MXPA96005556A - Adjustment travel connection - Google Patents

Abstract

The present invention relates to a mechanical press comprising: a press connection member, an eccentric bushing disposed within the press connection member, a second eccentric member disposed within the eccentric bushing creating an interface between said second eccentric member releasably connected with said eccentric bushing, a rotating crankshaft connected to the second eccentric member, and means for connecting said eccentric bushing with said press connection member by a temporary press fit adapted to prevent rotation therebetween and allow rotation with the crankshaft when said medium is activated and then causes an adjustment of the pre-travel path

Description

CONNECTION OF ADJUSTABLE TRAVEL BACKGROUND OF THE INVENTION 1. Field of the invention. The present invention relates to a mechanical punching press and sausage presses, and, more particularly, to an apparatus for an adjustable stroke connection for adjusting the length of travel of the press carriage. 2. Description of the related art. In mechanical presses, it is often desirable to adjust or change the path length of the reciprocating member, for example the carriage, to which the die cutting tool is installed. In some adjustment systems for prior art tools, there is a tendency for the parts of the system to wear out after a certain period of time in operation. It would be desirable to provide an apparatus or system that can utilize a travel length adjustment of the carriage or other parts quickly, easily and accurately. SUMMARY OF THE INVENTION The present invention provides an eccentric adjustable stroke connection system for use in changing the travel length of the carriage or other member of the mechanical press. An eccentric (arrow) present in the crankshaft carries an eccentric bushing, disposed thereon. A press connection member, such as a connecting rod or link, is attached near the eccentric bushing. During normal operation, there is a relative movement between the eccentric bushing and the connecting member or arm to thereby cause reciprocation of the press carriage. During travel adjustment, the pressurized oil is communicated between the eccentric bushing and the eccentric crankshaft, thereby releasing the press fit or interference fit between them, and causing the eccentric bushing to expand and form a connection for the adjustment of temporary press with the connection arm. At this time, the crankshaft can rotate, along with its eccentric (arrow), to thereby change the position of the eccentric inside the eccentric bushing. This causes a change in the length of travel. Then the oil pressure is released, which causes the eccentric bushing to contract and again, forms a press fit or interference fit with the eccentric crankshaft and releases the temporary press fit connection between the outside of the eccentric bushing and the connecting member or arm. After the oil pressure is reduced, normal operation can proceed. The invention comprises, in one of its forms, a mechanical press having a press connection member, an eccentric bushing disposed within the press connection member, and a second eccentric member disposed within the eccentric bushing, the second eccentric member that It connects freely with the eccentric bushing. The invention includes the mechanisms for connecting the eccentric bushing to the press connection member to prevent the rotation of these and to allow the rotation of the second eccentric member within the eccentric bushing, according to which the rotation of the crankshaft, when the members are activated , causes an adjustment of the travel of the press. The invention also includes, at least, a high coefficient of friction seal, disposed between the second eccentric member and the eccentric bushing, wherein the high friction seal prevents rotation of the eccentric bushing in relation to the second eccentric member before the eccentric member. creation of the temporary press adjustment connection. The invention comprises, in another form thereof, the mechanisms for fluid pressure for connecting the eccentric bushing to the pressure connection member, to prevent rotation therebetween and allow rotation of the second eccentric member within the eccentric bushing. The mechanisms for fluid pressure include the fluid conduits through the crankshaft, in communication with the fluid pressure-enhancing mechanisms, to increase the fluid pressure through the crankshaft passages. In one form of the invention, the intensifier may include a movable piston to increase the fluid pressure within the crankshaft passages. An advantage of the present invention is that the mechanical press can include a connection for adjusting the compact path that is operated by the fluid pressure. Previously, the connections for the travel adjustment used keys and / or gears between the crankshaft and the various eccentrics. The present invention utilizes a connection that is simple in design and greatly reduces the number of parts necessary for a travel adjustment mechanism. Another advantage of the present invention is that the significant reduction in costs is obtained together with the increase in the functionality of the press with a simple stroke adjustment connection. Additionally, maintenance costs for the adjustment and replacement of parts are reduced, compared to the previous adjustable travel connections. Another advantage of the present invention is that a fluid intensifier achieves a high average of fluid intensification, while being disposed within the press crankshaft. The novel fluid enhancer of the present invention is simple in its construction and operation, so it requires simple rotary sealing arrangements.

