operated swinging ram cutoff press - Google Patents
Cylinder operated swinging ram cutoff pressInfo
- Publication number
- CA1083949A CA1083949A CA302,296A CA302296A CA1083949A CA 1083949 A CA1083949 A CA 1083949A CA 302296 A CA302296 A CA 302296A CA 1083949 A CA1083949 A CA 1083949A
- Authority
- CA
- Canada
- Prior art keywords
- ram
- swinging
- connecting rod
- cylinder
- arcuate path
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23D—PLANING; SLOTTING; SHEARING; BROACHING; SAWING; FILING; SCRAPING; LIKE OPERATIONS FOR WORKING METAL BY REMOVING MATERIAL, NOT OTHERWISE PROVIDED FOR
- B23D25/00—Machines or arrangements for shearing stock while the latter is travelling otherwise than in the direction of the cut
- B23D25/02—Flying shearing machines
- B23D25/04—Flying shearing machines in which a cutting unit moves bodily with the work while cutting
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
- B30B1/10—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by toggle mechanism
- B30B1/16—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by toggle mechanism operated by fluid-pressure means
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Press Drives And Press Lines (AREA)
- Control Of Cutting Processes (AREA)
- Shearing Machines (AREA)
Abstract
ABSTRACT OF THE DISCLOSURE
A swinging ram type cutoff press for severing lengths of elongated stock such as tubing is disclosed of the type in which a ram is supported for swinging movement to operate a cutoff die set. The disclosed cutoff press in-cludes a power cylinder combined with a toggle link arrange-ment to produce the swinging movement of the ram. The relative geometry of the ram link support and the toggle mechanism coupled with the arrangement of the cylinder is such that a complete ram motion cycle is carried out during a single forward or return stroke of the cylinder. The force exerted by the cylinder and toggle mechanism is not resisted either by return springs or the weight of the ram, thereby further maximizing the usable power of the power cylinder. Accordingly, one may reduce the cylinder size requirements for a given application.
In addition the mechanical advantage afforded by the toggle mechanism provides for a maximum force at the ram full down position to maximize the force available for the blade stroke.
A swinging ram type cutoff press for severing lengths of elongated stock such as tubing is disclosed of the type in which a ram is supported for swinging movement to operate a cutoff die set. The disclosed cutoff press in-cludes a power cylinder combined with a toggle link arrange-ment to produce the swinging movement of the ram. The relative geometry of the ram link support and the toggle mechanism coupled with the arrangement of the cylinder is such that a complete ram motion cycle is carried out during a single forward or return stroke of the cylinder. The force exerted by the cylinder and toggle mechanism is not resisted either by return springs or the weight of the ram, thereby further maximizing the usable power of the power cylinder. Accordingly, one may reduce the cylinder size requirements for a given application.
In addition the mechanical advantage afforded by the toggle mechanism provides for a maximum force at the ram full down position to maximize the force available for the blade stroke.
Description
~0~35~9 `
BACI~GROUND OF T~ INVENTION
1 Field of the Invention This invention concerns presses and more particularly presses having a ram which is mounted for swinging movement, such as is used in cutoff apparatus for severing lengths of ~;
elongated stock emanating from a tubing mill or other such source. '
BACI~GROUND OF T~ INVENTION
1 Field of the Invention This invention concerns presses and more particularly presses having a ram which is mounted for swinging movement, such as is used in cutoff apparatus for severing lengths of ~;
elongated stock emanating from a tubing mill or other such source. '
2. Description of the Prior Art ~;
In the past, presses have incorporated rams operated ~ ~
by power cylinders, such as large diameter air cylinders. In ' ' these arrangements typically the ram would be mounted to the output member of the power cylinder, and the air cylinder would be stroked against the bias of return springs. The application of such cylinder-operated presses to tubing or other elongated stock cutoff apparatus has been limited for several reasons to relatively light duty situations. Firstly, the ram mechanism, if mounted directly to the output piston of the power cylinder ~ ~ `
has been limited in size by the size of the power cylinders, since the ram was typically guided in its stroke by the cylinder structure, or else additional ways or slides were by necessity required. Since the cost of power cylinders increases dispro-portionately with increasing cylinder bore size, it has been found to be economically unfeasible to operate rams over a cer-tain size by means of air cylinders. In addition, the typical arrangement of stroking the press against the bias of return springs has the disadvantage that the available force of which ;~
the ram would be capable of exerting would be proportionately ~
reduced as the return springs were compressed. This disadvantage ' is aggravated in the usual'situation in which maximum ~orce is required at the extreme position of the ram, and necessitates substantially increased cylinder size and/or operating pressure -- 1 -- ''o ~'
In the past, presses have incorporated rams operated ~ ~
by power cylinders, such as large diameter air cylinders. In ' ' these arrangements typically the ram would be mounted to the output member of the power cylinder, and the air cylinder would be stroked against the bias of return springs. The application of such cylinder-operated presses to tubing or other elongated stock cutoff apparatus has been limited for several reasons to relatively light duty situations. Firstly, the ram mechanism, if mounted directly to the output piston of the power cylinder ~ ~ `
has been limited in size by the size of the power cylinders, since the ram was typically guided in its stroke by the cylinder structure, or else additional ways or slides were by necessity required. Since the cost of power cylinders increases dispro-portionately with increasing cylinder bore size, it has been found to be economically unfeasible to operate rams over a cer-tain size by means of air cylinders. In addition, the typical arrangement of stroking the press against the bias of return springs has the disadvantage that the available force of which ;~
the ram would be capable of exerting would be proportionately ~
reduced as the return springs were compressed. This disadvantage ' is aggravated in the usual'situation in which maximum ~orce is required at the extreme position of the ram, and necessitates substantially increased cylinder size and/or operating pressure -- 1 -- ''o ~'
3~9L9 requirements to obtain force levels adequate to operate the cutoff die s0t.
