KR100230587B1 - Adjustable stroke connection of mechanical press - Google Patents

Abstract

The present invention relates to an adjustable stroke connection suitable for a mechanical press. The eccentric bushing is located in a press connecting portion having a second eccentric member located therein. The rotatable crankshaft is connected to the second eccentric member. The mechanism device connects the eccentric bushing to the press connecting member to prevent rotation therebetween, such that the second eccentric member rotates in the eccentric bushing, so that when the mechanism device is operated, the crankshaft Rotation is included to allow press stroke adjustment.

Description

Adjustable Stroke Connection

FIELD OF THE INVENTION The present invention relates to mechanical stamping presses and mechanical drawing presses, and more particularly to devices suitable for adjustable stroke connections for adjusting the stroke length of a press slide.

In mechanical presses, it is generally desirable to adjust or vary the stroke length of the reciprocating member, for example of a slide on which a stamping equipment is installed. In the tooth control system of the prior art, there is a tendency for part of the system to wear out after a certain operating time. It would be desirable to provide an apparatus or system that can be used to quickly, easily and accurately adjust the stroke length of a slide or other parts.

The present invention therefore provides two eccentric stroke connecting systems for use in changing the stroke length of a slide or other member of a mechanical press.

The eccentric member on the rotatable crankshaft is provided in an eccentric bushing located thereon. Press connecting members, such as connecting rods or links, are attached around the eccentric bushings. During normal operation, the press slide reciprocates due to the relative motion between the eccentric bushing and the connecting member or arm. During stroke adjustment, the oil of constant pressure passes between the eccentric bushing and the crankshaft eccentric member, thereby releasing the pressure fit or the forced fit therebetween, so that the eccentric bushing expands to provide a temporary pressure fit with the connecting arm. To form. At this time, the crankshaft rotates along the eccentric member to change the eccentric position inside the eccentric bushing. This causes a change in the stroke length. The oil pressure is then lowered to deflate the eccentric bushing, and again form a pressure fit or a forced fit with the crankshaft eccentric member to release the temporary pressure fit between the outside of the eccentric bushing and the connecting member or connecting arm. After this high oil pressure is reduced, normal press operation can proceed.

As one embodiment of the present invention, the present invention includes a press connecting member, an eccentric bushing disposed in the press connecting member, and a mechanical press including a second eccentric member disposed inside the eccentric bushing and detachably connected to the eccentric bushing. . The rotatable crankshaft is connected to the second eccentric member. The present invention connects the eccentric bushing and the press connection member to prevent mutual rotation and to allow the second eccentric member to rotate inside the eccentric bushing, so that when the means are operated, the crankshaft rotates, thereby adjusting the press stroke. Means for causing. The present invention also includes a seal having one or more high coefficients of friction, wherein the seal is disposed between the second eccentric member and the eccentric bushing, where the high friction force seal is provided prior to the temporary pressure fit. The rotation of the eccentric bushing with respect to the second eccentric member is prevented.

In another aspect of the present invention, the present invention includes fluid pressure means for connecting the eccentric bushing with the press connecting member to prevent rotation therebetween so that the second eccentric member can rotate inside the eccentric bushing. The fluid pressure means comprises a fluid passage through the crankshaft in communication with the fluid pressure enhancing means for increasing the fluid pressure passing through the crankshaft passage. In one embodiment of the present invention, the reinforcement means may include a movable piston for increasing the fluid pressure inside the passage of the crankshaft.

An advantage of the present invention is that the mechanical press may comprise a simple and small-looking stroke regulating connection operated by fluid pressure. The prior art stroke regulating connection used a key and / or gear between the crankshaft and several other eccentric members. The present invention uses a connection that is simple in design and has extensively reduced the number of components required for the stroke adjustment mechanism.

Another advantage of the present invention is that a significant reduction in cost is obtained by increasing the functionality of the press with a simple stroke regulating connection. In addition, the maintenance costs for adjusting and replacing parts are reduced, compared to the adjustable stroke connections of the prior art.

Another advantage of the present invention is the hydraulic reinforcement means which achieves a high rate of hydraulic reinforcement while arranged inside the crankshaft of the press. The new and highly advanced hydraulic enhancement means of the present invention are simple in construction and operation, requiring a simple rotary sealing device.

1 is a partial perspective view schematically showing a cut part of a crankshaft and a slide connecting portion;

2A and 2B are cross-sectional views showing the crankshaft and eccentric bushings at their respective maximum and minimum strokes, with the connections shown in elevation and without oil conduits for lubrication and crankshaft adjustment.