BRIEF DESCRIPTION OF THE DRAWINGS The aforementioned and other characteristics and advantages of the present invention, and the way to achieve them, will be more apparent and the invention will be better understood with reference to the following description of the embodiments of the invention taken in conjunction with the accompanying drawings, wherein: Figure 1 is a perspective, schematic view in partial section of a portion of the crankshaft and the carriage connection; Figures 2A and 2B are two sectional sectional views of the crankshaft and the eccentric bushing, the minimum and maximum path portions respectively, in which the connection is shown in an elevational view, and where the oil conduits for the Lubrication and crankshaft adjustment; Figure 3 is an enlarged view of the crankshaft and the eccentric bushing of Figure 2A; Figures 4A and 4B are axial cross-sectional, schematic views of the invention at separate moments of operation, especially during normal punching operations and during adjustment of stroke length / eccentric adjustment, respectively; Figure 5 is a sectional, axial sectional view of an alternative embodiment of the invention showing an additional connection of the hub between the eccentric bushing and the connection, and with an oil conduit for the adjustment of the crankshaft shown; Figure 6A is an axial sectional view of a first eccentric bushing. Figures 6B and 6C are sectional, axial views and a side view, respectively, of another eccentric bushing. Figure 6D is a cross-sectional, axial view of yet another eccentric bushing; Fig. 7 is a cross-sectional, axial view of an embodiment of the present invention in which the suitable method, which is provided, of high oil pressure to the crankshaft without a rotating high-pressure joint is shown; Figure 8 is a schematic sectional partial sectional view of the second seal configuration for sealing the high pressure oil between the eccentric bushing and the crankshaft eccentric; Figure 9 is an elevation view of the typical mechanical press using the present invention; and Figure 10 is a sectional, schematic sectional view of one of the U-shaped seals of the present invention. The corresponding reference characters indicate the corresponding parts through several views. Although the drawings represent the embodiments of the invention, the drawings are not necessarily to scale and certain features may be exaggerated or omitted, to better illustrate and explain the present invention.

