Patent Application
20060049560
This invention concerns springs and more particularly mechanical compression springs as are used to provide a return force such as in cam operated dies.
In cam operated tooling installed on dies in forming presses, a slide is operated by the press motion to drive a tool used to form a feature on a part.
One or more return springs are compressed as the tool is advanced by a camming action produced by the slide. When the press platens are moved apart, the compressed spring or springs act to retract the slide.
In metal forming, it sometimes takes considerable force to withdraw a piercing tool from the part, such that a high return spring force is required at the start of the return motion. At the same time, a substantial slide travel is required. Very stiff coil springs have limited available travel for a given space due to the thick cross section required to develop a high spring rate.
This required combination of long travel and high peak forces has led to the development and use of “nitrogen” springs in which compressed nitrogen is sealed in a chamber, and further compressed by a piston having a projecting rod subjected to a load, creating a fluid spring.
Nitrogen springs are capable of generating considerable forces while allowing substantial travel, and are widely used as return springs in die cam units.
However, nitrogen springs have several disadvantages, including their initial high cost and their need to be serviced regularly, and the fact that high cycle rates are not possible due to excessive heat build up.
These nitrogen springs must be precharged with nitrogen under high pressure so as to have an initial high spring rate.
This initial high spring rate creates a high shock force when the cam unit is impacted by the cam driver since there is a relatively high initial resistance to cam movement caused by the precharging of the nitrogen spring.
These disadvantages of nitrogen springs led to the development of a variable force spring assembly described in U.S. Pat. No. 5,390,903, assigned to the same assignee as the present application.
The design disclosed in U.S. Pat. No. 5,390,903 houses springs of different stiffness in telescoped casings which are arranged to successively compress the springs, which are nested together, allowing a large range of movement with low forces developed initially and very high forces developed at the end of the stroke. A stack of Belleville springs is used as the high rate spring.
The inclusion of machined casings and other components makes that device relatively high in cost to manufacture, and is not easily adapted to varying applications since the casings and other components must be reengineered for each application. Also, the Belleville springs used are not well suited for high cycling rates, as fatigue failure commonly occurs when Belleville springs are subjected to such service.
For this reason, there has heretofore not been any mechanical spring arrangement available which has become commercially successful as a replacement for nitrogen springs.
It is the object of the present invention to provide a mechanical spring combination having a large travel, with an initial low spring rate during an initial range of compression and developing a high spring force through second shorter range of compression of the spring combination.
The above recited object and other objects which will become apparent upon a reading of the following specification and claims are achieved by combining two springs in an end-to-end in series relationship, each spring having a substantially different spring rate.
A plunger is slidable within the lower rate spring as the lower rate spring is compressed by a flange on the upper end of the plunger. The plunger in turn is slidable on a pin projecting from the other end of the combination spring through the higher rate spring and into the plunger. The pin has a first flange affixed thereto abutting the lower end of the high rate spring and an intermediate flange above the higher rate spring is held against the other end of the higher rate spring by being seated on a shoulder on the pin.
The plunger moves into abutment with the second flange held against the upper end of the higher rate spring after a predetermined length of travel, and thereafter begins to compress only the higher rate spring for the remainder of its stroke.
The higher spring rate spring is normally preloaded by the second flange to a degree such that it is not deflected by the pressure exerted by the lower rate spring and is not further compressed, until the plunger engages the intermediate flange. Alternatively, the higher rate spring may be preloaded to a lesser extent such as to be allowed to be deflected at the same time as the lower rate spring after the precompression level of the higher spring rate is reached when a composite spring rate is affected until abutment of the plunger against the intermediate flange occurs, and the only higher rate spring compressed thereafter.
In a second embodiment, separate spring assemblies each having a plunger, connecting pin, and precompression flanges are connected together end-to-end as by a press fit coupling pin mated with bores in adjacent flanges. This allows different combinations of various springs to be readily provided to suit different applications.
In the following detailed description, certain specific terminology will be employed for the sake of clarity and a particular embodiment described in accordance with the requirements of 35 USC 112, but it is to be understood that the same is not intended to be limiting and should not be so construed inasmuch as the invention is capable of taking many forms and variations within the scope of the appended claims.
Referring to the drawings, and particularly
Each spring 12, 14 is held compressed between respective end flanges 16, 18 and a common intermediate flange 20.
End flange 16 is held to the common intermediate flange 20 by a stepped diameter pin 22 having a head 24 slidable within a plunger 26 connected to the associated end flange 16.