3 is an enlarged view of the crankshaft and eccentric bushing of FIG. 2A;

4A and 4B are axial cross-sectional views schematically showing the invention at separate times of operation, ie during normal stamping operation and during stroke / eccentric adjustment.

Figure 5 is an axial cross-sectional view of another embodiment of the present invention showing an additional connecting bushing between an eccentric bushing and a connecting portion, in which an oil conduit for crankshaft adjustment is shown.

6A is an axial cross-sectional view of the first eccentric bushing.

6B and 6C are axial cross-sectional and side views, respectively, of different eccentric bushings.

6d is an axial cross-sectional view of another eccentric bushing.

FIG. 7 is an axial cross-sectional view of one embodiment of the present invention, showing a suitable method of supplying high pressure oil to a crankshaft, without a high pressure rotating union.

Fig. 8 is a partial cross sectional view schematically showing a second seal shape for sealing high pressure oil between the eccentric bushing and the crankshaft eccentric member.

9 is an elevational view of a typical mechanical press using the present invention.

Figure 10 is a cross sectional view schematically showing one of the U-shaped seals of the present invention.

Like reference numerals refer to like parts in the various drawings. Although the accompanying drawings represent embodiments of the present invention, some of the drawings are not proportional to scale, and specific parts are exaggerated or omitted for ease of illustration and description of the invention.

The above and other features and advantages of the present invention, and a manner for achieving this, will become more apparent by referring to the following description of embodiments of the present invention with reference to the accompanying drawings.

The adjustable stroke connection of the present invention is an apparatus that can be ideally applied to various kinds of shapes of machine presses and stamping presses. Traditionally, the machine press 110 (FIG. 9) typically has a bed portion 117 and a head portion 115 having a head portion 115, a support assembly connected thereto, and a bed portion 117. And an upright member 113 connected to it. The upright member 113 is connected to or integral with the lower portion of the head portion and the upper portion of the bed. The slide 119 is positioned between the upright members 113 for guided reciprocating motion relative to the bed. Support rods (not shown) extending through the head portion, the upright member and the bed portion are attached to the ends of each other with tie rod nuts. The leg members 118 are formed as extensions of the bed and are generally mounted on the floor of the factory by means of shock absorbing plates.

In order to power the reciprocating motion of the slide 119, a drive mechanism 114 for a press is provided. Suitable mechanisms include a drive motor 116 attached to an auxiliary flywheel 120 attached to the head portion 115 by means of a belt. The secondary flywheel 120 is connected to the primary flywheel 112, which is selectively engaged by a clutch of a clutch / brake combination for promoting rotation of the press crankshaft 14, in turn, the slide and the crank. It causes a slide movement through the connection extending between the axes. This press 110 and its drive mechanism are merely examples. Various machine presses are known in the art, and the present invention can be used in any machine press that uses a device in the form of a crankshaft to obtain reciprocating motion of the press member. One example of a mechanical press is known from US Pat. No. 5,189,928 entitled "Adjustable Stroke Punch Press", which is incorporated herein by reference.

1 is a perspective view schematically showing a part of a crankshaft, a connecting portion in which force is transmitted by the combined eccentric bushing and crankshaft rotation. The connecting portion is formed with a lower portion and an upper portion, and the lower portion of the connecting member 10 is attached in a typical suitable manner to the press slide. The crankshaft 14 includes a cylindrical body 16 axially centered on the rotating crankshaft and a second eccentric member such as a cylindrical eccentric member 18 rotatably fixed or integrally formed. While one eccentric crankshaft is shown, a number of eccentric members can be provided along the axial length of the crankshaft 14 to cooperate with additional connections not shown.

The copper eccentric bushing 20 surrounds the crankshaft eccentric member 18 in an annular shape. 2A, 2B and 3 better illustrate the shape of these components, and the crackshaft body 16 is shown in hatched form. In normal press operation, when the crankshaft 14 rotates, the eccentric bushing 20 is press fit around the circumference of the crankshaft eccentric member at 22 sufficient to deliver the required torque to achieve a stamping or forming operation. The crankshaft eccentric member 18 is fixed to the crankshaft eccentric member 18 (ie, rotate together).

