Web or sheet-fed apparatus having high-speed positioning mechanism

BACKGROUND OF THE INVENTION

Field of the Invention

The present invention is generally concerned with an improved high speed web or sheet processing apparatus which is designed for extremely high registration and operation on material segments fed one after the other to the apparatus. In particular, the invention extends to such devices and corresponding methods, which are operable to first grip or hold a supplied material segment, after which the gripped segment for the purpose of precise alignment substantially simultaneously along orthogonal axes within the plane of the segment and perpendicularly about an axis of rotation is shifted to the segment level. The invention is particularly suitable for high speed, precise die cutting operations.

Description of the prior art

In the past, three-axis punch presses have been proposed for processing continuous webs. Such a press is in the<de-docref DNUM="4555968" CY="US">U.S. Patent No. 4,555,968</de-docref> disclosed. The press of this patent has a slidable and carried on an air cushion stamp unit, and the stamp unit is moved laterally to the direction of travel of the web and rotatable about an axis perpendicular to the web to the stamp unit in a precise positional alignment with the defined areas of the web bring that should be punched by the press. For an automatic mode of operation in the<de-docref DNUM="4555968" CY="US">U.S. Patent No. 4,555,968</de-docref> The press described is provided by a control system which has two groups of photo-optical sensors arranged to detect the presence of two T-shaped marks which are provided on opposite sides of the web adjacent to each defined area to be cut. The control system is electrically coupled to a servo motor to adjustably position the stamp unit, as soon as the forward movement of the web is interrupted, in a defined area on the web, generally in the vicinity of the working structure of the stamp unit.

Like in that <de-docref DNUM="4697485" CY="US">U.S. Patent No. 4,697,485</de-docref> a punch press is provided with a registration system that is operable to provide precise alignment of a slidable die cutting unit along two axes during the time that the web material is being advanced along a third axis with respect to the die unit so that As soon as a defined area of ​​the web reaches the stamp unit, the press can be operated immediately in order to subject the material to the punching operation. Continuous monitoring of an elongated indicator strip provided on the material allows the stamp unit to be displaced as required during web travel to ensure lateral and angular registration prior to the point at which advancement of the web is interrupted.

The <de-docref DNUM="5212647" CY="US">U.S. Patent No. 5,212,647</de-docref> describes a punch press that is provided with a registration system that quickly and precisely defines areas of a web with a movable stamp unit without requiring the use of elaborate or continuous markings or more than two detection devices for determining the location of the markings relative to the stamp unit . The registration system of patent no. 5 212 647 applies a pair of reference characters attached to a press chuck to indicate the position at which the characters appear on the web when the defined areas of the web are in a desired predetermined relationship relative to those held on the chuck Are stamp unit.

The <de-docref DNUM="5644979" CY="US">U.S. Patent No. 5,644,979</de-docref> describes an improved punch press, wherein the entire stamp unit is held on an air cushion with a lower plate and a displaceable upper stamp arrangement. When a defined area of ​​the web is first fed to the die-cutting station during operation, the target area is gripped by a vacuum hold-down device and the entire stamp unit is simultaneously adjusted along three axes, so as to ensure precise alignment between the target area on the web and the To achieve punching arrangement.

Although the accuracy provided by such prior art registration systems for punching devices is very good, such presses are relatively slow. For example, in the case of that in the<de-docref DNUM="5644979" CY="US">U.S. Patent No. 5,644,979</de-docref> described the need to move the relatively heavy and bulky stamp assembly to slow down the operation thereof. The earlier stamp presses are generally able to operate at speeds no faster than about 20 cycles / minute.

The <de-docref DNUM="4817477" CY="US">U.S. Patent No. 4,817,477</de-docref> shows the positioning of a pad with the help of three stepper motors, which are coupled to associated eccentric cams via belt drives. Translatory displacement paths and their geometrical alignment with one another are in the device according to the<de-docref DNUM="4817477" CY="US">U.S. Patent No. 4,817,477</de-docref> not provided.

The <de-docref KI="C2" DNUM="4337902" CY="DE">DE 43 37 902 C2</de-docref> describes a punch for web material with two plates arranged one above the other. One of the plates is displaceable transversely to the direction of movement of the web material to be processed, while the other plate can be rotated about a vertical axis. This device only allows alignment in two degrees of freedom.

Accordingly, there is a need in the art for an improved web or sheet fed sheet processing device, such as a punch press, which avoids the problems of previous units of this type and results in operation and registration at very high speed.

SUMMARY OF THE INVENTION

The invention is defined in claims 1 to 7. The following statements serve to explain the invention and its environment.

The present invention overcomes the problems outlined above and provides an apparatus and method for processing sequentially fed segments (ie areas of a continuous belt or discrete sheets / sheets) so that operations such as die cutting can be performed quickly and accurately. Generally speaking, the apparatus according to the invention comprises a work station, a device for initially feeding a segment of material into the station and a positioning device for precisely positioning the segment in the station after the initial feeding and before processing in the station. The positioning device includes a segment gripping or holding device for holding the initially supplied segment, a device for determining the position of the held segment within the station compared to a desired position thereof, and a moving device, which is coupled to the segment holding device, for moving the latter and the segment held by it to move the segment to the desired position. Generally speaking, the material segments carry at least one and preferably a pair of position-identifying markings, and the positioning device includes a reference arrangement which provides reference data corresponding to the desired position for the segment marks, together with a device for comparing the location of the segment marks with the reference data.

In another aspect of the invention, an apparatus and method for processing individual segments of a continuous, flexible web are provided, with accurate adjustment of the position of successively fed web segments by initially holding each successive segment and subjecting the held segment to an adjustment movement becomes, while the segment remains part of a continuous path. This adjustment movement is selected from the group consisting of a movement along one or two orthogonal axes in the plane of the segment and a rotary movement of the segment about an axis transverse to the segment plane and combinations of the aforementioned movements. It will be appreciated that the invention provides such a triaxial movement of individually held web segments while the respective segments remain part of the continuous web.

In preferred forms, the web gripping or holding device of the invention has a relatively lightweight vacuum hold-down plate within the web or sheet / sheet processing station. In the case of a punch press, the vacuum hold-down plate is in the form of a body provided with a central opening which surrounds a substantially stationary punch anvil for the floating die; the vacuum plate is, if necessary, in an axial direction (ie in the direction of web travel), a lateral direction (transverse to the axial direction) and / or rotatable about an axis of rotation perpendicular to the axial and lateral directions and to a plane containing the segments. As used herein, "die cutting" broadly refers to various activities, including (but not limited to) embossing, cutting, stamping, punching, roughing, and other similar activities.

The preferred mover is directly coupled to the vacuum plate and includes a number of spaced motors such as bidirectional stepper motors, each of which can transmit motion while the vacuum hold-down plate is moving. In order to achieve the most precise and fastest plate movement, the motors are coupled to the plate via eccentrics, so that actuation of the motors drives and moves the plate as required. In the most preferred form, the movement device has three such eccentrically coupled stepper motors, the axes of the plate-connecting shafts lying on a single, common straight line.