The plunger 26 has an opening in its lower end slidably fit to a larger diameter section 28 of the pin 22, allowing the plunger 26 to slide down when the flange 16 is advanced to compress the lower rate spring 12 until moving into abutment with the upper surface of the intermediate flange 20.
The smallest diameter section 30 of the pin 22 extends through a hole in the intermediate flange 20 with a slidable fit, allowing the flange 20 to move down when compressing the higher rate spring 14.
The smallest diameter pin section 30 extends within the higher spring rate 14 to the end flange 18, to which it is affixed as by a plug weld. This prevents the intermediate flange 20 from moving away, which allows a precompression of the higher rate spring 14. The end flange 18 has a pilot plug 32 extending up into the lower end of the higher rate spring 14.
The combination spring 10 is mounted in an installation so that the two end flanges 16, 18 are able to be compressed together.
Different rate springs can be readily substituted into the combination to enable different spring requirements to be engineered at very low cost, and different end fittings easily provided as required for a given application.
In the first stage of compression, the lower rate spring 14 is compressed against the intermediate flange 20, held in position by the precompression of the higher spring rate spring 14. When the lower end of the plunger 26 contacts the intermediate flange 20, as seen in
The plunger 26 pushes the intermediate flange 20 off the shoulder on the stepped diameter pin 22 as seen in
A plot 34 of a conventional nitrogen spring is also shown for comparison.
In
If the precompression of the high rate spring 14 is set to be less than in the above example such that the force in the lower rate spring 12 exceeds the higher rate spring force at some point during the compression of the lower rate spring 12, deflection of the higher rate spring will begin at point X as seen in
Thus, lesser composite spring rate exists from point X to point Y depicted as segment 36B. Abutment of the plunger 26 occurs at point Y.
Thereafter, the higher spring rate of the spring 14 alone controls, depicted by segment 36C.
The combination spring 10 can be easily redesigned for other applications, by merely changing the dimensions of the relatively simple hardware items, i.e., the plunger 26, the pin 22A, and substituting different springs 12A, 14A as in the combination spring 10A shown in
A different plunger travel distance X, can also easily be set. A slight clearance to eliminate any precompression of the lower rate spring 12 may be provided, if desired.
Different end features can be included, as the pilot end feature 32 shown in
Such a pilot feature 32 can be provided at one end and a tubular extension 34 at the other end in the combination spring 10B shown in
The body 44 moves relative the driver 42 as the press is operated closing the space 45.
A return stripping force is created by a combination spring 10C installed in a pocket 50 formed in the tooling body 44 extending in the direction of relative movement between the driver 42 and body 44 so that this relative motion will compress the combination spring 10C.
The combination spring 10C includes a boss 52 integral with the intermediate flange 20C extending within the high rate spring 14C, and a boss 54 integral with the end flange 18 also extending within the high rate spring 14C.
The combination spring 10C is largely confined and supported within the bore 50. The protruding portion of the low rate spring 12C is internally supported by the plunger 26C, to eliminate any tendency to buckle.
A removable plug 56 is threaded into the lower end of the bore 50 and together with a snap ring 58, resists the force exerted when the combination spring 10C is fully compressed.
Other arrangements for providing a removable closure for the bore 50 are described in copending application U.S. Ser. No. ______, filed on ______, Attorney Docket No. DNY-117.
Referring to
In this arrangement, each assembly 60A, 60B holds a respective compression coil spring 62A, 62B between a pair of end flanges 64A, 66A and 64B, 66B.
Each flange 64A, 64B, 66A, 66B has an integral boss 68A, 70A, 68B, 70B projecting into the associated spring 62A or 62B.
A headed pin 72A, 72B is received in a bore in each boss 68A, 68B, 70A, 70B, the head portion 74A, 74B slidable in the outboard boss 70A, 70B. The stem portion 76A, 76B is plug welded in the opposite boss 70A, 68B. This captures the springs 62A, 62B between the associated pairs of flanges 64A, 66A and 64B, 66B.
Thus, the outside, away flanges 64A, 64B are free to collapse to compress the springs 62A, 62B respectively to the distance allowed by the spacing A, B.
Each spring assembly 60A, 60B is readily connectable by a coupling pin 76 press fit into counterbores 78A, 78B in adjacent flanges 66A, 64B.
Thus, various spring assemblies can be inventoried and combined in any combination suited to a particular application.
Optional pilots 80A, 80B can be press fitted in the bases of the opposite flanges 64A and 66B.
Urethane or other compression springs can be substantial for the coil springs shown, although the coil springs are preferred.