Oil is supplied between the connecting portion 10 and the eccentric bushing 20 to smooth the rotation. For example, oil may flow into the radial play 26, 의 between 0.003 inches and 0.005 inches from the top of the connection or from the top of the connection in conduit 24 to provide an oil film on which the eccentric bushing 20 rotates. do. FIG. 4A illustrates how 125 psi (pound per square inch) of oil can be delivered to the radially spread play 26 through hose 25 and conduit 24 to smooth connection motion. . At this operating point, the conduits in Fig. 4A, indicated by dashed lines inside the crankshaft 14 and the eccentric member 18, are not used in a way that affects the stroke adjustment described below. As the crankshaft 14 and the eccentric bushing 20 which rotates with the crankshaft 14 rotate with respect to the connection part 10, the connection part 10 moves up and down and affects the reciprocation motion of the slide 119. FIG.

When a change or adjustment is required in the stroke of the slide 119, the rotation of the crankshaft 14 and thereby the movement of the slide are stopped, and the oil supply through the conduit 24 at the top of the connection portion 10 is stopped. . The high pressure oil is then supplied to the inner diameter of the eccentric bushing 20 via a crankshaft 24 such as axial bores 28 and one or more longitudinal bores 29. The high pressure oil is, but is not limited to, a pressure between 7,000 psi and 10,000 psi and is distributed around the circumference of the crankshaft eccentric member 18. Seals 100, 102 may be provided along the axial end of the inner diameter of bushing 20, to prevent leakage of high pressure oil. The high pressure oil is intended to reduce the pressure fit between the crankshaft eccentric member 18 and the eccentric bushing by expanding the eccentric bushing 20 annularly. The high pressure oil creates a slight radial play between the eccentric bushing 18 and the crankshaft eccentric member 18, denoted 31, which surrounds the periphery between the eccentric bushing 20 and the connection 10. Creates a temporary pressure fit or a forced fit. The lubricated radial play 31 (see FIG. 4B) allows the crankshaft 14 to rotate relative to the eccentric bushing 20, which does not rotate due to a temporary pressure fit with the connection 10. As the crankshaft 14 rotates, the crankshaft body 16 is displaced to another position with respect to the eccentric bushing 20, which effectively changes the stroke length of the connecting portion 10 to the desired length. When the adjustment is complete, the high pressure oil at 31 supplied through the crankshaft 14 is stopped, and due to the elasticity of the metal structure, the crankshaft eccentric which causes the rotation of the crankshaft to reciprocate the connection to continue the stamping operation. (With the pressure fitting thereof with the second eccentric member 18, the eccentric bushing 20 is returned.

2A and 2B show how a 180 ° rotation of the crankshaft 14 with the eccentric bushing 20 achieves a 2.5 inch stroke length. Naturally, other stroke lengths are possible within the scope of the present invention.

5 shows another embodiment of the present invention, which illustrates a stamping operation. In this embodiment, an additional connecting bushing 11 is located between the connecting portion 10 and the bushing 20, and the connecting bushing 11 fits inside the circumferential groove provided radially outside of the eccentric bushing 20. Oil may flow into the radial play 26 to form an oil film that facilitates free rotation of the crankshaft and its eccentric bushings relative to the connecting portion 10 and the bushing 11 associated therewith. In this embodiment, the seal 35 prevents leakage of high pressure oil between the crankshaft eccentric member 18 and the eccentric bushing 20. During stroke adjustment, the high pressure oil is supplied through a plurality of longitudinal bores 29 and transported by axial bores 28. Axial perforations 28 extend through the crankshaft to respective connections along the axial length of the crankshaft.

To prevent the eccentric bushing 20 from changing into a "egg shape" and unbalanced stress development when the eccentric bushing 20 is expanded to alleviate pressure fit with the crankshaft eccentric member 18 as described above. In order to help, various eccentric bushing shapes can be introduced.

For example, FIG. 6A is an axial cross-sectional view of the eccentric bushing 20, in which the eccentric protrusion 40 is an internal cavity in fluid communication with an inner opening 43 of the eccentric bushing receiving the crankshaft eccentric member 18. (41). When high pressure oil flows around the crankshaft eccentric member circumference, the high pressure oil provides radially outward pressure (shown by arrow 42), which is also inside the protrusion cavity 41 as shown. Works on FIG. 6B is a transverse cross-sectional view of an embodiment conceptually similar to FIG. 6A, where the outer protrusions have an I beam shape with a central rib 45. The pressure generated by the high pressure oil is indicated at 42. Fig. 6C shows a side view of the eccentric bushing of Fig. 6B, wherein the eccentric protrusion includes a rib 45 having a groove cut out from the axial end of the eccentric bushing. Fig. 6d shows an axial lateral cross section of another embodiment, wherein the eccentric protrusion 47 of the eccentric bushing 20 is hollow.

