Title of Invention

SWING CLAMP APPARATUS WITH SPRING BIASED CAM ASSEMBLY

Abstract

An improved shiftable clamp (12) adapted for connection to a fixture (10) is provided wherein the clamp (12) is selectively operable to engage and hold a workpiece (14) to the fixture (10). The clamp (12) includes a tubular body (22) and a piston (24) telescopically received within the body (22). Movement of the piston (24) is guided and controlled by means of a cam assembly (26) including a cam track (64) formed in the piston (24) and an associated cam track follower ball (66) mounted on the body (22). A spring unit (74) is also provided on the body (22) and includes a spring (82, 96) serving to self-center and bias the ball (66) into the track (64). This insures that the ball (66) smoothly rotates during movement of piston (22) and reduces wear and premature clamp failure.

Full Text

SWING CLAMP APPARATUS WITH SPRING BIASED CAM ASSEMBLY BACXOIOUKD OF THE INVENTION Field of the Invention The present inratikaiis nroafiy concsmed with improved clamps used for clamping workpieces to fixtures, and especially so-called swing clamps which simultaneously move in axial and rotational directions to allow easy placement and removal of workpieces. More particularly, the invention is concerned with such clamps including a shiftable piston equipped with a workpiece-engaging outer head, where piston movement is guided and controlled via an internal cam assembly made up of a specially configured cam track and cam follower ball arrangement. Such cam assemblies are provided with spring units serving to bias and self-center the follower balls into the associated tracks, providing many operational advantages including increased damp speeds sxi reduction in clamp wear and damage. Description of thePrks: in HjroanGc rrhwiwm- are commonly used in manufacturing operations to hold and clamp workpieces to stationary fixtures, so that the workpieces may be machined or otherwise worked upon. Typical hydraulic damps include a cylinder body adapted for attachment to a fixture and a piston telescopically received within the cylinder body for movement between an retracted, clamping position and an extended, release position. A clamping head is attached to the distal end. of the piston for holding and clamping workpieces to the fixture when the piston is in its retracted, clamping position. Commonly, several such clamps aie mounted to a single fixture so that a workpiece may be securely held at several locations while it is being worked upon. Swing clamps are hydraulic clamps that include swinging mechanisms serving to swing the clamping heads away from the workpiece when the pistons are extended to their release positions. Swing clamps make it easier to load and unload workpieces from fixtures, especially in confined spaces. One type of swinging mechanism used in swing clamps is a cam assembly having a curved cam track or groove formed in either the piston or the cylinder body and a corresponding cam follows frag attached to the other of the piston and cylinder body. The follower ball moves along fee carved cam track when the piston is shifted which serves to rotate the piston and clampioc JK9S2S /*^°'r'p(y* Conventional cam assemblies in swing clamps are subject to premature wear over time that interferes with the swinging oper&km of the clamps. Specifically, when the cam follower ball moves in Hie trads^ itksHbiecXK) canamSaEB&al forces tending to push the ball to the sides of the groove. Over time, f&e can bail -w-ars down Ae edges of the track and creates dimples along the length thereof. The dimples and worn regions of the cam track often catch the ball during piston movement, creating a "choppy" clamp operation. When a clamp is used in severe conditions, its cam ball may completely wear down the edges of the track, causing the ball to completely roll out of the groove. Excessive wear on the cam grooves of a clamp can be a serious problem. In many clamping operations, it is important for the clamping head to swing to a precise location away from the workpiece, and then return to the same exact starting position when the clamp is shifted to its clamping position- Whsi the cam groove on a clamp become worn, the swing clamp can no longer achieve this precse and rspeatable swinging movement. Thus, the entire swing clamp must.be iraixsL e^ea -&***** the remaining parts of the clamp are m good condition. U.S. Pavaff. NG. 5.?Tf.T18 describes a decided improvement in the swing clamp art. In this patent, .lases may of a special cam track design which inhibits the cam follower ball from prematurely wearing the cam track edges. Specifically, the cam track described in the' 118 patent includes a central arcuate region and a pair of substantially planar side faces extending tangentially from the central arcuate region. This construction forces the cam follower ball to be more centrally seated within the cam track without pushing up against the edges of the cam track. SUMMARY OF THE INVENTION The present invention is directed to further improvements in shiftable clamps, and particularly the swing clamps described above. Broadly speaking, the clamps of the invention include a hollow body for attachment to a fixture, with the body presenting an interior wall. A piston is telescopicaHy received within the body for movement between clamping and released positions. A cam assembly is used for guiding and controlling relative movement between the piston and body, wife the cam assembly having a cam track formed in one of the interior wall of the body an&iieaKterwall of the piston, and a cam follower received within the cam track and attached to theofteroftbe interior wall of the body and the outer wall of the piston. The specific improvement of the invention involves the use of a spring for biasing the ball toward the cam tract It has been discavraed TTiaf use of such a spring affords a number of operational advantages, including improved rirttnj.wtg ^seeds and reduced wear. In preferred forms, nse biasa% sprisg ihm»i part of a spring unit having a follower-engaging component wi& a spring remote fern die follower, thereby