In other contexts, power cylinders have been coupled with force-multiplying mechanisms, such as toggle link mechanism and the ram stroked vertically upward to -obviate the need for return springs or double acting cylinders. However the weight of the ram in this design `
would also act to reduce the available force exerted by the ram as the ram was stroked by the power cylinder. In addi-tion the cylinder controls tended to be rather complex and subject to the burdensome maintenance requirements, since the cylinder would be depressurized and the return springs or ram weight utilized to return the ram to its initial position.
In some applications, the timing of the press operation is critical, as in those cutoff press apparatuses involving cutting on the fly or cutting of the stock as it rapidly emanates from a stock production mill, such as a tubing or extrusion mill, in which the entire cycle must of ~ ~ -necessity be carried out with relatively precise timing. These design problems have limited the application of such c~linder-operated presses to the aorementioned stock cutoEE applications.
In such apparatus, it has been the practice to provide a swinging ram type press in which a ram member has been sup-ported on a pair of pivotal links which constrain the ram move-mentto that of a swinging motion about the pivotal support of the links, its pivotal movement producing both translation in the direction of the movement of the stock, as well as a ~o~3a349 reciprocation thereof of the ram transverse to the direction of movement of the stock. A typical example of such a press is disclosed in U. S. Patent No. 3,288,011. In this design, the ram is driven so as to be swung or oscillated about these pivotally supported links by means of a crank mechanism driven ;
by an electric motor and clutch, the crank mechanism being con-nected to the connecting rod to the ram to induce the swinging movement. The weight of the ram acts in concurrence with the downward and forward movement of the ram induced during the ram stroking in a forward direction, with the geometry of the links, etc~ producing the full stroking of the ram without the need for reversal of the electric motor or precise control over the crank mechanism or electric motor and clutch.
The swinging movement of the ram in turn produces operation of the cutoff die set which is adapted to be recipro-cated by the ram as it travels with the stock on an upper rail set carried by the ram and a lower rail set fixed to the machine base. The cutoff die set, as described in the aforementioned U. S. patent, includes means for initially clamping the die set to the stock to be severed, causing the die set to traverse the rail set together with the stock. Subsequently, downward move-ment of a cutoff blade, included in the die set is induced by the downward movement of the ram moving through its arcuate path as it swings about the pivotal supports provided by the pivotal links. Continued rotation of the eccentric crank drives the ram to its full down position with further rotation producing a reversal of movement of the swinging ram, to first withdraw the cutoff blade, then releasing the stock from the die set to allow it to be returned to its initial pOsitiQn by means of a return cylinder or other mechanism prior to initiation of a new cycle.
3~4~
:
.:
A variation of the basic mechanism provides for an adjustable `
length connecting rod which serves to provide a capability for shifting the segment o the arcuate path through which the ram is constrained to move by virtue of its support on the pivotally supported links, which shifting provides for adjusting the shut height or the position of the ram in its full down position, as well as the length of its stroke in such a way as to adapt the cutoff apparatus to die sets of varying configurations, to accommo-date its application to varying tube sizes etc.
While these machines have performed very satisfactorily and are adapted to reliably stroke the ram through its required swinging movement, the electric motor, clutch, and eccentric crank components comprise a considerable element of manufacturing cost in the apparatus.
On the other hand, while the aforementioned cylinder-operated presses suffer from the disadvantages described, they do exibit the inherent advantage of a generally lower manufac-turing costs, due to the use of simple power cylinders as a source of operating means for the ram where cylinders of a reasonable size are able to be utilized.
Accordinglyr it is an object of the present invention to adapt a power cylinder to a swinging ram cutoff press of the sort described.
It is a further object of the present invention to adapt such power cylinder to the cutoff mechanism described in such a way as to not necessitate the use of complex controls or adversely affecting the reliability of the machine.
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It is yet another object of the present invention to ;
provide such an adaptation which does not involve the use of return springs tending to reduce the available force generated by the cylinder during stroking of the ram.
It is a further object of the present invention to incorporate a power cylinder operating device into a swinging -ram type cutoff apparatus in such a way as to enhance the available force at that portion of the ram's stroke requiring maximum force to be exerted by the ram.
It is yet another object of the present invention to provide such an adaptation without entailing the incorporation of expensive and precision structural or control components.
SUMMARY OF THE INVENTION
These and other objects which will become apparent upon reading of the following Specification and Claims are accom-plished by incorporating a power cylinder into a swinging ram press by providing a toggle link pivotally connected at one end to a connecting rod link, in turn pivotally connected to the ram, with the power cylinder pinned to the connected ends of the toggle link and connecting rod so as to act as a toggle mechanism upon stroking of the power cylinder. The relative geometry of the ram supporting links, the toggle link, the connecting rod link and the power cylinder is such that the toggle mechanism is at the extreme, advanced position of the ram, and the power cylinder executes its full oscillation of the ram upon a stroke in either direction to obviate the need for a reversal of the cylinder-operating member during the stroking of the ram. The connecting rod link is adjustable in length to provide a capability for adapting the cutoff apparatus to varying shut height and stroke requirements of differing die set sizes and configurations.
1~83~
BRIEF DESCRIPTION OF THE D~WINGS
FIGURE 1 is a ~ront elevational view of a swinging -ram cutoff press, according to the present inv~ntion.