DETAILED DESCRIPTION OF THE EMBODIMENTS The adjustable travel connection of the present invention is ideally suited for a broad classification of die and mechanical press configurations. Conventionally, a mechanical press (Figure 9) typically includes a crown portion 115, a bed portion 117 having a set of supports connected thereto, and the support uprights 113 connected to the portion of the crown 115 with the portion of the bed 117. The uprights 113 are connected to or integrated with the underside of the crown and the upper side of the bed. The carriage 119 is placed between the uprights 113 to guide the reciprocal movement relative to the bed. The tie rods (not shown), which extend through the crown, the uprights and the bed portion, are attached at each end with the bolts of the tie rod. The members of the leg 118 are formed as an extension of the bed and are generally mounted on the work floor by means of the blow absorbing insoles. To drive the reciprocal movement of the carriage 119, a drive mechanism 114 for the press is provided. A suitable mechanism includes a driver motor 116, attached by means of a belt, to an auxiliary steering wheel attached to the crown 115. The auxiliary steering wheel 120 is connected to the main steering wheel 112, which, in turn, is selectively engaged by the clutch of the clutch / brake combination to drive the rotation of the press crankshaft 14, which, in turn, affects the movement of the carriage by means of the extended connections between the car and the crankshaft. This description of the press 110 and its driving mechanisms is merely illustrative. A wide variety of mechanical presses are well known in the art, and the present invention can be used with a mechanical press that uses a crankshaft type device to achieve the reciprocal movement of a press component. An example of the mechanical press is presented in U.S. Patent No. 5,189,928, entitled "ADJUSTABLE STROKE PUNCH PRESS", the patent of which is incorporated herein by reference. The reference to Figure 1 shows a perspective, schematic view of a portion of the crankshaft, its associated eccentric bushing, and the connection that is driven by the rotation of the crankshaft. The connection can be formed of a lower portion and a cap, and a lower portion of the connecting member 10 is typically attached in a desired shape to the carriage press. The crankshaft 14 includes a cylindrical main portion 16, axially centered on the axis of the rotating crankshaft and a second eccentric member, such as an eccentric cylinder 18 fixed rotatably thereto or formed integrally therewith. Although only one eccentric crankshaft is shown, multiple eccentrics can be provided along with the axial length of the crankshaft 14 to cooperate with additional connections that are not shown. The crankshaft eccentric ring 18 is an eccentric bronze bushing 20. Figures 2A, 2B and 3 best illustrate the configuration of these components, wherein the main portion of the crankshaft 16 is shown in dotted lines. During the normal operation of the press 16, as the crankshaft 14 rotates, the eccentric bushing 20 is placed in place on the eccentric of the crankshaft 18 (i.e., rotated with it) by means of a press fit or interference fit around the eccentric circumference of the crankshaft at 22 which is sufficient to transmit the torque that is required to meet the die-cutting or forming operation. The oil supplied to lubricate the rotation of the eccentric bushing 20 relative to the connection 10. For example, the oil passes through the upper part of the connection or the connection cover in a conduit 24 and in an annular gap of. 003"up to .005" 26, to provide an oil film in which the eccentric bushing rotates. Figure 4A shows how the oil, such as at 125 p.s.i., can be distributed through a tube 25 and duct 24 to the annular gap / running set 26 to lubricate the connecting movement. At this point of the operation, the conduits in Figure 4A that are indicated in dashed lines within the crankshaft 14 and the eccentric 18 are not used in the manner to affect the stroke adjustment that will be described below. As the crankshaft 14 and its co-rotating eccentric bushing 20 rotate relative to the connection 10, the connection 10 moves up and down to effect a reciprocal movement of the carriage 119. When a change or adjustment in the travel is desired. of the carriage 119, the rotation of the crankshaft 14 stops, and therefore the movement of a carriage, and the oil that is supplied by means of a conduit 24 in the upper connection 10 stops. Then, the high pressure oil is supplied through the crankshaft 24, such as through a hole 28 and one or more crossed holes 29, towards the inner diameter of the eccentric bushing 20. It is expected to have a high oil pressure, but not Limited to 7,000 psi up to 10,000 p.s.i., and distributed circumferentially around the crankshaft eccentric 18. Seals 100, 102 may be provided, along the edges in the inner diameter of the bushing 20, to prevent escape of high oil pressure. The high pressure oil tends to circularly expand the bushing 20 to release the press fit between the eccentric crankshaft 18 and the eccentric bushing 20. The high pressure oil creates a small eccentric annular gap 20 and an eccentric crankshaft 10 indicated in 31, and creates a temporary press fit or interference fit situation at 33, circumferentially between the eccentric bushing 20 and the connection 10. (see also Figure 4B) The lubricated annular gap 31 allows the crankshaft 14 to rotate relative to the eccentric bushing 20, which, because its temporary press fits with the connecting member 10 does not rotate. While the crankshaft 14 rotates, the main portion of the crankshaft 16 changes in a different position relative to the eccentric bushing 20, which, in turn, effectively changes the length of the path of the connection 10 to the desired length. When the adjustment is complete, the high-pressure oil at 31 is supplied even though the crankshaft is stopped, allowing the eccentric bushing 20, due to the resilience of its construction metal, to return to its press fit with the crankshaft eccentric ( second eccentric member 18) to again allow the rotation of the crankshaft to alternate the connection and, therefore, continue the punching operations. Figures 2A and 2B show how a rotation of the crankshaft 14 together with the eccentric bushing 20 to 1802 is achieved, as shown, at a running length of 2.5". Other course lengths are naturally within the scope of the invention. Figure 5 shows an alternative embodiment of the invention, and this embodiment is shown during the punching operations In this embodiment, an additional bushing connection 11 is interposed between the connection 10 and the bushing 20, and the connecting bushing 11 fits in a circumferential groove provided in the outer radial portion of the eccentric bushing 20. The oil can be introduced into an annular gap 26 to provide an oil film 26 which facilitates the free rotation of the crankshaft and its eccentric bushing relative to the connection 10 and its associated bushing 11. In this embodiment, the seals 35 prevent high-pressure oil leakage from between the bushing. of the crankshaft 18 and an eccentric bushing 20. During travel adjustment, the high pressure oil is supplied through multiple crossed holes 29 fed by an axial hole 28. The axial hole extends through the crankshaft towards each connection to the along the axial length of the crankshaft. To help prevent the possibility that the eccentric bushing 20 takes the "egg" shape and develops uneven tension when it expands to release its press fit with the crankshaft eccentric 18, as described above, they can be used, possible form, a variety of eccentric bushings. For example, Figure 6A is a sectional, sectional, axial view of an eccentric bushing 20 in which the portion of the eccentric compartment 40 includes an internal cavity 41 in fluid communication with the internal opening of the eccentric bushing 43, which receives the eccentric crankshaft 18. When the oil is introduced at high pressure, in the form of a circumference, along the eccentric of the crankshaft, the oil at high pressure provides a force directed radially outwards (as indicated by the arrows 42). ), and the force also acts within the cavity of compartment 41, as shown. Figure 6B is a cross-sectional view, conceptually similar to the view of Figure 6A, in which the portion of the outer compartment has a beam-like configuration I, with a central rib 45. The forces produced by high-pressure oil are indicated again at 42. Figure 6C shows the eccentric bushing of Figure 6B in the side view, where it is shown how the eccentric compartment includes the rib 45 removed the axial edge of the eccentric bushing. Figure 6D presents yet another embodiment in the cross-sectional view, wherein the eccentric compartment 47 of the eccentric bushing 20 is hollow. Referring now to Figure 7, yet another aspect of the present invention allowing a conventional rotary union is shown., as opposed to the rotating union of high pressure, which is used to introduce the high pressure oil used for eccentric hub expansion. Most of the embodiments shown in Figure 7 are conceptually the same as the embodiments described above. A cylindrical crankshaft eccentric 52 is integrated with the main portion of the crankshaft 50 and ringed by an eccentric bushing 54 having a press fit at 55 on the eccentric 52. A ring bushing 56 is provided to the eccentric bushing 54 with a small bushing 56. annular gap 60. The connection bushing 56 is a press fitted within an opening provided between the connection cover 63 and the lower connection 62, which is attached to the press carriage. Axially, it extends through the main portion of the crankshaft 50, is the orifice 65, from which radially branched transverse holes 67 extend through the eccentric of the crankshaft 52. The axial bore 65 extends towards the left in Figure 7 to other connections. To achieve the high pressure of the oil that is used to expand the eccentric bushing 54 without needing to introduce the oil at that high pressure through the rotating union in the crankshaft, an intensifier is provided at an average 10: 1 (or other). At the end of the axial hole 65 is the intensifying rod or piston 69 which is sealed by means of a seal 70, placed in the internal groove of the crankshaft. Alternatively, the seal can be mounted on the plunger 69. The plunger 69 terminates in a circumferentially sealed python 72. The oil, for example at 1,000 psi, passes from 74 in the rotary union 76 and in the chamber 78 where it again drives the piston 72 to force the plunger 69 to move to the left. During the movement of the plunger, the air passes through the vent 79. Since the plunger has a tenth of the cross-sectional area, or another fraction, of the cross-sectional area of the piston 72, the oil which is already inside the axial hole 65 and in the transverse holes 67, increases to a pressure of approximately 10,000 psi by the movement of the piston. The piston and piston are designed such that they have sufficient travel to allow sufficient oil to travel to cover the expansion of the eccentric bushings of all connections. When the high pressure oil within the transverse holes 67 moves in the cavity of the internal diameter of the eccentric bushing 54 to radially expand the bushing, the seals 81 prevent the oil from escaping or leaking out of the closed system. Figure 8 is a partial cross-sectional, axial view of another method of sealing the high-pressure oil used to expand the eccentric bushing. In this embodiment, the O-shaped ring face seal 84 is mounted on the eccentric bushing 86 to cooperate with the radially aligned walls of the ribs 88 projecting from the eccentric of the crankshaft 90. O, the seals can be provided 88 to project against the oil leak. Another configuration can also be employed within the scope of the present invention.