biasing the follower through the component. The spring may be of any desired construction, for example a bellville spring or a small coil spring. In the usual case, the cam follower is a ball and the spring unit is mounted within a recess on the clamp body; the component has an arcuate face in direct engagement with the ball, whereas the spring is within the recess. BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is an isometric view of a fixture equipped with a plurality of clamps in accordance with, the iyivaujnw^ sbown with the clamps engaging and clamping a workpiece to the fixture; Fig- 2 k a vexiical secdooal view of a preferred clamp of the invention; Fig. 3 is a fragmentary sectional view taken along line 3-3 of Fig, 2 and illustrating the construction of a bellville spring assembly used for biasing the cam follower ball into the cam groove of the piston: Fig. 4 is a sectional view similar to that of Fig, 3, but depicting the use of a coil spring assembly; and Fig. 5 is a sectional view similar to that of Fig. 3, but illustrating the use of a removable sleeve forming a part of the overall clamp body. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT Turning now to the drawings, Fig. 1 illustrates a fixture 10 equipped with a plurality of clamps 12 adapted to releasably hold a workpiece 14 in position on the fixture 10. As illustrated, the exemplary fixture 10 includes a base 16 supporting an upright mounting box 18, the latter having a workpiece-supporting wall 20. The clamps 12 are threadably secured within threaded bores provided in wall 20 as will be described. Briefly, in operation the claxnps 20 are selectively movable between fee clamping position depicted in Fig. 1 to thus hold workpiece 14 in place, and a retxacasL smtng-away position allowing removal of the workpiece 14 after it is worked upon, and positioning of another workpiece 14 in its place. In more detail, the body 22 has an **nTTggfr*3 segment 30 presenting an inner wall 32 as well as a threaded exterior wall 34. Each, damp 12 includes an elongated, tubular body 22 together with a piston 24 tftfcsi ■; \m J3J\ its ti fz&wjfhm the body 22, and a cam assembly broadly referred to by the numeral 26 xbr gni Pis6m24 fryfrfffes ibsse 54 sqnipped with a sealing ring 56 engaging surface 32, a guide section 58 pr^s^Mting a& IXHTT surface 59 and extending upwardly from base 54, and a rod 60 extending beyond portion 40. A relatively large translation spring 62 is seated within plug 38 and engages the underside of base 54 as shown. As illustrated in Fig. 2, the section 58 has a slightly reduced diameter as compared with base 54 but has'a greater diameter than rod 60. The assembly 26 includes a plurality (here three, two of which are shown) of circumferentially spaced apart cam tracks 64a, 64b ... formed in the outer surface-59 of piston section 58. The preferred tracks 64 are configured for guiding the piston along different paths during piston movement. For example, the track 64a is configured so as to cause piston 24 (and thereby head 28) to swing during retraction and extension of the piston, whereas track 64b is essentially rectilinear so that the piston 22 merely reciprocates without any swinging movement. In addition, the assembly 26 includes a cam follower ball 66 which is secured to body segment 30 adjacent inner surface 32; the ball 66 is seated within one of the tracks 64 as will be readily apparent from a consideration of Figs. 2 and 3. One possible geometry of the cam tracks 64 and the follower ball 66 is described in detail in the referenced U.S. Patent No. 5,820,118, incorporated herein by reference. Briefly however, the cam foikrws^isis a ottfer peripheral surface presenting a radius of curvature R, whereas the cam trade inclades z cexriral arcuate region 68 having a radius of curvature R' substantially equal to the radius R. Moreover, the track 64 has a pair of opposed, substantially planar side face 70, 72 extending from arcaais regkai 68, wi& the side faces 70, 72 each having a proximal end converging into the region S5 aad si nppcssd fetal ead that diverges from the region 68, with the distal ends also diverging -rrer oae aawV; In other embodiments, the cam track has a geometry which matches thai oftbs cam JbHower. Specifically, the cam track has essentially the same radius of curvature as the corresponding cam follower. The preferred assembly 26 also has a spring unit 74 seated within the recess 33 which biases the ball 68 toward and into the adjacent track 64. Referring to Fig. 3, the unit 74 includes a force-transmitting annular component 76 having an arcuate face 78 engaging ball 66? and an opposite, substantially planar face 80. In the depicted embodiment, a bellville spring 82 is disposed between the inner surface of recess 33 and face 80, and thereby biases ball 68. Fig. 4 illustrates a scKaewhatioodified embodiment wherein a resilient elastomeric plug 84 is used to house a spring issr 86, In flris case a through-bore 88 is provided in the segment 30 and is cogrSgnrsd K) iscagggping 84. The latter includes an annular wall 90 defining a recess 92. The unit S6is skmlar£> nmt 74 in that itincfaflfls acomponent 94 identical with component 76. However, m tins case a coil spring 96 is seated within recess 92 and engages the planar face of component 94. Fig. 5 illustrates a still further embodiment of the invention wherein the body 22a is formed using an outer tubular wall 98 together with an inner, replaceable sleeve 100 the latter being equipped with a recess 33a. The recess 33a houses the identical spring unit 74 described with reference to Fig. 3. Use of a replaceable sleeve 100 permits ready repair of a clamp 12 in the field. Each clamp 28 is in the form of an elongated element 101 presenting a workpiece-engaging underside 102. A screw 104 is employed to attach each element 101 to the outer end of each rod 60. After the clamps 12 are installed on wall 20 of fixture 10 by threading the segments 30 thereof into the pre-drilled holes in wall 20, the clamps may be used for holding workpieces 14 in place. Turning to Fig. 2, it will be seen that the spring 62 of each clamp 12 serves to bias the corresponding piston 22 to its extended position where, in the illustrated embodiment, the head 28 is swung LaeuiBy to a clearing position allowing removal and replacement of a workpiece 14 onto the fixture. When this is done, the individual clanips are actuated by application of hydraulic fluid through the ports 50, whereupon the pressurized fluid passes downwardly between the walls 32, 59 and engages base 54, thereby moving the piston downwardly against the bias of spring 62. During such movement of the pistons, the heads 28 are swung laterally owing to the configuration of cam tracks 64a and follower balls 66 until the heads come into proper holding relationship with the workpiece 14. After operations on workpiece. 