FIGURE 2 is a side elevational view of the swinging ram cutoff press, shown in FIGURE 1.
FIGURE 3 is a view of the Section 3-3, taken in FIGURE 1.
FIGURE 4 is a view of the Section 4-4, taken in FIGURE 1.
FIGURE 5 is a diagrammatic view of the swinging ram cutoff press, shown in FIGURE 1, in an advanced position of the swinging ram.
FIGURE 6 is a diagrammatic representation of the swinging ram, shown in FIGURES 1 through 5, w:ith the swinging ram elevated by retraction of the power cylinder.
FIGURE 7 is a diagrammatic representation of the swinging ram cutof press, shown in YIGURES 1 through 6, with an adjustment of the length of the connecting rod link to pro-duce a longer stroke, greater shut height stroking of the swinging ram.
DETAI~ED DESCRIPTION
In the following detailed description certain specific terminology will be utilized for the sake of clarity and a parti-cular embodiment described, but it is to be understood that the same is not intended to be limiting and, indeed, should not be so construed, inasmuch as the invention is capable of considerable variation within the scope of the appended claims.
Reerring to the drawings, and particula~l~ FIGURES 1 through 4, the swinging ram cutoff apparatus 10, according to the present invention, is depicted. The cutoff apparatus 10 ~ ..
?3g4~ :
includes base support means 12 including a lower housing 14 and an upper housing 16, each comprised of a steel weldment. Sup-ported on the upper housing 16 for swinging movement is a die set operating ram 18, the means providing the pivotal support :
being provided by a pair of pivotal links 20 and 22 pinned at one end to the upper housing 16 and at the other to the ram 18.
This mode of support serves to constrain the ram to swinging movement through an arcuate path.
This swinging movement is adapted to operate a die ~ :
set 24 which is retained between an upper rail set 26 affixed ~.
to the lower surface of the ram 18 and a lower rail set 28 affixed to the lower housing 14 by means of an upper die set carriage 30 and a lower die set carriage 32, as shown in FIGURES
1 and 2. The descending movement of the ram 18 created by its swinging motion reduces the clearance between the upper rail set 26 and lower rail set 28 which movement induces operation of the ~"
cutoff die set 24. This operation includes a movement of a pair of clamping jaws 34 and 36 upon initial downward movement of the :
ram 18 to clamp the die set 24 to the work W passing through the clearance space between the upper rail set 26 and the lower rail set 28, clutching the die set 24 to the workpiece W so as to cause it to move together therewith along the upper rail set 26 and the lower rail set 2~.
Further downward movement of the ram 18 occurring as i~
its swinging motion progresses causes operation of the cutoff blade 38 causing the severing of the work W within the die set 24. Upon reversal of movement of the ram 18, the cutoff blade :~:
38 is initially withdrawn, then the clamping jaws 34 and 36 are operated to release the work W, all of this taking place before the die set 24 has reached its limit of travel on the upper rail set 26 and lower rail set 28. Upon release of the clamping jaws :
~399LS~
34 and 36 a return cylinder, not shown, returns the die set 24 to its initial position, as shown in FIGURE 1.
Since this aspect of the cutoff press per se does not comprise the present invention and inasmuch as the details of the same are now very well known to those skilled in the art, the specific design of the die set 24 and other structural de-tails relating thereto are not here disclosed.
A pair of baffles 40 and 42 are typically provided to collect the cutoff slugs caused by shearing of the workpiece W, which may be collected into a bin, not shown, disposed within a cutout opening 44 in the front plate of the lower housing 14.
The links 20 and 22, as noted above, are pivotally supported on the upper housing 16 and also pivotally connected to the ram 18. FIGURE 4 depicts in some detail the nature of these pivotal connections, with the connection of link 22 de-picted as typical. Each of the links 20 and 22 are bifurcated into arms 48 and 50 to form a clevis at its lower end, receiving a pivot pin 46 passing through each arm 48 and 50 of the link 22 and also through a bore 52 formed in the ram 18. A pair of needle bearings 54 and 56 are provided to provide a rotatable support for the pivot pin 46 within the bore 52, with a spacer sleeve 58 provided to maintain the separation of needle bearings 54 and 56. A pair of thrust washers 60 and 62 are also included.
The link 22 is pivotally supported at its other end within the upper housing 16 between a pair of end plates 62 and 64 forming part of the weldment of which the upper housing 16 is constituted, by means of a pivot pin 65 having end portions 66 and 68 disposed and retained between the end plates 62 and 64 with a central portion 70 passing through a bore 72 formed in the link end portion 74 joining the bifurcations 48 and 50.
.. , . . .. .. : ~ :: . . . .
~ ~339~9 ;~
A pair of needle bearings 76 and 78 are provided, maintained in axial position by means of a spacer sleeve 80.
Thrust bearings 82 and 84 are also provided cooperating respec~
tively with a boss portion 85 welded to end plate 62 and a shoulder formed by the enlarged diameter end portion 68 of the connecting pivot pin 70. A boss portion 87 is also provided receiving the end portion 68, as shown.
Lubrication fittings 86 and ~8 may be provided in order to supply lube passages 90 and 92 formed internally in the pin 46 and 70, respectively. Suitable retainers 94, 96, 98 and 100 are provided to provide endwise or axial retention of the pivot pins 46 and 70, respectively, with the lube fittings 86 and 88 and cap screws 102 and 104 being provided to secure the respective retainers 94, 96, 98 and 100 to the link 22 and the upper housing 16, respectively.