The preferred positioning device also utilizes a pair of charge coupled device (CCD) cameras mounted within the processing station along with a pair of split prisms and fixed reference characters carried by the stamp assembly. In operation, when a material segment is fed to the processing station, each camera receives a combined image consisting of both an image of the fixed mark and one of the reference numbers carried by the material segment. This image data is then used to calculate a positional error and movement distance information, which in turn is used in the operation of the respective stepper motors, so as to move the vacuum plate and the material segment held by it for precise positioning of the segments.

The device of the invention is similar to that in Figs <de-docref DNUM="4555968" CY="US">U.S. Patent No. 4,555,968</de-docref>, <de-docref DNUM="4697485" CY="US">4 697 485</de-docref>, <de-docref DNUM="5212647" CY="US">5 212 647</de-docref> and <de-docref DNUM="5644979" CY="US">5 644 979</de-docref> described, all of which are referred to here.

BRIEF DESCRIPTION OF THE DRAWINGS

<figref idref="S40">1</figref> Figure 3 is a side view of the preferred web fed die cutter according to the invention;

<figref idref="S41">2</figref> is a top view of the in <figref idref="S40">1</figref> shown apparatus and shows in detail the feed assembly and the slidable web stop adjustment plate thereof;

<figref idref="S42">3</figref> FIG. 12 is a vertical sectional view, with portions broken away for clarity, illustrating the input end of the punch station, which is a portion of that shown in FIGS <figref idref="S40">1</figref> to <figref idref="S41">2</figref> shown device forms;

<figref idref="S43">4</figref> Figure 4 is a partial view, with parts broken away for clarity, of the slidable segment support vacuum plate assembly of the invention;

<figref idref="S43">5</figref> is a sectional view taken along line 5-5 <figref idref="S43">4</figref> and also shows the construction of the slidable plate and anvil assembly;

<figref idref="S43">6</figref> Fig. 6 is a sectional view taken along line 6-6 <figref idref="S43">4</figref>illustrating the internal construction of the plate and anvil assembly;

<figref idref="S44">7</figref> Fig. 14 is a partial view showing the input end of the plate and anvil assembly with the stamp assembly illustrated in dashed lines;

<figref idref="S44">8</figref> Figure 8 is a sectional view taken along line 8-8 <figref idref="S43">4</figref>illustrating the side plate parts of the slidable plate and the anvil assembly below;

<figref idref="S44">9</figref> Fig. 3 is an enlarged partial vertical section illustrating one of the eccentric drive motor units coupled to the slidable segment support plate;

<figref idref="S45">10</figref> Fig. 4 is a schematic view of the die cutting station illustrating the orientation of the CCD cameras and associated prisms used to detect the path segment position;

<figref idref="S45">11</figref> Fig. 11 is a schematic block diagram illustrating the connection between the computer control of the punch device and the detection cameras and the stepper motor drive units;

<figref idref="S46">12</figref> Fig. 3 is an exploded perspective view of the components of a second embodiment of the invention constructed for sheet or sheet feed mode;

<figref idref="S47">13</figref> Figure 12 is a top view of the device of <figref idref="S46">12</figref>, parts broken away for clarity;

<figref idref="S47">14</figref> Fig. 12 is a vertical sectional view of the device of Figs <figref idref="S46">12</figref>–<figref idref="S47">13</figref>;

<figref idref="S48">15</figref> Figure 12 is a partial side view in partial vertical section of the panel / sheet powered device <figref idref="S46">12</figref>;

<figref idref="S48">16</figref> is a top view of the drive unit with three motors that make up part of the panel / sheet-fed device <figref idref="S46">12</figref> forms;

<figref idref="S49">17A</figref> and <figref idref="S50">17B</figref> Together are a flow diagram of the preferred control software that is used in the web fed device <figref idref="S40">1</figref> is used to precisely position successive path segments within the die-cutting station;

<figref idref="S45">18</figref> Figure 3 is a schematic top view of the XY-θ table and interconnected X1, X2 and Y axis drive units of the invention;

<figref idref="S45">19</figref> Figure 14 is a schematic illustration of certain geometric relationships of the X1, X2 and Y drive units used in developing the preferred control algorithm of the invention;

<figref idref="S45">20</figref> Figure 3 is a schematic representation of certain additional geometric relationships used in the development of the control algorithm; and

<figref idref="S40">21</figref> Fig. 3 is a partial top view of a continuous path illustrating respective path segments along their length, along with position-indicating reference references for each such segment.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

In the drawings, and in particular in <figref idref="S40">1</figref>, is a punch <b>30</b> illustrated. Generally speaking, the device contains<b>30</b> a punch press or station <b>32</b>made with a stamp unit <b>34</b> is equipped, a material feed arrangement <b>36</b> for sequentially feeding stock to the station <b>32</b> for sequential punching of segments <b>38</b> from that (<figref idref="S40">21</figref>) and a segment positioning device <b>40</b> adjacent to the stamp unit for precise positioning of each respective segment <b>38</b> relative to the stamp unit.

The order <b>30</b> is set up for use in editing elongated ribbons, the successive segments <b>38</b> with punching areas <b>42</b> have as a target and printed markings such as reference numerals <b>44</b> wear (<figref idref="S40">21</figref>), the latter being in predetermined positions relative to the corresponding target areas. An example of a material in the arrangement<b>30</b> can be processed is a flexible synthetic resin tape. Punching such material as part of the production of many devices can be very critical and extremely tight punch tolerances are required. Hence the arrangement<b>30</b> designed for high speed, but with very precise punching of the successive segments <b>38</b>. Viewed in more detail, the station contains<b>32</b> One Base <b>46</b>which is a central, upright, generally rectangular plate <b>48</b> and a spacer <b>50</b> wearing. On the plate<b>48</b> are four upright rods <b>52</b> held and support an upper frame member adjacent their upper ends <b>54</b>. A piston plate<b>56</b> is below the frame element <b>54</b> from the bars <b>52</b> carried back and forth with the help of a piston <b>58</b> vertically movable. Above the frame element<b>54</b> is a micrometer unit <b>60</b> mounted and allows a selective adjustment of the amount of vertical displacement of the piston plate <b>56</b>, and between the element <b>54</b> and the plate <b>56</b> becomes a sensor mechanism <b>62</b> such as a glass scale held up for feedback to a controller with respect to the vertical position of the plate <b>56</b> to care.