Figure 7 shows another aspect of the present invention, which allows a traditional rotating union to be used for introducing high pressure oil used for the expansion of the eccentric bushing, as corresponds to a special high pressure rotating union. Most of the embodiments shown in FIG. 7 are conceptually similar to the above-described embodiments. The cylindrical crankshaft eccentric member 52 is enclosed at 55 with an eccentric bushing 54 which is integral with the crankshaft main body 50 and is pressure-fitted with the eccentric member 52. The connecting bushing 56 surrounds the eccentric bushing 54 and is provided with a slight radial play at 60. The connecting bushing 56 is press fit inside the opening provided between the connecting upper part 63 and the connecting lower part 62, which is attached to the press slide.

The perforation 65 extends axially through the crankshaft body 50 and the longitudinal perforation 67 branching therefrom extends through the crankshaft eccentric member 52. Axial drilling 65 extends to the left of FIG. 7 towards the other connection. The high pressure oil used to inflate the eccentric bushing 54 does not require oil to flow into the crankshaft through the rotating union at this high pressure, so as to have a ratio of 10: 1 (or other). An apparatus is provided. Inside the end of the axial perforation 65 is an increasing rod or reciprocating part 69, which is sealed by a seal 70 located in the inner groove of the crankshaft. Optionally, the seal can be mounted to the reciprocating portion 69. The reciprocating portion 69 ends in the piston 72 sealed to the outer circumference. For example, oil at a pressure of about 1,000 psi flows from 74 into the rotary union 76 and into the fluid chamber 78, where the oil acts on the piston 72 to move the reciprocating section 69 to the left. . During the reciprocating motion, air passes through the hole 79.

Since the reciprocating portion 69 has a frictional force equal to one tenth of the cross sectional area of the piston 72 or other cross sectional area, the oil in the axial perforations 65 and the longitudinal perforations 67 is already generated by the piston movement. Rise to a pressure of 10,000 psi. The piston and the reciprocating part are designed to have sufficient stroke so that enough oil can be conveyed to complete expansion of the eccentric bushings of all connections. When the high pressure oil inside the longitudinal perforations 67 proceeds to the inner diameter cavity of the eccentric bushing 54 in order to expand the bushing radially, the seal 81 causes the oil to escape or leak from the closure system. To prevent them.

Fig. 8 is a partial axial cross sectional view showing another method of sealing the high pressure oil used to inflate the eccentric bushing. In this embodiment, the seal 84 with an o-ring face mounted to the eccentric bushing 86 acts with the radially aligned walls of the rib 88 protruding from the crankshaft 90. Alternatively, the seal can be provided to the rib 88 to prevent leakage of oil. Other seal shapes can also be introduced within the scope of the present invention.

The present invention includes two seals 100, 102, Figs. 1 and 10 made of a friction member having a high coefficient of friction, and when the pressure is kept constant, the eccentric bushing 20 and the second eccentric member ( The seals 18 create a restraining force or restraint mechanism such that they can be fixed to each other until a pressure fit or a force fit is made in the gap 26 located between the connecting portion 10 and the eccentric bushing 20. .

When the crankshaft 14 rotates, clutch torque is generated between the eccentric member 18 and the eccentric bushing 20 to overcome the high frictional force of the above features. This feature allows multiple eccentric members to be displaced at the same time at the same time, without additional mechanical teeth, sprockets or other mechanisms to ensure proper timing or displacement therebetween. Such a sealing device, having a high coefficient of friction, further reduces parts and simplifies the shape. No other mechanical parts are required to fix the position of the plurality of eccentric members with respect to each other, so that after the press stroke change is completed, the slides remain parallel.

An additional feature of the invention is that the same adjustable stroke connection can be used between the crankshaft and the balancing device, so that the balance of the press can be maintained. Therefore, the form of the connection that can be used with the present invention can be a normal linking arm or other link of the press part, such as a motion balancer, or the like.

Although the adjustable stroke of the present invention uses a single oil passage through the crankshaft, the first passage actuates the adjustable stroke connecting mechanism of the present invention in relation to the slides, and the second passage provides a stroke adjusting device suitable for the parallel arrangement. It would be possible to have two different oil passages coming from the opposing sides, actuated.