The ram operating mechanism which is adapted to oscil-late the ram through its swinging movement in the arcuate path through which it is constrained to move by the links 20 and 22, includes a toggle link 106, a connecting rod link 108 and an operating cylinder assembly 110. The toggle link 106 is mounted at one end to the upper housing 16 in a similar Eashion as the links 20 and 22 by the journaling of a end section 109 in the side plates 62 and 64 included the upper housing 16 weldment.
The toggle link 106 has bifurcated portions 111 and 112 which act as a clevis for a master pivot pin 114 retained in the outer end of bifurcations 111 and 112 by means of retainer plates 115 and 116 retained by cap screws 118 at one end and a lube fitting 120 at the other end in similar fashion to the other pivotal connections, described above.
Master pivot pin 114 has journaled thereon one end of the connecting rod 108. The connecting rod 108 is formed as two . . : ; .. , ,-- .. :, :
9~9 ~
end portions 124 and 126 joined by an oppositely threaded adjusting rod 128 threadably received within bores 130 and 132 formed in the respective connecting rod ends 124 and 126. The threaded adjusting rod 128 having a central wrenching portion .
130 so as to enable the threaded rod to be rotated to vary the effective length of the connecting rod 108. The upper end 124, as noted, is journalled on the master pivot pin 114, as shown, with bearing 134 provided and thrust spacers 136 and 138, in-termediate the clevis 141 end portions 140 and 142 of the oper- :
ating cylinder assembly 110, to be described further herein.
The clevis portions 140 and 142 are similarly journalled by means of rotary bearings 144 and 146 receiving the master pivot pin 114 with thrust spacers 148 and 150 provided intermediate the bifurcations 110 and 112 of the toggle link 106 and the clevis portions 140 and 142 of the operating cylinder assembly 110. , .
The lower connecting rod end 126 is journalled within an opening 150 provided in the ram 18 in the region whereat a pivot pin 152 associated with the front pivotal link 20 is con-nected to the ram 18 so that the connecting rod 126 is also journalled on the pivot pin 152 as provides the pivotal support for the link 20. A needle bearing 154 is provided while separate bearings 156 and 158 are provided in appropriate openings in the ' bores in the ram 18 to provide a rotatable support of the ram 18 on the pivot pin 152. Retainer thrust bearings 160 and 162 are also provided to maintain the proper spacing between the ram 18 and bifurcated portions 164 and 166 of the pivot link 20. Cap screws 168 cooperating with a retainer plate 170 and a lube fitting 172 cooperating with a retainer plate 174 serves to retain the pivot pin 152 in the assemblage.
1~3g~9 ~ .:
The power cylinder assembly 110 includes a power cylinder body 176 pivotally mounted at its rear portion by means of a pivot pin 178 passing through an opening 180 formed in a mounting plate 182 affixed to the rear of the power cylin-der body 176. The pivot pin 178 is retained in a pair of clevis ~
plates 184 and 186 welded to a mounting bracket 188 secured to ~ -the upper housing 16, as shown in FIGURES 1 and 2. ;
The power cylinder assembly 110 also includes an -operating rod 192 connected to a clevis end portions 140, 142.
In operation, the cylinder assembly 110 is in an initial position, either with the operating rod 192 in the fully retracted position, as shown in FIGURE 1, or fully extended position, as shown in FIGURE 6 in schematic form. ~n either the fully retracted or extended position, the ram 18 is in the full up position, with the toggle link 106 and connecting rod 108 askew, as shown in FIGURES 1 or 6. By initiation of a cutoff cycle, the cylinder assembly 110 is pressurized by means of solenoid control val~res, not shown, to cause the operating rod 192 to be retracted~ or extended. The toggle link 106 and connecting rod link 108 are drawn into the aligned position, as shown in FIGURE 1, with an incraasing mechanical advantage characteristic of toggle mechanisms being imposed on the ram 18 through the connecting rod 108. A maximum mechanical advan-tage is achieved in the ull down position o the ram 18 as de-picted in FIGURE 1, since the operating rod extends trans-versely to the aligned toggle link 106 and connecting rod link 108 and generally transversely to the pivotal links 20 and 22.
Continued movement of the operating rod 192 again produces ele-vation of the ram 18 so that in the fully retracted or extended position, the ram 18 has again returned to the initial or up position. It must be seen that the power cylinder 110 need not be reversed during the cycling of the cutoff press, but in a ll)B3949 single stroke produces both the down and up movement of the ram.
Furthermore, the mechanical advantage is at a maximum when the force requirements are at a maximum, i.e., at the ram full down position. It should also be noted that the ram 18 weight does not work in opposition to the force applied by the power cylin-der assembly 110 to further maximize the force able to be exerted by the power cylinder assembly 110 to the ram 18.
The adjustment of the connecting rod 108 produces a very advantageous flexibility in the application of any given press, since the shut height and stroke may be varied by means of the adjustability in length of the connecting rod 108. This can be seen by ~he schematic representation of FIGURE 7 showing the adjustment rod 128 threaded fully into the connecting rod ends 124, 126 to reduce the connecting rod 108 length to a minimum.
This produces an increased stroke, but instead o~ reducing the shut height, the shut height is increased, as shown in FIGURES 5 and 7.
The power cylinder assembly may be provided by an air cylinder, since the output requirements are reduced to a minimum by the disclosed arrangement, although hydraulic cylinders alter-natively could be used if desired. In addition the power cylin-der assembly 110 would normally include means for controlling decelerati~on to control bounce at the end of the retraction or extension of the operating rod 192, but, since such devices are well known in the art, and many suitable designs are available, this device is not here described.