14 are completed, the pressurized hydraulic fluid is relieved, thereby permitting the springs 62 to return the individual pistons 22 and clamps 28 to their extended and swung-away positions. The provision of spring units in accordance with the invention provides a number of significant operational advantages. First, the spring units insure that the biased cam follower balls 66 self-center in the associated tracks 64a. Thus, the balls 66 are constrained in both vertical and horizontal planes, providing a stationary point for the cam tracks 64a for proper guidance through both axial and rotary motion. In essence, the components 76 act as bearing races allowing the balls 66 to rotate as the pistons move through their strokes, while at the same time biasing the balls 66 so that they remain fully engaged in the tracks 64a. This construction reduces the static and dynamic frictional forces generated between the balls 66 and the track 64a, especially during starting movement of the pistons, allowing smoother tracking and essentially eliminating the tendency of the balls to drag within the tracks, rather than to rotate. The spring units give an even load distribution and, owing to the self-centering action of the spring units, the balls 66 are inhibited from riding up on the edge of the tracks. At the same time, the design allows a degree of ball float within the tracks to compensate for manufacturing and operational variations. It has been found that cam damage during inadvertent arm contact, a frequent problem in the art, is reduced with the present invention. Consequently, higher clamp speeds are possible as compared with current designs, while at the same time eliminating the wear a£d operational problems commonly encountered with conventional clamps. Although not shown in detail, it will be appreciated that the clamps of the invention may assume a variety of different configurations. For example, while in the illustrated embodiment the hydraulic clamp is single acting, making use of the translation spring 62, the invention is not so limited. Thus, it is well within the skill of the art to employ a double acting hydraulic design wherein pressurized hydraulic fluid is used to move the piston 22 in both directions. Additionally, while a rotatable cam follower ball is preferred, other follower designs could be employed. I Claim: 1. In a damp fir damping a workpiece to a fixture, said clamp having an elongated, hollow body Jbr *IM*W**# ID the fixture aid presenting an interior wall, a piston presenting an outer wall an&iacscaacsEy received wifein said body for movement between a:. clamping position for clainpfflg said "worfcpisce to the fixture and a release position, and a cam assembly for guiding relative movement between said piston and said body, the cam assembly including a cam track formed in one of said interior wall of the body and said outer wall of the piston, and a cam follower received within said cam track and attached to the other of said interior wall of the body and said outer wall of the piston, the improvement comprising a spring biasing said cam follower toward said cam track. 2. The damp of claim L there being a force-transmitting component engaging said follower- ssad soring engaging sxiA component 3. Tbgrirgnp of claim 2, said componentpresenting an arcuate face engaging said follower and an opposed spring-engaging face. 4. The clamp of claim 1, said follower comprising a ball. 5. The clamp of claim 1, said cam track comprising a groove formed in said piston outer wall. 6. The clamp of claim 1, the cam assembly including aplurality of differently configured, spaced apart cam tracks formed in said piston outer wall, said cam follower being positionable in any one of the cam tracks for guiding said relative movement in respective directions corresponding to the configuration of the one cam track. 7. The clamp of claim 1, further including a clamping head operably coupled with said piston wr engaging and clamping the workpiece to the fixture when the piston is in said clamping postine tijereof. 8. Theclamp of claim l,saidcamfoUowerhavinganouterperipheral surface presenting a HK*™g nf ra-in/ajiff*, fng ramTrarirtnrhirfTpa^ /»j*ptpi1 flrr.natfirPigirm having a radius of curvature substantially equal to lie radios of cnrvafczre of said cam follower, and a pair of opposed, substantially planar stffrikgy scEacBrsSamthe central arcuate region, said side faces each having a proximal end that converges into said central arcuate region and an opposite distal end that diverges from the central arcuate region, the distal ends diverging away from one another. 9. The clamp of claim 1, said body including an outer wall and an inner sleeve operably coupled with the outer wall, said sleeve presenting said body inner wall. 10- The dasnp of claim 1, said spring comprising a coil spring. 11. The dssap of claim L, said spring comprising a bellville spring. 12. The damp of claim 1, including an resilient elastomeric plug operatively maintaining the position of said spring. 13. The clamp of claim 1, including hydraulic fluid passageways formed in said body permitting application of pressurized hydraulic fluid within said body in order to effect movement of said piston relative to said body. * - *■-■ *" 14. Theclamp of claim 13, said piston being a single acting piston, there being a translation spring operably coupled with said piston.