One form of the seal that can be usefully used in the present invention is a U-shaped seal. This type of seal is actuated by the action of internal hydraulics to disperse the ribs of the seal. This movement creates a stopping force between the eccentric member and the journal which allows for a fixed force to be developed. It can be seen that the U cups or U-shaped seals perform better than other types of seals used to date. Fig. 10 shows typical U-shaped seals 100 and 102 while pressure is applied between two eccentric members. The holding force increases with pressure. Therefore, the restraining force can be easily manipulated at any torque required by the device.

Although the present invention has been described by the preferred embodiment, other modifications are possible within the spirit and scope of the present invention. This application is therefore intended to cover all variations, uses or applications which employ the general principles of the invention. Furthermore, the present application is intended to include all matters conceivable from those known and commonly used in the art to which this invention pertains and that are defined within the scope of the appended claims.

Claims (15)

Press connecting member 10; An eccentric bushing 20 disposed inside the press connecting member; A second eccentric member 18 disposed inside the eccentric bushing 20, wherein the second eccentric member 18 is connectable to the eccentric bushing 20 so as to be released; A rotatable crankshaft (14) connected to said second eccentric member (18); And connecting the eccentric bushing 20 to the press connecting member 10 so as to prevent rotation between the eccentric bushing 20 and the press connecting member 10. And a means for adjusting the press stroke by rotating the eccentric member (18) so that the crankshaft (14) can rotate when it is operated. The method of claim 1, wherein the connecting means has a fluid pressure applied to the contact surface between the second eccentric member 18 and the eccentric bushing 20, the pressure being the second eccentric member 18 and the eccentric. Machine press, characterized in that for enabling relative rotation between bushings (20). The method of claim 1, wherein the connecting means is applied to the contact surface between the second eccentric member 18 and the eccentric bushing 20, so that the eccentric bushing 20 and the pressure connecting portion 10 is temporarily pressure Mechanical press characterized by having a fluid pressure to be connected together by a custom connection (33). 4. Press as claimed in claim 3, characterized in that the means operate through the crankshaft (14). 4. The high frictional force seal of claim 3, further comprising one or more high frictional seals disposed between the second eccentric member (18) and the eccentric bushing (20). Machine press, characterized in that to prevent the rotation of the eccentric bushing (20) relative to the second eccentric member (18) before the creation of (33). 6. A mechanical press as set forth in claim 5 wherein said high pressure seal comprises a U-shaped seal. Machine press as claimed in claim 1, characterized in that the means operate through the crankshaft (14). The machine press as claimed in claim 1, wherein the eccentric bushing (18) comprises an internal cavity (41) in communication with the second eccentric member (18). The machine press as claimed in claim 1, wherein the eccentric bushing (20) comprises a beam rib having an I-shaped cross section. Press connecting member 10; An eccentric bushing 20 disposed inside the press connecting member 10; A second eccentric member 18 disposed inside the eccentric bushing 20, wherein the second eccentric member 18 may be connected to the eccentric bushing 20 so as to be released; A rotatable crankshaft (14) connected to said second eccentric member (18); In order to prevent rotation between the eccentric bushing 20 and the press connecting member 10, the eccentric bushing 20 is connected to the press connecting subsidiary 10 so that the second inside of the eccentric bushing 20 is formed. As fluid pressure means for rotating the eccentric member 18, the fluid pressure means is adapted to move the crankshaft passages 65 and 67 into the crankshaft 14 in communication with the fluid pressure intensifying means for increasing the fluid pressure. And a fluid pressure means including a fluid passageway (65, 67) therethrough. 11. The mechanical press as set forth in claim 10, wherein said fluid pressure intensifying means comprises a movable piston (72) for increasing fluid pressure in said crankshaft passage (65, 67). The method of claim 10, wherein the fluid pressure increasing means is applied to the contact surface between the second eccentric member (18) and the eccentric bushing (20), so that between the second eccentric member (18) and the eccentric bushing (20). And a fluid pressure to allow relative rotation of the machine press. 11. The method of claim 10, wherein the fluid pressure means is applied to the contact surface between the second eccentric member 18 and the eccentric bushing 20, so that the eccentric member 18 and the eccentric bushing 22 are temporarily pressurized. Mechanical press characterized by having a fluid pressure to be brought into contact by a custom connection (33). 14. The seal of claim 13 further comprising one or more high frictional seals disposed between the second eccentric member 18 and the eccentric bushings 20, such that the high frictional seals comprise the temporary pressure fit connection. Machine press, characterized in that to prevent the rotation of the eccentric bushing (20) relative to the second eccentric member (18) before the creation of (33). 15. The mechanical press as recited in claim 14, wherein the high frictional seal includes a U-shaped seal.