--1~--
In other contexts, power cylinders have been coupled with force-multiplying mechanisms, such as toggle link mechanism and the ram stroked vertically upward to -obviate the need for return springs or double acting cylinders. However the weight of the ram in this design `
would also act to reduce the available force exerted by the ram as the ram was stroked by the power cylinder. In addi-tion the cylinder controls tended to be rather complex and subject to the burdensome maintenance requirements, since the cylinder would be depressurized and the return springs or ram weight utilized to return the ram to its initial position.
In some applications, the timing of the press operation is critical, as in those cutoff press apparatuses involving cutting on the fly or cutting of the stock as it rapidly emanates from a stock production mill, such as a tubing or extrusion mill, in which the entire cycle must of ~ ~ -necessity be carried out with relatively precise timing. These design problems have limited the application of such c~linder-operated presses to the aorementioned stock cutoEE applications.
In such apparatus, it has been the practice to provide a swinging ram type press in which a ram member has been sup-ported on a pair of pivotal links which constrain the ram move-mentto that of a swinging motion about the pivotal support of the links, its pivotal movement producing both translation in the direction of the movement of the stock, as well as a ~o~3a349 reciprocation thereof of the ram transverse to the direction of movement of the stock. A typical example of such a press is disclosed in U. S. Patent No. 3,288,011. In this design, the ram is driven so as to be swung or oscillated about these pivotally supported links by means of a crank mechanism driven ;
by an electric motor and clutch, the crank mechanism being con-nected to the connecting rod to the ram to induce the swinging movement. The weight of the ram acts in concurrence with the downward and forward movement of the ram induced during the ram stroking in a forward direction, with the geometry of the links, etc~ producing the full stroking of the ram without the need for reversal of the electric motor or precise control over the crank mechanism or electric motor and clutch.
The swinging movement of the ram in turn produces operation of the cutoff die set which is adapted to be recipro-cated by the ram as it travels with the stock on an upper rail set carried by the ram and a lower rail set fixed to the machine base. The cutoff die set, as described in the aforementioned U. S. patent, includes means for initially clamping the die set to the stock to be severed, causing the die set to traverse the rail set together with the stock. Subsequently, downward move-ment of a cutoff blade, included in the die set is induced by the downward movement of the ram moving through its arcuate path as it swings about the pivotal supports provided by the pivotal links. Continued rotation of the eccentric crank drives the ram to its full down position with further rotation producing a reversal of movement of the swinging ram, to first withdraw the cutoff blade, then releasing the stock from the die set to allow it to be returned to its initial pOsitiQn by means of a return cylinder or other mechanism prior to initiation of a new cycle.
3~4~
:
.:
A variation of the basic mechanism provides for an adjustable `
length connecting rod which serves to provide a capability for shifting the segment o the arcuate path through which the ram is constrained to move by virtue of its support on the pivotally supported links, which shifting provides for adjusting the shut height or the position of the ram in its full down position, as well as the length of its stroke in such a way as to adapt the cutoff apparatus to die sets of varying configurations, to accommo-date its application to varying tube sizes etc.
While these machines have performed very satisfactorily and are adapted to reliably stroke the ram through its required swinging movement, the electric motor, clutch, and eccentric crank components comprise a considerable element of manufacturing cost in the apparatus.
On the other hand, while the aforementioned cylinder-operated presses suffer from the disadvantages described, they do exibit the inherent advantage of a generally lower manufac-turing costs, due to the use of simple power cylinders as a source of operating means for the ram where cylinders of a reasonable size are able to be utilized.
Accordinglyr it is an object of the present invention to adapt a power cylinder to a swinging ram cutoff press of the sort described.
It is a further object of the present invention to adapt such power cylinder to the cutoff mechanism described in such a way as to not necessitate the use of complex controls or adversely affecting the reliability of the machine.
r~ 4 :~0~399~9 ~.
It is yet another object of the present invention to ;
provide such an adaptation which does not involve the use of return springs tending to reduce the available force generated by the cylinder during stroking of the ram.
It is a further object of the present invention to incorporate a power cylinder operating device into a swinging -ram type cutoff apparatus in such a way as to enhance the available force at that portion of the ram's stroke requiring maximum force to be exerted by the ram.
It is yet another object of the present invention to provide such an adaptation without entailing the incorporation of expensive and precision structural or control components.
SUMMARY OF THE INVENTION
These and other objects which will become apparent upon reading of the following Specification and Claims are accom-plished by incorporating a power cylinder into a swinging ram press by providing a toggle link pivotally connected at one end to a connecting rod link, in turn pivotally connected to the ram, with the power cylinder pinned to the connected ends of the toggle link and connecting rod so as to act as a toggle mechanism upon stroking of the power cylinder. The relative geometry of the ram supporting links, the toggle link, the connecting rod link and the power cylinder is such that the toggle mechanism is at the extreme, advanced position of the ram, and the power cylinder executes its full oscillation of the ram upon a stroke in either direction to obviate the need for a reversal of the cylinder-operating member during the stroking of the ram. The connecting rod link is adjustable in length to provide a capability for adapting the cutoff apparatus to varying shut height and stroke requirements of differing die set sizes and configurations.
1~83~
BRIEF DESCRIPTION OF THE D~WINGS
FIGURE 1 is a ~ront elevational view of a swinging -ram cutoff press, according to the present inv~ntion.
FIGURE 2 is a side elevational view of the swinging ram cutoff press, shown in FIGURE 1.
FIGURE 3 is a view of the Section 3-3, taken in FIGURE 1.
FIGURE 4 is a view of the Section 4-4, taken in FIGURE 1.
FIGURE 5 is a diagrammatic view of the swinging ram cutoff press, shown in FIGURE 1, in an advanced position of the swinging ram.