Documents:

3387-CHENP-2006 AMENDED PAGES OF SPECIFICATION 05-01-2012.pdf

3387-CHENP-2006 AMENDED CLAIMS 05-01-2012.pdf

3387-CHENP-2006 CORRESPONDENCE OTHERS 16-08-2011.pdf

3387-CHENP-2006 FORM-3 05-01-2012.pdf

3387-CHENP-2006 OTHER PATENT DOCUMENT 05-01-2012.pdf

3387-CHENP-2006 CORRESPONDENCE OTHERS.pdf

3387-CHENP-2006 CORRESPONDENCE PO.pdf

3387-CHENP-2006 EXAMINATION REPORT REPLY RECEIVED 05-01-2012.pdf

3387-CHENP-2006 FORM-18.pdf

3387-CHENP-2006 POWER OF ATTORNEY 05-01-2012.pdf

3387-chenp-2006-abstract.pdf

3387-chenp-2006-assignement.pdf

3387-chenp-2006-claims.pdf

3387-chenp-2006-correspondnece-others.pdf

3387-chenp-2006-description(complete).pdf

3387-chenp-2006-drawings.pdf

3387-chenp-2006-form 1.pdf

3387-chenp-2006-form 3.pdf

3387-chenp-2006-form 5.pdf

3387-chenp-2006-pct.pdf