The present invention includes two seals 100 and 102 (Figures 1 and 10) made with a high coefficient of friction material which, when pressurized, creates a supporting force or mechanism such that both the eccentric bushing 20 and the second member eccentric 18 are closed together until a press fit or interference fit is created in the gap 26, placed between the connecting member 10 and the eccentric bushing 20. The torque of the clutch, during the rotation of the crankshaft 14 will have to exceed the high coefficient of friction of this characteristic which, therefore, is created between the eccentric member 18 and the eccentric bushing 20. This feature allows the multiple eccentrics to move at the same time with the same angle, without any additional teeth, gear teeth , or other mechanisms to ensure the appropriate time of displacement between them. This seal arrangement, with a high coefficient of friction, also reduces the parts and simplifies the design. No other mechanical parts are needed to maintain the position of multiple eccentrics relative to each other, such that the carriage remains parallel after the change of the press path is complete. A further feature of the invention is that the same adjustable path connection between the crankshaft and the rocker arm can be used, so that the balance can be maintained. Thus the types of connection members usable with the present invention can be those of the normal connection arm or other link to the press part, such as a dynamic rocker. Although the adjustable travel mechanism of the present invention utilizes a single oil conduit through the crankshaft, it may be possible to have two different oil passages, which come from opposite sides, one to operate the adjustable stroke connection mechanism. of the present invention, in relation to the carriages, and the other conduit operating the travel adjustment for a rocker arrangement. A type of seal useful in the present invention has been found, the U-type seal. This type of seal operates by means of the action of the pressure of an internal fluid separating the lips of the seal. This movement creates a brake force between the eccentrics and the stump, which allows the development of a grip force. It has been found that the U-shaped or U-cup seal operates better than any other type of seal that has been used up to now. Figure 10 shows a typical U-shaped seal (100, 102), while applying pressure between the two eccentric members. The grip force increases with pressure. Therefore, the clamping force can be easily handled for any torque that is required in the device.