FIGURE 6 is a diagrammatic representation of the swinging ram, shown in FIGURES 1 through 5, w:ith the swinging ram elevated by retraction of the power cylinder.
FIGURE 7 is a diagrammatic representation of the swinging ram cutof press, shown in YIGURES 1 through 6, with an adjustment of the length of the connecting rod link to pro-duce a longer stroke, greater shut height stroking of the swinging ram.
DETAI~ED DESCRIPTION
In the following detailed description certain specific terminology will be utilized for the sake of clarity and a parti-cular embodiment described, but it is to be understood that the same is not intended to be limiting and, indeed, should not be so construed, inasmuch as the invention is capable of considerable variation within the scope of the appended claims.
Reerring to the drawings, and particula~l~ FIGURES 1 through 4, the swinging ram cutoff apparatus 10, according to the present invention, is depicted. The cutoff apparatus 10 ~ ..
?3g4~ :
includes base support means 12 including a lower housing 14 and an upper housing 16, each comprised of a steel weldment. Sup-ported on the upper housing 16 for swinging movement is a die set operating ram 18, the means providing the pivotal support :
being provided by a pair of pivotal links 20 and 22 pinned at one end to the upper housing 16 and at the other to the ram 18.
This mode of support serves to constrain the ram to swinging movement through an arcuate path.
This swinging movement is adapted to operate a die ~ :
set 24 which is retained between an upper rail set 26 affixed ~.
to the lower surface of the ram 18 and a lower rail set 28 affixed to the lower housing 14 by means of an upper die set carriage 30 and a lower die set carriage 32, as shown in FIGURES
1 and 2. The descending movement of the ram 18 created by its swinging motion reduces the clearance between the upper rail set 26 and lower rail set 28 which movement induces operation of the ~"
cutoff die set 24. This operation includes a movement of a pair of clamping jaws 34 and 36 upon initial downward movement of the :
ram 18 to clamp the die set 24 to the work W passing through the clearance space between the upper rail set 26 and the lower rail set 28, clutching the die set 24 to the workpiece W so as to cause it to move together therewith along the upper rail set 26 and the lower rail set 2~.
Further downward movement of the ram 18 occurring as i~
its swinging motion progresses causes operation of the cutoff blade 38 causing the severing of the work W within the die set 24. Upon reversal of movement of the ram 18, the cutoff blade :~:
38 is initially withdrawn, then the clamping jaws 34 and 36 are operated to release the work W, all of this taking place before the die set 24 has reached its limit of travel on the upper rail set 26 and lower rail set 28. Upon release of the clamping jaws :
~399LS~
34 and 36 a return cylinder, not shown, returns the die set 24 to its initial position, as shown in FIGURE 1.
Since this aspect of the cutoff press per se does not comprise the present invention and inasmuch as the details of the same are now very well known to those skilled in the art, the specific design of the die set 24 and other structural de-tails relating thereto are not here disclosed.
A pair of baffles 40 and 42 are typically provided to collect the cutoff slugs caused by shearing of the workpiece W, which may be collected into a bin, not shown, disposed within a cutout opening 44 in the front plate of the lower housing 14.
The links 20 and 22, as noted above, are pivotally supported on the upper housing 16 and also pivotally connected to the ram 18. FIGURE 4 depicts in some detail the nature of these pivotal connections, with the connection of link 22 de-picted as typical. Each of the links 20 and 22 are bifurcated into arms 48 and 50 to form a clevis at its lower end, receiving a pivot pin 46 passing through each arm 48 and 50 of the link 22 and also through a bore 52 formed in the ram 18. A pair of needle bearings 54 and 56 are provided to provide a rotatable support for the pivot pin 46 within the bore 52, with a spacer sleeve 58 provided to maintain the separation of needle bearings 54 and 56. A pair of thrust washers 60 and 62 are also included.
The link 22 is pivotally supported at its other end within the upper housing 16 between a pair of end plates 62 and 64 forming part of the weldment of which the upper housing 16 is constituted, by means of a pivot pin 65 having end portions 66 and 68 disposed and retained between the end plates 62 and 64 with a central portion 70 passing through a bore 72 formed in the link end portion 74 joining the bifurcations 48 and 50.
.. , . . .. .. : ~ :: . . . .
~ ~339~9 ;~
A pair of needle bearings 76 and 78 are provided, maintained in axial position by means of a spacer sleeve 80.
Thrust bearings 82 and 84 are also provided cooperating respec~
tively with a boss portion 85 welded to end plate 62 and a shoulder formed by the enlarged diameter end portion 68 of the connecting pivot pin 70. A boss portion 87 is also provided receiving the end portion 68, as shown.
Lubrication fittings 86 and ~8 may be provided in order to supply lube passages 90 and 92 formed internally in the pin 46 and 70, respectively. Suitable retainers 94, 96, 98 and 100 are provided to provide endwise or axial retention of the pivot pins 46 and 70, respectively, with the lube fittings 86 and 88 and cap screws 102 and 104 being provided to secure the respective retainers 94, 96, 98 and 100 to the link 22 and the upper housing 16, respectively.
The ram operating mechanism which is adapted to oscil-late the ram through its swinging movement in the arcuate path through which it is constrained to move by the links 20 and 22, includes a toggle link 106, a connecting rod link 108 and an operating cylinder assembly 110. The toggle link 106 is mounted at one end to the upper housing 16 in a similar Eashion as the links 20 and 22 by the journaling of a end section 109 in the side plates 62 and 64 included the upper housing 16 weldment.