As best with the <figref idref="S42">3</figref> and <figref idref="S43">6</figref> can be seen, shows the stamp unit <b>34</b> one on the spacer <b>50</b> held upholstery <b>64</b> with a central piston pocket recess <b>66</b> therein, as well as a relatively wide, longitudinally extending slot <b>68</b>. On the upholstery<b>64</b> between the upstanding sidewalls of the slot <b>68</b> an anvil arrangement <b>70</b> held. The anvil arrangement<b>70</b> contains a lower piston <b>72</b>which is set up in the recess <b>66</b> to fit (<figref idref="S43">6</figref>), as well as an upper anvil block <b>74</b>; The piston<b>72</b> is about screws <b>74b</b> on the block <b>74</b> attached. The block<b>74</b> provides a flat upper anvil surface <b>76</b> and a pair of relatively narrow, elongated, elongated slots <b>74a</b> across the surface <b>76</b> ready. The block<b>74</b> is also with four transverse openings <b>75</b> provided therethrough, which are set up for receiving electrical heating elements. The piston<b>72</b> is with a peripheral seal <b>78</b> provided, and in the recess <b>66</b> a supply of balancing medium or material is provided; The piston<b>72</b> and thus the anvil assembly <b>70</b> is therefore supported elastically. A pair of alignment blocks<b>80</b> is on the cushion <b>64</b> on each side of the slot <b>68</b> and engages opposite side wall surfaces of the block <b>74</b> on.

The stamp unit <b>34</b> also includes an upper support plate <b>82</b>that are below the plate <b>56</b> is arranged. The plate<b>82</b> holds a central punch arrangement <b>84</b>that are above the anvil surface <b>76</b> is arranged, and a pair of positioning CCD cameras <b>86</b>, <b>88</b> and other structures associated with the positioning device as described later. The order<b>84</b> contains a stamp unit <b>89</b>that occur at every work cycle of the stamp arrangement <b>84</b> the anvil arrangement below <b>70</b> touched.

A total of four telescopic guide units <b>90</b> are between the plate <b>82</b> and the upholstery <b>64</b> and are operatively coupled to guide the upward and downward movement of the plate <b>82</b> and thus the stamp unit <b>84</b> to support. Such a spring-loaded cylinder<b>92</b> is adjacent to each unit <b>90</b> and is so biased to normally unity <b>84</b> above the anvil surface <b>76</b> to keep.

As best with the <figref idref="S40">1</figref> and <figref idref="S41">2</figref> is seen the upstream end or input end of the assembly <b>36</b> on a sliding carriage <b>94</b> for movement thereof in a direction transverse to the path of travel of the web material through the station <b>32</b> held. In this way, each of two webs to be described later can be processed relative to the stamping unit<b>34</b> be positioned. The order<b>36</b> generally includes a pair of feed rollers arranged side by side <b>96</b>, <b>98</b>that have a first and a second lane <b>100</b>, <b>102</b> hold on stock material, with engines <b>104</b>, <b>106</b> serve the roles <b>96</b>, <b>98</b> to drive. The whole arrangement<b>36</b> also has vacuum clamping arrangements <b>108</b>, <b>110</b> and guide roller sets <b>112</b>, <b>114</b> to guide the lanes through the station <b>32</b>. As will be appreciated by those skilled in the art, the feed rolls<b>96</b>, <b>98</b> of the associated engines <b>104</b>, <b>106</b> driven to the tracks <b>100</b>, <b>102</b> unwind so that stock material for punching through the station <b>32</b> can be performed. The vacuum clamping arrangements<b>108</b>, <b>110</b> maintain a predetermined tension on the tracks as they are being fed, whereas the guide roller sets <b>112</b>, <b>114</b> the trains in the station <b>32</b> to lead; these components are set up so that they have a slight adjustment movement of the web segments within the station<b>32</b> allow as described later.

The order <b>36</b> also ensures that the remnants of the punched sheets are picked up <b>100</b>, <b>102</b> after processing it in the station <b>32</b> and contains a sliding carriage for this purpose <b>115</b>, the home drive roller sets <b>116</b>, <b>118</b> and recording foils <b>120</b>, <b>122</b> holds, the latter of engines <b>124</b>, <b>126</b> are driven. A stepper motor<b>28</b> is for driving each set of drive rollers <b>116</b>, <b>118</b> provided and functions as a coarse feeder for rapidly advancing either the web <b>100</b> or the train <b>102</b> along a movement path to successively defined segments <b>38</b> to the station <b>32</b> to and into the station <b>32</b> to lead into it.

A pair of air cylinders <b>130</b>, <b>132</b> is provided to the sled <b>94</b> or the sledge <b>115</b> between a first position in which the web <b>100</b> with the station <b>32</b> and the stamp unit <b>34</b> is aligned, and a second position in which the web <b>102</b> is similarly oriented to move. Through the plate<b>48</b> extends in a direction parallel to the path of travel of the webs <b>100</b>, <b>102</b> a pair of rotatable shafts <b>134</b>, each wave <b>134</b> a pair of opposite axial ends that extend across the plate <b>48</b> extend beyond, provides. At each end of the waves<b>134</b> is a pinion <b>136</b> attached so that rotation of each pinion on each shaft is transmitted to the other pinion on the opposite side of the base plate. At the bottom of each sled<b>94</b>, <b>115</b> a rack is engaged with the proximal sprockets <b>138</b>, <b>140</b> held so that each slide when the cylinder is actuated <b>130</b>, <b>132</b> moved in alignment with the other.

The positioning device <b>40</b> is adjacent to the anvil block <b>74</b> and is in a surrounding relationship with the surface <b>76</b>. The device<b>40</b> generally has a vacuum plate member <b>142</b> as well as a movement arrangement <b>144</b> on being operable with the item <b>142</b> is coupled. The purpose of the device<b>40</b> is for fine and precise adjustment of the position of each segment <b>31</b> inside the station <b>32</b> to worry so that the target area <b>42</b> of which is punched exactly.

The vacuum plate <b>142</b> contains an upper plate <b>146</b>that have a central, essentially square opening <b>148</b> provides that is set up the central area of ​​the block <b>74</b> record and thus the surface <b>76</b> to expose. The plate<b>142</b> contains a front area <b>150</b>with a series of vacuum openings <b>152</b> is provided therein, together with a spaced, opposite rear area <b>154</b>, the vacuum openings through it in a similar way <b>156</b> Has. The areas<b>150</b>, <b>154</b> are by side margin parts <b>158</b>, <b>160</b> connected to each other, each with vacuum openings <b>162</b>, <b>164</b> are provided.

The total plate <b>142</b> also has a lower plate member <b>166</b> on that similarly an opening <b>168</b> in that which has to the opening <b>148</b> is aligned; the bottom plate<b>166</b> is on the top plate <b>146</b> by fasteners <b>147</b> attached. As best in<figref idref="S43">6</figref> can be seen between the plates <b>146</b> and <b>166</b> elongated inner channels <b>170</b>, <b>172</b> intended. Individual vacuum line couplings<b>174</b>, <b>176</b> are operational with the lower plate <b>166</b>, with the corresponding channels <b>170</b>, <b>172</b> in communication, for connection to a selectively operable vacuum system (not shown). These channels are connected to the vacuum openings via suitable internal passageways<b>152</b>, <b>156</b>, <b>162</b> and <b>164</b>. On again<figref idref="S43">6</figref> it can be seen that the aligned openings <b>148</b>, <b>168</b> in the top and bottom panels <b>146</b>, <b>166</b> are dimensioned so that they are slightly larger than the neighboring block <b>74</b>; the importance of this feature is hereafter clarified.

By including the side margin parts <b>158</b>, <b>160</b> in the corresponding anvil block slots <b>74a</b> (please refer <figref idref="S44">8</figref>) becomes the vacuum plate <b>142</b> held for a limited simultaneous axial, lateral and rotating movement thereof. It can be seen that the slots<b>74a</b> are dimensioned somewhat wider than the assigned side edge parts <b>158</b>, <b>160</b>in order to limit the movement of the vacuum plate <b>142</b> to record.

The movement arrangement <b>144</b> has three stepper motor units <b>178</b>, <b>180</b>, <b>182</b> on, each at the front end of the vacuum plate <b>142</b> are attached (see <figref idref="S43">4</figref>). On the units<b>178</b> to <b>182</b> is referred to as the X1, Y and X2 units, respectively. Each of the units<b>178</b> to <b>182</b> contains an electrically operated bidirectional stepper motor <b>184</b>with an encoder <b>186</b> is equipped and a rotatable output shaft <b>188</b> Has. In addition, each motor has a sled<b>190</b>, <b>192</b> or. <b>194</b> with a central opening at the top of each stepper motor <b>184</b> is attached. Based on<figref idref="S44">7</figref> and <figref idref="S44">9</figref> it can be seen that the sled <b>192</b> is an elongated integral block member provided with a central opening and generally T-shaped side surfaces <b>196</b>, <b>198</b> with the longitudinal axis of the block in a perpendicular transverse relationship relative to the longitudinal web direction through the station <b>32</b> is oriented. Hanging end edge yoke bearings<b>199</b> become adjacent to the outer ends of the sled <b>192</b> held. In addition, the sled<b>192</b> an upper surface <b>200</b> with a central opening. Similarly, the sledges<b>190</b> and <b>194</b> spaced, somewhat T-shaped side surfaces and corresponding top surfaces <b>202</b> and <b>204</b>; these slides also have end yoke bearings<b>201</b> (please refer <figref idref="S43">5</figref>). In the case of the sledge<b>190</b> and <b>194</b> however, their longitudinal axes are transverse to the surfaces <b>196</b>, <b>198</b> oriented, ie they are aligned with the longitudinal direction of the web through the station <b>32</b>.

The units <b>178</b> to <b>182</b> are below the vacuum plate <b>142</b> for a limited translational movement thereof during the movement of the plate <b>142</b> held. More specifically, the units are<b>178</b> to <b>182</b> on a transverse, somewhat L-shaped mounting rail <b>206</b> mounted, the three laterally spaced unit-receiving openings <b>208</b>, <b>210</b> and <b>212</b> each has the stepper motor <b>144</b> every unit <b>178</b>, <b>180</b> or. <b>182</b> record, tape. The top surface of the rail<b>206</b> adjacent to each of the openings <b>208</b> to <b>212</b> is provided with a pair of spaced rails or guide units for each associated unit. That is, unit tours<b>214</b>, <b>216</b> are over the opening <b>208</b> and are transverse to the longitudinal direction through the station <b>32</b> oriented; Unity tours<b>218</b>, <b>220</b> are adjacent to the opening <b>210</b> are provided and are oriented in alignment with the longitudinal direction; and unit tours<b>222</b>, <b>224</b> are adjacent to the opening <b>112</b> parallel to the guides <b>214</b>, <b>216</b> intended. The yoke bearings<b>201</b> form part of the sled <b>190</b> and <b>194</b> and take the unit tours <b>214</b>, <b>216</b> or. <b>222</b>, <b>224</b> on. The yoke bearings are similar<b>199</b>that are part of the sled <b>192</b> form the unity leadership <b>218</b>, <b>220</b> on. In this way, each of the units<b>178</b> to <b>182</b> to a limited extent within the assigned rail openings <b>208</b> to <b>212</b> slidable.

The units <b>178</b> to <b>182</b> are by means of identical respective eccentric coupling arrangements <b>226</b>, <b>228</b>, <b>230</b> with the vacuum plate <b>142</b> coupled. These arrangements each contain a fixed pin connector<b>232</b>on the vacuum plate <b>142</b> above each underlying unit <b>178</b> to <b>182</b> is attached. Each such connector contains a hanger pin<b>234</b>how best in <figref idref="S44">9</figref> you can see. A connection between the individual stepper motor output shafts<b>188</b> and the associated pins <b>234</b> is done by providing eccentric blocks <b>236</b> manufactured as best in <figref idref="S44">9</figref> is shown. The center-to-center distance between the pins<b>234</b> and <b>188</b> for each unit <b>178</b> to <b>182</b> defines the crank arm length for this unit.

The overall positioning device <b>40</b> also includes the aforementioned CCD cameras <b>86</b>, <b>88</b>that on mounts <b>242</b>, <b>244</b> are held by the plate <b>82</b> hanging down (<figref idref="S45">10</figref>). The cameras<b>86</b>, <b>88</b> are with assigned prisms <b>246</b>, <b>248</b> provided on the stamp unit <b>34</b> are mounted, the latter also fixed position marks <b>250</b>, <b>252</b> having. Each marker preferably contains<b>250</b>, <b>252</b> a closed line that forms a square, with the open area of ​​the square the size of one of the fiducial marks <b>44</b> on every segment <b>38</b> corresponds. For example, if solid, circular reference numbers are printed on the web, the reference marks would<b>250</b>, <b>252</b> have a square with an inner surface that is equal in width and height to the diameter of the circular reference numerals. Between each fiducial mark<b>250</b>, <b>252</b> and the desired location of the corresponding marker <b>44</b> extends a clear line of sight with an associated slit prism <b>246</b> or <b>248</b> along the line of sight. The images projected along the line of sight from above and below the slit prism are both laterally reflected as a single composite image in which both the reference mark and the reference mark are visible on the web. The cameras<b>86</b>, <b>88</b> are thus vertical with an associated slit prism <b>246</b>, <b>248</b> aligned so that each camera receives the composite image reflected from the prism. For example, each CCD camera can be provided with a two-dimensional arrangement of 512 × 489 pixels and outputs analog signals representative of the image. These signals are converted into digital signals by a conventional analog-digital converter device. Lenses, which form part of each CCD camera, are also provided for focusing the camera on the corresponding slit prism. Preferably, the lenses focus the assembly on an area of ​​about 1/6 square inch to the desired resolution for aligning the stamp unit and the target area<b>42</b> every segment <b>38</b> to get within about 2/10 000 of an inch.