While the invention has been described as having a preferred design, the present invention can be modified even within the spirit and scope of this presentation. Therefore, the application is intended to cover any variation, used, or adaptations of the invention that use its general principles. Additionally, this application attempts to cover the derivatives of this presentation as within the customary and known practice of the art, to which this invention belongs and which falls within the limits of the appended claims.

Claims (15)

1. CLAIMS: 1.
2. A mechanical press comprising: a press connection member; an eccentric bushing arranged with the press connection member; a second eccentric member disposed within the eccentric bushing, the second eccentric member releasably connected to the eccentric bushing; a rotating crankshaft connected to the second eccentric member; and the mechanisms for connecting the eccentric bushing to the press connection member to prevent rotation therebetween and allow rotation of the second eccentric member within the eccentric bushing by the rotation of the crankshaft when the mechanisms are activated, then causing a travel adjustment of the press The press according to claim 1, wherein the connection mechanisms comprise a fluid pressure applied to the interface between the second eccentric member and the eccentric bushing whereby the pressure allows relative rotation between the second eccentric member and the eccentric bushing.
3. The press according to claim 1, wherein the connection mechanisms comprise the pressure of the fluid applied to the interface between the second eccentric member and the eccentric bushing causing the eccentric bushing and the press connection to be connected together by a temporary press adjustment connection.
4. 4. The press according to claim 3 in which the mechanisms operate through the crankshaft.
5. The press according to claim 3, further comprising at least one high friction seal disposed between the second eccentric member and the eccentric bushing whereby the high friction seal prevents rotation of the eccentric bushing relative to the second eccentric member. prior to the creation of the temporary press adjustment connection.
6. The press according to claim 5, wherein the friction wing seal comprises a U-shaped seal.
7. The press according to claim 1 wherein the mechanisms operate through the crankshaft.
8. The press according to claim 1, wherein the eccentric bushing includes an internal cavity in communication with the second eccentric member.
9. The press according to claim 1, wherein the eccentric bushing includes a beam-shaped rib I in a cross section.
10. 10. A mechanical press comprising: a press connection member; an eccentric bushing arranged with the press connection member; a second eccentric member disposed within the eccentric bushing, the second eccentric member releasably connected to the eccentric bushing; a rotating crankshaft connected to the second eccentric member; and the mechanisms for fluid pressure to connect the eccentric bushing with the member for the press connection to prevent rotation therebetween and allow the rotation of the second eccentric member within the eccentric bushing, the mechanisms for fluid pressure include the conduits for the fluid to pass through the crankshaft in communication with the fluid pressure enhancing mechanisms to increase the fluid pressure through the crankshaft ducts.
11. The press according to claim 10, wherein the fluid pressure enhancer includes a movable piston to increase the fluid pressure within the crankshaft passages.
12. The press according to claim 10, wherein the mechanisms for fluid pressure comprise a fluid pressure applied to the interface between the second eccentric member and the eccentric bushing whereby the pressure allows relative rotation between the second eccentric member and the eccentric bushing.
13. The press according to claim 10, wherein the fluid pressure mechanisms comprise the fluid pressure applied to the interface between the second eccentric member and the eccentric bushing which causes the eccentric bushing and the press connection to be connect together by means of a temporary press adjustment connection.
14. 14. The press according to claim 13, which further comprises at least one high friction seal disposed between the second eccentric member and the eccentric bushing whereby the high friction seal prevents rotation of the eccentric bushing relative to the second eccentric member prior to the creation of the adjusting connection of the eccentric bushing. temporary press.
15. 15. The press according to claim 14, wherein the friction wing seal comprises a U-shaped seal.