The toggle link 106 has bifurcated portions 111 and 112 which act as a clevis for a master pivot pin 114 retained in the outer end of bifurcations 111 and 112 by means of retainer plates 115 and 116 retained by cap screws 118 at one end and a lube fitting 120 at the other end in similar fashion to the other pivotal connections, described above.
Master pivot pin 114 has journaled thereon one end of the connecting rod 108. The connecting rod 108 is formed as two . . : ; .. , ,-- .. :, :
9~9 ~
end portions 124 and 126 joined by an oppositely threaded adjusting rod 128 threadably received within bores 130 and 132 formed in the respective connecting rod ends 124 and 126. The threaded adjusting rod 128 having a central wrenching portion .
130 so as to enable the threaded rod to be rotated to vary the effective length of the connecting rod 108. The upper end 124, as noted, is journalled on the master pivot pin 114, as shown, with bearing 134 provided and thrust spacers 136 and 138, in-termediate the clevis 141 end portions 140 and 142 of the oper- :
ating cylinder assembly 110, to be described further herein.
The clevis portions 140 and 142 are similarly journalled by means of rotary bearings 144 and 146 receiving the master pivot pin 114 with thrust spacers 148 and 150 provided intermediate the bifurcations 110 and 112 of the toggle link 106 and the clevis portions 140 and 142 of the operating cylinder assembly 110. , .
The lower connecting rod end 126 is journalled within an opening 150 provided in the ram 18 in the region whereat a pivot pin 152 associated with the front pivotal link 20 is con-nected to the ram 18 so that the connecting rod 126 is also journalled on the pivot pin 152 as provides the pivotal support for the link 20. A needle bearing 154 is provided while separate bearings 156 and 158 are provided in appropriate openings in the ' bores in the ram 18 to provide a rotatable support of the ram 18 on the pivot pin 152. Retainer thrust bearings 160 and 162 are also provided to maintain the proper spacing between the ram 18 and bifurcated portions 164 and 166 of the pivot link 20. Cap screws 168 cooperating with a retainer plate 170 and a lube fitting 172 cooperating with a retainer plate 174 serves to retain the pivot pin 152 in the assemblage.
1~3g~9 ~ .:
The power cylinder assembly 110 includes a power cylinder body 176 pivotally mounted at its rear portion by means of a pivot pin 178 passing through an opening 180 formed in a mounting plate 182 affixed to the rear of the power cylin-der body 176. The pivot pin 178 is retained in a pair of clevis ~
plates 184 and 186 welded to a mounting bracket 188 secured to ~ -the upper housing 16, as shown in FIGURES 1 and 2. ;
The power cylinder assembly 110 also includes an -operating rod 192 connected to a clevis end portions 140, 142.
In operation, the cylinder assembly 110 is in an initial position, either with the operating rod 192 in the fully retracted position, as shown in FIGURE 1, or fully extended position, as shown in FIGURE 6 in schematic form. ~n either the fully retracted or extended position, the ram 18 is in the full up position, with the toggle link 106 and connecting rod 108 askew, as shown in FIGURES 1 or 6. By initiation of a cutoff cycle, the cylinder assembly 110 is pressurized by means of solenoid control val~res, not shown, to cause the operating rod 192 to be retracted~ or extended. The toggle link 106 and connecting rod link 108 are drawn into the aligned position, as shown in FIGURE 1, with an incraasing mechanical advantage characteristic of toggle mechanisms being imposed on the ram 18 through the connecting rod 108. A maximum mechanical advan-tage is achieved in the ull down position o the ram 18 as de-picted in FIGURE 1, since the operating rod extends trans-versely to the aligned toggle link 106 and connecting rod link 108 and generally transversely to the pivotal links 20 and 22.
Continued movement of the operating rod 192 again produces ele-vation of the ram 18 so that in the fully retracted or extended position, the ram 18 has again returned to the initial or up position. It must be seen that the power cylinder 110 need not be reversed during the cycling of the cutoff press, but in a ll)B3949 single stroke produces both the down and up movement of the ram.
Furthermore, the mechanical advantage is at a maximum when the force requirements are at a maximum, i.e., at the ram full down position. It should also be noted that the ram 18 weight does not work in opposition to the force applied by the power cylin-der assembly 110 to further maximize the force able to be exerted by the power cylinder assembly 110 to the ram 18.
The adjustment of the connecting rod 108 produces a very advantageous flexibility in the application of any given press, since the shut height and stroke may be varied by means of the adjustability in length of the connecting rod 108. This can be seen by ~he schematic representation of FIGURE 7 showing the adjustment rod 128 threaded fully into the connecting rod ends 124, 126 to reduce the connecting rod 108 length to a minimum.
This produces an increased stroke, but instead o~ reducing the shut height, the shut height is increased, as shown in FIGURES 5 and 7.
The power cylinder assembly may be provided by an air cylinder, since the output requirements are reduced to a minimum by the disclosed arrangement, although hydraulic cylinders alter-natively could be used if desired. In addition the power cylin-der assembly 110 would normally include means for controlling decelerati~on to control bounce at the end of the retraction or extension of the operating rod 192, but, since such devices are well known in the art, and many suitable designs are available, this device is not here described.