As schematically in <figref idref="S45">11</figref> is part of the device <b>40</b> a computer control <b>254</b> provided, which typically has a central processing unit, an input device, display means and a memory for storing data and suitable software. As shown, the cameras are<b>86</b>, <b>88</b> coupled with the controller, which also connects to the stepper motor units <b>178</b> to <b>182</b> Has. In addition, the control<b>254</b> with the roller motors <b>104</b>, <b>106</b> and <b>124</b>, <b>126</b>, the clamping units <b>108</b>, <b>110</b>, <b>116</b> and <b>118</b> and stepper motors <b>128</b> to control the lanes <b>100</b>, <b>102</b> connected. Generally speaking, once a given segment<b>38</b> by appropriate actuation of the feed assembly <b>36</b> to move the web <b>100</b> or <b>102</b> initially and roughly within the station by a predetermined axial distance <b>32</b> positioned, it will be with the plate <b>142</b> connected vacuum system operated to the segment <b>38</b> firmly on the plate <b>142</b> to grab. The appropriate downstream take-up reel motor<b>124</b> or <b>126</b> and the associated drive roller sets <b>116</b>, <b>118</b> are then reversed to the web <b>100</b> or <b>102</b> easy to loosen downstream of the station, reducing the web tension. This feature leaves together with the settings of the upstream web tension units<b>108</b>, <b>110</b>, which allow for a slight path movement, a path segment adjustment along the orthogonal X and Y axes and a path rotation movement without fear of the path splitting or tearing.

The cameras <b>86</b>, <b>88</b> are next operated to generate image data. The control<b>254</b> receives such image data from the cameras <b>86</b>, <b>88</b> and compares the relative positions of the reference marks <b>250</b>, <b>252</b> and the markings <b>44</b> for the segment <b>38</b> and generates appropriate error data showing the difference between the current X, Y and θ positions of the marks <b>44</b> and their desired positions as from the reference marks <b>250</b>, <b>252</b> represented, represent. The position of the plate<b>142</b> is also about the encoders <b>186</b> each stepper motor <b>184</b> known. The difference data is then used by the controller in the manner to be described to the units<b>178</b> to <b>182</b> selectively drive to the position of the vacuum plate <b>142</b> and thus the segment <b>38</b> change until the markings <b>44</b> are aligned with the assigned reference markings (within preselected tolerances). The setting of the segment<b>38</b> takes place, of course, while the segment remains part of the web, the latter taking up the required slight amount of adjustment due to the loosening of the web described. At this point, the punching can be started in the usual way, by the upper stamp-bearing area of ​​the stamp unit<b>34</b> in cutting contact with the segment <b>38</b> is lowered. After such a cutting process, the arrangement<b>36</b> pressed to the next segment <b>38</b> to the station <b>32</b> to move where the process is repeated.

The control <b>254</b> also applies the calculated difference between the current axial or longitudinal distance between the reference numerals <b>44</b> and the markings <b>250</b>, <b>252</b> to the feed assembly <b>36</b> to control. That is, after each segment feed operation, the axial distance of the web feed for the next actuation of the assembly<b>36</b> varies in order to compensate for the determined axial distance error. In this way, the initial web feed is controlled to prevent inaccuracies in the initial feed step from accumulating to a point where successive segments<b>38</b> could no longer be brought into a sufficiently close alignment, so that the cameras <b>86</b>, <b>88</b> at the same time can view an image that has the fixed markings <b>250</b>, <b>252</b> and the reference numerals <b>44</b> contains. The control<b>254</b> thus controls the operation of the motors of the drive arrangement <b>36</b> in response to the axial difference data calculated during the previous work sequence.

To better understand the process and algorithm with which the vacuum plate <b>142</b> is set to accurately align each segment <b>38</b> In the station <b>32</b> will ensure on the <figref idref="S45">18</figref> and <figref idref="S45">19</figref> referenced, which is a schematic representation of one for the vacuum plate <b>142</b> representative XY-θ table or a schematic representation that shows the movements of the respective drive units <b>178</b> to <b>182</b> shows. In these figures, the symbols have the following definitions:<ul><li>X1 = drive unit <b>178</b>;</li><li>Y = drive unit <b>180</b>;</li><li>X2 = drive unit <b>182</b>;</li><li>T = distance between reference numerals;</li><li>C._x1 = radial eccentric length or crank length of drive unit X1 (drive unit <b>178</b>);</li><li>C._y = radial eccentric length or crank length of the drive unit Y (drive unit <b>180</b>);</li><li>C._x2 = radial eccentric length or crank length of drive unit X2 (drive unit <b>182</b>);</li><li>α = angle between the Y axis and the drive unit X1 crank length;</li><li>γ = angle between the X axis and the drive unit Y crank length;</li><li>β = angle between the Y axis and the drive unit X2 crank length; and</li><li>M = length between the axes of the plate pins <b>234</b>.</li></ul>

As can be seen from these figures, the XY-θ table (ie the vacuum plate <b>142</b>) about the three pens <b>234</b> by radial eccentric lengths or crank arms C_x1, C_y and C_x2 attached, which are driven by the corresponding stepper motors. Units X1 and X2 slide along the Y axis, while unit Y slides along the orthogonal X axis. The central axes of all the pins<b>234</b> lie on a common straight line, the three pins preferably being equally spaced. The units X1 and X2 have the same crank length, but the crank length C_y can be different.

There are two types of movement associated with each crank: <br />an active rotation of the motor shafts <b>188</b>by the effective crank arms of the eccentric <b>236</b> the vacuum plate <b>142</b> move, and passive translation (sliding) of the individual drive units to accommodate such a plate movement. A translation of the table or the plate<b>142</b> To reach along the X axis, the crank arms associated with units X1 and X2 rotate in opposite directions (one clockwise, the other counterclockwise, or vice versa) while the Y unit slides up or down. Rotation of the table (about an axis transverse to the plane of the segment) is accomplished by rotating both the X1 and X2 crank arms in the same direction (clockwise to rotate the table counterclockwise or counterclockwise to rotate the table clockwise) without any movement of the Y unit. The translation of the table or the plate<b>142</b> along the Y axis is achieved by rotating the Y crank arm, with the X1 and X2 units both sliding left or right together. Whenever the X1 or X2 crank arms turn away from the Y axis, the X1 or X2 drive units slide inwards; Whenever the X1 or X2 crank arms turn on the Y axis, the X1 or X2 drive units slide outwards. When the Y crank arm turns away from the Y axis, the Y unit slides up; when the Y crank arm turns towards the X axis, the Y unit slides down. Because the system is non-linear, for the same amount of translation or rotation of the table, the amount of each crank arm movement is different at different crank angles. For the same reason, for a single translation along the X-axis or for a table rotation, the rotary movements of the X1 and X2 crank arms do not necessarily have the same amount, but depend on the crank angles.

Especially with reference to <figref idref="S45">19</figref> it can be seen that the following applies at any given time: <de-math align="left">2Msinθ = C_x(sinα + sinβ)<fdist />(1)</de-math><de-math align="left">Y = C_ysinγ<fdist />(2)</de-math><ul><li>1. For a pure T rotary movement (swiveling on the central pin) with (+) Δθ <de-math align="left">C._x(sinα₂ - sinα₁) = M (sinθ₂ - sinθ₁)</de-math>therefore<de-figure num="1"><img file="DE19882275B4_D0001.tif" /></de-figure></li></ul>

From (1) we have <de-figure num="2"><img file="DE19882275B4_D0002.tif" /></de-figure>and <de-figure num="1"><img file="DE19882275B4_D0003.tif" /></de-figure>whereupon given Δθ and using (3) and (4) <de-figure num="2"><img file="DE19882275B4_D0004.tif" /></de-figure>Similar, <de-figure num="3"><img file="DE19882275B4_D0005.tif" /></de-figure><ul><li>2nd For a pure X translation with (+) Δx, from (1) <de-math align="left">sinα₁ + sinβ₁ = sinα₂ + sinβ₂<fdist />(7)</de-math><de-math align="left">C._xsinα₂ = C_xsinα₁ + Δx</de-math><de-figure num="4"><img file="DE19882275B4_D0006.tif" /></de-figure>and <de-figure num="5"><img file="DE19882275B4_D0007.tif" /></de-figure>Similar, <de-figure num="1"><img file="DE19882275B4_D0008.tif" /></de-figure>and <de-figure num="2"><img file="DE19882275B4_D0009.tif" /></de-figure>(8) can also be replaced by sinβ₂ in (7) with that of in (10).</li><li>3rd For a pure Y translation with (+) Δy we have from (2) <de-figure num="3"><img file="DE19882275B4_D0010.tif" /></de-figure></li><li>4th Compound movement</li></ul>

From (1), (2), (9), (11) and (12) it can be seen that a Y movement is independent of an XT movement; therefore only an XT movement is discussed below.

The initial position is α₀, β₀, the desired translation Δx and rotation Δθ, the resulting position α₂, β₂.

Although it is a non-linear system, a simultaneous 3-axis movement can be obtained if the following is introduced: <ul><li>a. First Δx, arrived at α₁, θ₁, then Δθ, results from (5) and (8) <de-figure num="4"><img file="DE19882275B4_D0011.tif" /></de-figure></li></ul>

After (3) or (4) (14) can be written as <de-math align="left">f (α₂) = f_x(α₀, β₀, Δx) + f₀(α₀, β₀, Δθ) + const<fdist />(15)</de-math>here <de-figure num="5"><img file="DE19882275B4_D0012.tif" /></de-figure><de-figure num="1"><img file="DE19882275B4_D0013.tif" /></de-figure><de-math align="left">Const = sinα₀<fdist />(19)</de-math><ul><li>b. First Δθ, arrived at α₁, θ₁, then Δx, results from (8) and (5) <de-figure num="2"><img file="DE19882275B4_D0014.tif" /></de-figure>(14), (15) and (20) shows the independence of the movement sequence.</li></ul>

From (3), (4) and (18) follows <de-figure num="3"><img file="DE19882275B4_D0015.tif" /></de-figure>

The following equations of motion are derived: <de-math align="left">α₂ = sin^–1(f_x + f_θ + sinα₀)<fdist />(21)</de-math><de-math align="left">β₂ = sin^–1(–F_x + f_θ + sinβ₀)<fdist />(22)</de-math><de-math align="left">γ₂ = sin^–1(f_y + sinγ₀)<fdist />(23)</de-math> here <de-figure num="1"><img file="DE19882275B4_D0016.tif" /></de-figure>With <de-figure num="2"><img file="DE19882275B4_D0017.tif" /></de-figure><ul><li>5. Determination of ΔX, ΔY and Δθ</li></ul>

The position differences in the camera <b>86</b> and the camera <b>88</b> can be translated into a physical error.

The coordinate system rotation transformation is

<de-figure num="3"><img file="DE19882275B4_D0018.tif" /></de-figure>

So the increment equation can be derived as <de-figure num="4"><img file="DE19882275B4_D0019.tif" /></de-figure> here <de-figure num="5"><img file="DE19882275B4_D0020.tif" /></de-figure><de-figure num="1"><img file="DE19882275B4_D0021.tif" /></de-figure><de-math align="left">α_i = Kx_i· CosΘ<fdist />(31)</de-math><de-math align="left">b_i = Kx_i· SinΘ<fdist />(32)</de-math><de-math align="left">c_i = Ky_i· CosΘ<fdist />(33)</de-math><de-math align="left">d_i = Ky_i· CosΘ<fdist />(34)</de-math>

θ_i is the angle between the camera I coordinate system and the physical table coordinate system.

Kx₁, Kx₂, Ky₁, Ky₂ are the camera movement scaling factors of the X and Y axes of the coordinate system unit of the camera <b>86</b> and the camera <b>88</b> against the coordinate system unit of the table.

To measure the physical error, the average method is used as shown by the following. It is assumed that line 1 and line 1 'should be aligned.

The central point of line l is determined by <de-figure num="2"><img file="DE19882275B4_D0022.tif" /></de-figure>and the central point of line l 'is determined by <de-figure num="3"><img file="DE19882275B4_D0023.tif" /></de-figure>

Hence the shift of the central points between two lines <de-figure num="4"><img file="DE19882275B4_D0024.tif" /></de-figure>

The theta error can be found through <de-figure num="1"><img file="DE19882275B4_D0025.tif" /></de-figure> here, <br />T is the distance between goal 1 and goal 2, <de-math align="left">ΔX₁₂ = ΔX₁ - ΔX₂</de-math><de-math align="left">ΔY₁₂ = ΔY₁ - ΔY₂</de-math><de-math align="left">for Δθ &lt;&lt; 1, ΔX₁₂ &gt;&gt; ΔY₁₂,</de-math><de-figure num="2"><img file="DE19882275B4_D0026.tif" /></de-figure>

Since the target line to be aligned is next to the swivel center, an additional translation error is introduced by the θ correction. The additional X error is eliminated. The additional Y error can be found by referring to<figref idref="S45">20</figref> can be determined, where D = the distance between the Y axis and the reference line T; R = the distance from the origin to the reference number; Δθ = rotational error; and ΔY '= the distance of the Y-axis shift generated by rotation by Δθ.

Consequently, <de-math align="left">ΔY '= ΔθR · sinα = Δθ · D<fdist />(39)</de-math>here D is the distance between the Y axis and the finish line T.

Therefore, the total required Y movement is the sum of (29) and (39).

So we have <de-figure num="3"><img file="DE19882275B4_D0027.tif" /></de-figure>

The resolution and range of motion of the preferred device 40 is determined as follows. The discussion can start on<de-figure num="1"><img file="DE19882275B4_D0028.tif" /></de-figure>be limited because there is symmetry.

The following design parameter values ​​are used for verification.

All of the motor encoders in the preferred embodiment have 4000 pulses / revolution so that an encoder pulse produces Δα = Δβ = Δγ = 0.09 °. M = 3.0 '', C_x = C_y = 0.050 ", T = 5.562", D = 7.09 ". <ul><li>1. resolution</li><li>a. X axis</li></ul>

From (8) we have <de-math align="left">ΔX = C_x(sin (α₁ + Δα) - sinα)</de-math>

Apply and use the first and second derivatives <de-figure num="2"><img file="DE19882275B4_D0029.tif" /></de-figure>

The extreme value is obtained from (43) at <de-figure num="3"><img file="DE19882275B4_D0030.tif" /></de-figure>or <br />α₁ = 90 ° - Δα

From (44) it is indicated that it is a monotonically decreasing function.

Consequently <de-math align="left">Minimum ΔX = C_x(1 - sin (90 ° - Δα))<fdist />(45)</de-math>

The maximum is obtained at <br />α₁ = 0 <de-math align="left">Maximum ΔX = C_xsin (Δα)<fdist />(46)</de-math>

With this construction <de-math align="left">X resolution = 0.05sin (0.09 °) = 0.000078539 ''</de-math><ul><li>b. Y axis<br />Similar, <de-math align="left">Minimum ΔY = C_y(1 - sin (90 ° - Δα))<fdist />(47)</de-math><de-math align="left">Maximum ΔY = C_ysin (Δγ)<fdist />(48)</de-math></li></ul>

With this construction, <de-math align="left">Y resolution = 0.000078539 ''</de-math><ul><li>c. T axis</li></ul>

Off (5)<de-figure num="1"><img file="DE19882275B4_D0031.tif" /></de-figure>

Apply and use the first derivative

<de-figure num="2"><img file="DE19882275B4_D0032.tif" /></de-figure>

With (49), (3) and (4) it can be found that at <br />α₁ = 90 ° - Δα <br />minimum <de-figure num="1"><img file="DE19882275B4_D0033.tif" /></de-figure>Similarly, get the maximum at <br />α₁ = O <br />maximum

<de-figure num="2"><img file="DE19882275B4_D0034.tif" /></de-figure>

With this construction, <de-math align="left">Δθ = sin^–1<chf>(0.005)<chfbr type="bar">3</chfbr></chf>sin (0.09 °)) = 0.0015 °</de-math>

T resolution <de-math align="left">AX_θ = sin (<chf>Δθ<chfbr type="bar">2</chfbr></chf>) T = sin (0.0015 / 2) 5.562 = 0.000072806 ''</de-math><ul><li>2nd Range of motion</li><li>a. X axis</li></ul>

Off (8) <de-math align="left">ΔX = C_x(sin (α₁ + Δα) - sinα₁)</de-math>

For <br />α = -90 ° <br />α₁ + Δα = 90 ° <de-math align="left">X range of motion ΔX = 2C_x<fdist />(52)</de-math>

With this construction, maximum X movement = 0.1 '' <ul><li>b. Y axis<br />Similar, <de-math align="left">Y range of motion ΔY = 2C_y<fdist />(53)</de-math></li></ul>

With this construction, maximum Y movement = 0.1 '' <ul><li>c. θ axis</li></ul>

Off (49) <de-figure num="1"><img file="DE19882275B4_D0035.tif" /></de-figure>

For <br />α = -90 ° <br />β₁ = –90° <br />α₁ + Δα = 90 °

θ range of motion <de-figure num="2"><img file="DE19882275B4_D0036.tif" /></de-figure>

With this construction, maximum θ movement = 0.954973873 ° <de-math align="left">ΔX_θ = sin (<chf>Δθ<chfbr type="bar">2</chfbr></chf>) T = sin (0.955 / 2) 5.562 = 0.04635 ''</de-math>

Next, attention is paid to the <figref idref="S49">17A</figref> and <figref idref="S50">17B</figref> which are a flow diagram of the preferred software incorporating the algorithm described above. This software is in computer control<b>254</b> stored, the latter with the drive unit encoders and the stepper motors as well as with the cameras <b>86</b>, <b>88</b> is connected (see <figref idref="S45">11</figref>).

The first step is segment alignment activity by getting images from the cameras <b>86</b>, <b>88</b> at <b>256</b> started. As previously explained, such images both contain data related to the reference marks<b>250</b>, <b>252</b> as well as the current locations of the reference numerals <b>44</b> on the segment <b>38</b>. These images obtained are then searched (step<b>258</b>) to determine the reference character images therein. A first search (step<b>260</b>) initiates this determination. In the initial subroutine, the data is referenced to the reference marks<b>250</b>, <b>252</b> received (step <b>262</b>), and the current positions of the reference symbols <b>44</b> compared to the location of the reference marks <b>250</b>, <b>252</b> fixed (step <b>264</b>). In the following provisions, due to the fact that the reference marks<b>250</b>, <b>252</b> are fixed on the crotch <b>262</b> to be dispensed with. In the next step<b>266</b> the program determines the differences between the desired and current positions of the reference numerals <b>44</b>. This data is then manipulated to convert the X-axis differences and the Y-axis differences into a physical error as described in the above algorithm (steps<b>268</b>, <b>270</b>). The determination made in these latter steps is then applied to correct the θ error (<b>272</b>), followed by a calculation of an additional Y-axis error caused by the θ correction, step <b>274</b>, please refer <figref idref="S45">20</figref> and the related discussion above.

Next, the program determines whether the X, Y and θ values ​​for the reference numbers <b>44</b> are within the preselected tolerances (step <b>276</b>). If these values ​​are within tolerance, the alignment operation is complete as in step<b>278</b> shown and there is no segment setting <b>38</b> by means of the vacuum plate <b>142</b> required. However, if any of these values ​​are out of tolerance, the program next determines how and to what extent the vacuum plate<b>142</b> must be moved to correct the positional accuracy.

In the first step, the movement parameters are initialized (step <b>280</b>), and the Y-axis error is determined as the sum of the original error plus an additional error caused by rotation (step <b>282</b>). Next, the program determines whether there is any X-axis or θ error (step<b>284</b>). If no such error is determined, the program proceeds to step<b>286</b> and determines if there is any Y axis error. If the answer is no, the program next takes the step<b>288</b> and calculates the required translation component for the Y axis. The final step is to execute the necessary positioning instructions on the stepper motors<b>184</b> the respective drive unit <b>178</b> to <b>182</b> (Step <b>290</b>) and a return to the starting point for the next determination.

On the other hand, if in step <b>284</b> an X-axis and / or θ error is determined, the X1 and X2 crank arm angles are read via the stepper motor encoder (step <b>286a</b>), and X-axis and θ-translation and rotation components are calculated (steps <b>292</b>, <b>294</b>). The program then goes to step<b>286</b> continued as mentioned earlier. If in step<b>286</b> If it is ensured that there is no Y-axis error, the program again proceeds by the steps <b>288</b>, <b>290</b> to execute. However, if such an error is determined, the program calculates the desired crank positions for the X1, X2 and Y drive units (step<b>296</b>), and the Y crank angle is read (step <b>298</b>). After completing these routines, the program proceeds through the steps<b>288</b> and <b>290</b> proceed to completion as shown.

Next, attention is paid to the <figref idref="S46">12</figref> to <figref idref="S48">16</figref> directed that illustrate another embodiment according to the invention, wherein segments in the form of sheets / sheets can be processed. (The term "segment" used herein with respect to the material to be processed in the devices of the invention is intended to cover both areas of a continuous web as well as discrete sheets.) As in<figref idref="S47">13</figref> shown is the positioning arrangement <b>300</b> a sheet-fed processing device such as a die cutter or a laminating unit. The order<b>300</b> generally contains a panel of a segment holder <b>302</b> with a central, generally rectangular opening <b>304</b>, where a vacuum hold-down plate <b>306</b> inside the opening <b>304</b> is arranged, a movement arrangement <b>308</b>that are operational with the plate <b>306</b> and a sheet / panel feed assembly <b>310</b>.

The bracket is in detail <b>302</b> in the form of a metallic plate <b>312</b>who have favourited Two Pairs of Belt Way Slots <b>314</b>, <b>316</b> and <b>318</b>, <b>320</b> has, each on opposite sides of the opening <b>304</b> are arranged. The bracket<b>302</b> also contains a pair of elongated, rod-like elements <b>322</b>, <b>324</b>that are at the bottom thereof adjacent to the side edges of the opening <b>304</b> are attached and extend inwards, as best in <figref idref="S47">14</figref> you can see. The Elements<b>322</b>, <b>324</b> are on the plate <b>312</b> using fasteners <b>326</b> appropriate. A nasal element<b>328</b> is similar at the bottom of the plate <b>312</b> attached adjacent to the front transverse edge thereof.

The hold-down plate <b>306</b> contains an upper metallic plate <b>330</b> with a number of vacuum openings <b>3323</b> through there. The plate<b>330</b> is on an underlying block <b>334</b> attached, thereby interacting a channel <b>336</b> just below the plate <b>330</b> is defined (see <figref idref="S47">14</figref>). A pair of vacuum connections<b>338</b>, <b>340</b> are in the block <b>334</b> provided, this via vertical connecting paths <b>342</b> with the channel <b>336</b> stay in contact (<figref idref="S48">15</figref>). These connections<b>338</b>, <b>340</b> are set up for connection to a vacuum system, which is not shown. The plate<b>330</b> and the block <b>334</b> are inside the opening <b>304</b> with the help of elements <b>322</b>, <b>324</b> held. As in<figref idref="S47">13</figref> illustrated is the opening <b>304</b> dimensioned so that it is slightly larger than the plate <b>330</b>so as to limit the movement of the latter within the limits of the opening <b>304</b> allow.

The movement arrangement <b>308</b> contains an elongated channel <b>344</b>that is below the block <b>334</b> is arranged and three spaced stepper motor drive units <b>346</b>, <b>348</b> and <b>350</b> wearing. For this purpose the channel<b>344</b> three generally rectangular openings provided therethrough, terminal openings <b>352</b> and <b>354</b>that are transverse to the longitudinal axes with respect to the longitudinal axis of the channel <b>344</b> are oriented, and a central opening <b>356</b>with its longitudinal axis parallel to that of the channel <b>344</b> is oriented. Each of the drive units contains a stepper motor<b>358</b> and an associated encoder <b>360</b> and a rotatable output shaft <b>362</b>. In addition, each of the units has a sled<b>364</b>, <b>366</b> or. <b>368</b>, which allows the unit to operate while the assembly is in operation <b>30</b> to postpone. Each such sled is in the form of a block with a central opening, the generally T-shaped sidewall surfaces<b>370</b> and an apertured top surface <b>372</b> Has. Every sledge<b>364</b> to <b>368</b> is with a pair of hanging yoke bearings <b>374</b>, <b>376</b> Mistake. In the case of the terminal sledge<b>364</b> and <b>368</b> these yoke bearings are parallel to the longitudinal axis of the channel <b>344</b> oriented while at the central sled <b>366</b> the yoke bearings are oriented perpendicular to this longitudinal axis. A pair of guides<b>378</b>, <b>380</b> are of rail type on opposite sides of each opening <b>352</b> to <b>356</b> on the canal <b>344</b> attached and fit the described yoke bearings for each slide <b>364</b> to <b>368</b>. So the guides are<b>378</b> to <b>380</b> for the terminal sledge <b>364</b> to <b>368</b> with the longitudinal axis of the channel <b>344</b> aligned while the guides for the central sled <b>366</b> are perpendicular to this axis.

The stepper motor <b>358</b> each drive unit <b>346</b> to <b>350</b> is operable with the bottom of the block through an eccentric coupling mechanism <b>334</b> coupled. An eccentric block<b>382</b> is on every motor output shaft <b>362</b> attached as best in <figref idref="S46">12</figref> you can see. The block<b>334</b> is with three spaced stationary couplers <b>384</b> equipped, each of which has a downward projecting pin <b>386</b> Has. The pencils<b>386</b> are made of suitable staggered openings in the corresponding eccentric block <b>382</b> added. The center-center distance between the pins<b>362</b>, <b>386</b> for each unit defines the crank length for that unit. The axes of the three pins are also located<b>386</b> on a common straight line.

The feed arrangement <b>310</b> contains a total of four endless belts <b>388</b>, <b>390</b>, <b>392</b>, <b>394</b>that on rolls <b>396</b> are mounted. The roles<b>396</b> are rotatable on suitable cross shafts <b>398</b>, <b>400</b> assembled.

The top stretches of each of the straps <b>388</b> to <b>394</b> are within the corresponding belt travel slots <b>314</b> to <b>320</b> recorded as from a consideration of the <figref idref="S47">13</figref> and <figref idref="S48">15</figref> is understandable.

When operating the arrangement <b>300</b> first a sheet / slab over the straps <b>388</b> to <b>394</b> for rough positioning on the plate <b>312</b> fed. At this time, the vacuum system is operated so that through the openings<b>332</b> a vacuum is drawn so as to hold the sheet. The drive units<b>346</b> to <b>350</b> are then operated, as necessary, so as to keep the plate <b>306</b> and the block <b>334</b> inside the opening <b>304</b> to move the sheet / board within the arrangement <b>300</b> to position exactly. A die cutting or laminating or other operation can then be performed on the precisely positioned sheet (or board), whereupon the arrangement<b>310</b> can be operated again to move the processed sheet (or the processed sheet) out of the arrangement.

It can be seen that the movement arrangement <b>308</b> can be controlled in a manner similar to that described in connection with the first embodiment, or by any other equivalent means. Generally speaking, all that is required is to provide reference data corresponding to the desired end position of the sheet / plate, along with means for comparing the current start position of the sheet / plate with this reference data. With this information, the drive units <b>346</b> to <b>350</b> appropriately operated for the final accurate positioning of the sheet / panel.

The use of the invention allows high speed operation on the order of 40 to 45 cycles / minute with dwell times of 200 milliseconds between strokes.

Although the invention is described in detail with the aid of a punching device, the invention is not limited to this. Rather, the invention can be used in a number of applications that require high speed and repetition of operations with high accuracy, such as various painting techniques.