--1~--
Claims (6)
1. A swinging ram cutoff apparatus for severing lengths of elongated stock such as tubing comprising:
base support means;
a ram;
support means mounting said ram on said base support means for swinging movement through an arcuate path, said support means comprising a plurality of links, means pivotally supporting each of said plurality of links on said base support means at one end and pivotally connecting each of said plurality of links to said ram at their other ends;
ram operating means oscillating said ram on said base support means through said arcuate path, said ram operating mechanism including a toggle link pivotally supported on said base support means, and a connecting rod link pivotally connected at one end to said ram, and also including a pivotal connection between said toggle link and said connecting rod link, said con-necting rod link and said toggle link being mounted to be aligned with each other when said ram is in its extreme down position in said oscillation arcuate path and further wherein said plurality of links extend in a generally transverse direction to said aligned connecting rod link and toggle link;
said ram operating means further including means mov-ing said pivotal connection linearly to produce said oscillation of said ram through said arcuate path; and a cutoff die set operable by said oscillation of said ram to sever said elongated stock.
base support means;
a ram;
support means mounting said ram on said base support means for swinging movement through an arcuate path, said support means comprising a plurality of links, means pivotally supporting each of said plurality of links on said base support means at one end and pivotally connecting each of said plurality of links to said ram at their other ends;
ram operating means oscillating said ram on said base support means through said arcuate path, said ram operating mechanism including a toggle link pivotally supported on said base support means, and a connecting rod link pivotally connected at one end to said ram, and also including a pivotal connection between said toggle link and said connecting rod link, said con-necting rod link and said toggle link being mounted to be aligned with each other when said ram is in its extreme down position in said oscillation arcuate path and further wherein said plurality of links extend in a generally transverse direction to said aligned connecting rod link and toggle link;
said ram operating means further including means mov-ing said pivotal connection linearly to produce said oscillation of said ram through said arcuate path; and a cutoff die set operable by said oscillation of said ram to sever said elongated stock.
2. The cutoff apparatus according to Claim 1 wherein said means moving said pivotal connection includes a power cylinder means drivingly connected to said pivotal connection and producing said movement of said pivotal connection.
3. The swinging ram cutoff apparatus according to Claim 2 wherein said power cylinder means includes an operating rod pivotally connected to said pivotal connection.
4. The swinging ram cutoff apparatus according to Claim 1 wherein said connecting rod link includes means for adjusting the length of said connecting rod link, whereby said arcuate path through which said ram is oscillated may be shifted by adjustments made in the length of said connecting rod link.
5. The swinging ram cutoff apparatus according to Claim 1 including means for operating said power cylinder oper-ating member to an extended or retracted position, said ram being in an extreme up position of said arcuate path in the fully extended or retracted position of said operating member, whereby said ram may be oscillated through said arcuate path by the operation of said power cylinder from either its extreme retracted position to its extended position or from its fully extended position to said retracted position, whereby a rever-sal of said power cylinder means is not required during said oscillation of said ram through said arcuate path.
6. The swinging ram cutoff apparatus according to Claim 1 further including means for adjustably varying the length of said connecting rod link, whereby said arcuate path through which said ram is oscillated may be shifted to produce variations in stroke down position of said ram.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US79920477A | 1977-05-23 | 1977-05-23 | |
| US799,204 | 1977-05-23 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1083949A true CA1083949A (en) | 1980-08-19 |
Family
ID=25175290
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA302,296A Expired CA1083949A (en) | 1977-05-23 | 1978-04-28 | Cylinder operated swinging ram cutoff press |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JPS53145179A (en) |
| CA (1) | CA1083949A (en) |
| DE (1) | DE2822475A1 (en) |
| GB (1) | GB1600586A (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3102786A1 (en) * | 1981-01-28 | 1982-08-26 | National Mfg. Co., Inc., 07928 Chatham, N.J. | Machine for trimming the edges at the open ends of metal containers |
| FR2624772B1 (en) * | 1987-12-22 | 1990-06-08 | Ravni Lionel | DEVICE FOR THE CONTINUOUS CUTTING OF FILIFORM ELEMENTS IN PARTICULAR |
| CN113021437B (en) * | 2021-03-01 | 2023-01-10 | 安徽风芯材料科技有限公司 | Sectional type cutting equipment of macromolecular material polyethylene board production usefulness |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1508433A (en) * | 1920-02-02 | 1924-09-16 | Charles M Woulf | Baling press |
| GB835388A (en) * | 1957-10-11 | 1960-05-18 | Ets Grimar | An arrangement for actuating shears and similar machines and for various types of presses |
| US3288011A (en) * | 1965-06-30 | 1966-11-29 | Borzym Alexander | Flying cutoff machine with swinging ram |
| DE1974429U (en) * | 1967-09-18 | 1967-12-07 | Kieserling & Albrecht | PRESS WITH HYDROMECHANICAL DRIVE. |
| GB1337666A (en) * | 1971-09-02 | 1973-11-21 | Victory Kidder Ltd | Guillotines or the like machines |
| DE2234872A1 (en) * | 1972-07-15 | 1974-01-31 | Stocko Metallwarenfab Henkels | CABLE LUG STOP MACHINE |
| DE7535078U (en) * | 1975-11-05 | 1976-03-18 | Ungerer Geb. Dollinger, Irma, 7530 Pforzheim | FLYING SWING SHEARS |
-
1978
- 1978-04-28 CA CA302,296A patent/CA1083949A/en not_active Expired
- 1978-05-03 GB GB1745978A patent/GB1600586A/en not_active Expired
- 1978-05-17 JP JP5870778A patent/JPS53145179A/en active Granted
- 1978-05-23 DE DE19782822475 patent/DE2822475A1/en not_active Ceased
Also Published As
| Publication number | Publication date |
|---|---|
| GB1600586A (en) | 1981-10-21 |
| JPS5749330B2 (en) | 1982-10-21 |
| JPS53145179A (en) | 1978-12-18 |
| DE2822475A1 (en) | 1978-12-07 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |