TECHNICAL FIELD
The invention relates to an apparatus for automated abrasive machining or smoothing of surfaces of workpieces, for example for the grinding of workpiece surfaces.
BACKGROUND
The finishing of surfaces in small-scale production is still carried out by hand in most cases. This takes a lot of time and must be performed by an experienced worker. The higher the quality demands placed on the finished surface, the more complex this processing step becomes. An example of this is the surface of a car bonnet, for which the quality requirements placed on the surface are relatively high. There is no adequate solution for producing such a surface quality in small series other than manual work with a (hand) grinding machine. The grinding results of known automatic grinders are often inadequate, their adjustment is highly time consuming and they often require long run-in and run-out areas to prevent irregularities from arising on the finished final surface. These irregularities arise due to vibrations in the grinding belt or to the sluggish regulation of the contact force. The contact force is the force with which the grinding belt acts on the workpiece surface. The publication JP S63-089263 describes a device that controls the contact force by means of a suitable bearing. Because of the high inertial mass of the grinding machine, however—the inertia—inevitably leads to the phenomena described above.
The underlying object of the invention is thus to provide a device which enables elaborate grinding or grinding tasks to be performed, partially or fully automated, with improved quality.
SUMMARY
The mentioned object can be achieved, for example, with an apparatus according to claim 1 or with a method according to claim 9 and with a system according to claim 12. Various embodiments and further developments are the subject of the dependent claims.
Hereinafter an apparatus for processing a surface of a workpiece is described. According to one embodiment, the apparatus includes a frame and a roller carrier on which a first roller is rotatably supported and which itself is slidably supported on the frame along a first direction. The device comprises at least a second roller which is supported on the frame and a belt which is guided at least around the two rollers and whose tension results in a belt force that acts on the roller carrier. The apparatus further includes an actuator that is mechanically coupled to the frame and the roller carrier in such a way that an adjustable actuator force is applied between the frame and the first roller along the first direction. The belt is, with the aid of the second roller—or with the aid of the second roller and further rollers—guided in such a manner that the resulting belt force acting on the roller carrier acts, at a desired deflection of the actuator, approximately in a second direction orthogonal to the first direction.
Further, a method for the surface machining of a workpiece is described. According to one embodiment of the method, an apparatus is used comprising a frame, a roller carrier on which a first roller is rotatably supported and which itself is slidably supported to the frame along a first direction, an actuator mechanically coupled with the frame and the roller carrier, and a belt which is guided at least around the first roller, the belt exerting a resulting belt force on the roller carrier. The method thereby comprises positioning the workpiece on the first roller, measuring a contact force between the first roller and the workpiece, and adjusting a contact force between the first roller and the workpiece by adjusting a force acting between the frame and the actuator. While positioning the workpiece this is positioned relative to the apparatus such that the deflection of the actuator corresponds to its desired deflection. At the desired deflection, the resulting belt force acting on the roller carrier acts approximately in a second direction which is orthogonal to the first direction. The retroactive effect of the belt force on the actuator can thus theoretically be reduced to zero.
Further, a system for robot-supported surface machining of workpieces is described. In accordance with one embodiment, the system includes a machining device and a manipulator for the positioning of the workpiece relative to the machining device. This comprises a frame and a roller carrier on which a first roller is rotatably supported, the roller carrier being slidably supported on the frame along a first direction. The machining device comprises at least a second roller which is supported on the frame and a belt which is guided at least around the two rollers, and due to the tension of which a resulting belt force acts on the roller carrier. The machining device further includes an actuator that is mechanically coupled with the frame and the roller carrier such that an adjustable actuator force acts between the frame and the first roller along the first direction. The belt is guided, with the aid of the second roller—or with the aid of the second roller and further rollers—such that the resulting belt force acting on the roller carrier, at a desired deflection of the actuator, approximately acts in a second direction that is orthogonal to the first direction.
BRIEF DESCRIPTION OF THE DRAWINGS
The invention is explained in greater detail below with reference to the examples illustrated in the figures. The drawings are not necessarily to scale and the invention is not limited to the illustrated aspects. Emphasis instead being placed upon illustrating the principles underlying the invention. The figures show:
FIG. 1 shows a belt grinding device, in which the contact force between the workpiece and grinding belt is produced with the help of a manipulator.
FIG. 2 shows a belt grinding device according to an embodiment of the invention with resilient bearing of a first roller of the belt grinding device.
FIG. 3 shows a belt grinding device according to an embodiment of the invention, wherein the first roller is supplemented with a roller set.
FIG. 4 shows a detail of the device of FIG. 3 for better illustration of the forces acting on the rollers in the operating point (FIGS. 4a and 4c) and outside of the operating point (FIG. 4b).
FIG. 5 shows a further embodiment in which the resulting tension in the grinding belt and the contact force between the workpiece and the grinding device are approximately orthogonal to each other.
FIG. 6a shows a detail of the device of FIG. 5 to better illustrate the forces acting on the rollers and FIG. 6b shows an alternative to FIG. 6a.
FIG. 7 shows a further embodiment as an alternative to the example of FIG. 3.
FIG. 8 shows a variation in which not the work piece, but the grinding device is guided by a manipulator.
FIG. 9 shows an alternative example for the decoupling of belt forces and actuator force.
FIG. 10 shows a block diagram concerning the control of the contact force in a device according to the illustrated embodiments.
In the figures, like reference numerals designate the same or similar components each having the same or similar meaning.
DETAILED DESCRIPTION
The examples of the invention described herein will be described in connection with a belt grinding device 100. Other applications of the invention, for example, for surface coating or for polishing surfaces, are also possible.
The finishing of technical and optically high-quality surfaces requires a very high degree of precision in the production. Adherence to the required accuracy is made more difficult by the fact that the condition of the workpiece surface 200a changes during the processing period. Therefore, the finishing of surfaces, in particular for small series, is mostly carried out by hand in many fields. An example of a known grinding device 100 is illustrated in FIG. 1. The grinding device 100 is stationary and has a rotating grinding belt 102 which is guided over at least two rollers 101, 103. In the present example it is assumed that the belt rotates in the clockwise direction. The grinding belt 102 is tensioned by a tensioning element 105 (tension roller), which is supported by a linearly moveably suitable bearing 130 (for example by means of a slide bearing). The components (rollers 101 and 103, tensioning element 105) are connected by means of one or more carriers 401, 402, 403 with a frame 160 (such as a machine bed or a housing part).
For machining, the surface to be machined 200a of a workpiece 200 is pressed against the grinding belt 102 in the area of the first roller 101 while the grinding belt 102 is in motion. The necessary contact force FK (grinding force) can, for example, be manually adjusted or with the aid of a manipulator 150 that holds the workpiece. The manipulator 150 may be, for example, a standard industrial robot (with six degrees of freedom). Alternatively, however, other manually or mechanically actuated clamping and/or pressing devices can be used as a manipulator. Due to the contact force FK, friction occurs between the work surface 200a and the grinding belt 102 resulting in the abrasion of material. Main factors affecting the processing result include the contact force FK per surface area (contact surface area on which grinding belt 102 and the surface of the workpiece 200a touch), hereinafter also referred to as contact pressure, and the rotational speed of the grinding belt 102. As the contact surface area between the workpiece and grinding belt 102 does not usually change significantly during a grinding operation, contact pressure and contact force FK are de facto proportional. In the area of corners and edges the contact force (i.e., its desired value) may be reduced due to the smaller contact surface area.
For a uniform grinding result, a correct adjustment (i.e., control) of the contact force FK throughout the entire machining process is desirable. A force control by the generally “rigid” manipulator in known automated grinding devices has proven to be difficult, especially when placing the workpiece 200 on the grinding belt. In general, transient disturbances (force peaks) in the contact force FK are very difficult to compensate by conventional means of control. This is usually a consequence of the inertia of the moving parts of the manipulator 150 and of limitations in the actuators (minimum dead time, maximum force or torque, etc.). Insufficient force control results in inhomogeneous grinding patterns with chatter marks. Chatter marks are surface irregularities caused by insufficient control of the contact force FK. In areas in which has a higher contact force FK (temporarily) acts, cavities in the workpiece surface 200a are caused by greater material abrasion. At those points at which a lower contact force FK is temporarily prevalent, less material is removed and elevations remain. An experienced worker can compensate these inaccuracies when grinding by hand. When the workpiece surface 200a is placed on the grinding belt 102 automatically, in particular with the aid of a manipulator 150, these inaccuracies cannot be easily compensated. Due to the high inertia of the manipulator 150, adjustment to the prevailing grinding situation entails large time delays. In addition, the manipulator 150 can oscillate to varying degrees around its predefined desired position, which can lead to a non-uniform grinding pattern.
Instead of moving the workpiece 200 by means of a manipulator, it is also possible to clamp the workpiece 200 and to keep the grinding machine movable. In this case the actuator, with which the grinding force is controlled, would be coupled with the grinding machine, so that the grinding machine presses against the (stationary) workpiece. Also in this case there is the problem that the mass of the grinding machine, and thus its inertia, is relatively large and thus the same problem exists as in the above-described variation.
In the example shown in FIG. 2, the workpiece 200 is held and positioned by a manipulator 150. However, the manipulator 150 requires only a simple position control, the contact force control is—as described below—implemented in the grinding machine 100. Therefore relatively cheap manipulators (e.g. industrial robots) can be used, which can hold the workpiece at a desired position and can move it along a desired trajectory. In particular, no expensive force or torque sensors are needed in the joints of the manipulator. The actuator 302 used for the force control can be a simple linear actuator in this example, such as an actuator with low friction and passive compliance. Pneumatic cylinders, pneumatic muscles, air bellows, as well as electric direct drive (without gears), for example, are possible. In the present example, a pneumatic cylinder is used as actuator 302.
The actuator 302 does not act on the grinding machine 100 as a whole, but only on those rollers of the of the grinding machine 100 that press against the workpiece while in operation (i.e., on the roller 101). The roller 101 is (via the roller carrier 401) linearly slidably supported on the frame 160 (linear guide 140). The actuator 302 acts between roller carrier 401 and frame 160. In the present example, the actuator is supported on the roller carrier 401 and on a further carrier 404 which is rigidly connected to the frame 160. In accordance with the control of the actuator 302, an actuator force FA is applied to the roller 101 operating along the movement direction (x-direction) of the linear guide 140. Due to the comparatively small mass of the first roller 101 (and the roller carrier 401) only low inertia forces arise on the actuator 302.
Beyond this, the grinding device shown in FIG. 2 has the same structure as the grinding device in the previous example of FIG. 1. The second roller 103 is unslidably mounted via the (roller) carrier 403 to the frame 160. In this context, unslidably does not mean that the position of the roller 103 is unchangeable, for example for the purpose of setting a proper tension on the grinding belt. During operation of the device (e.g. during a grinding process), however, the position of the roller 103 does not change. The roller 103 is driven (motor 104), whereas the roller 101 serves only as a deflection roller. The grinding belt 102 is led around both rollers 101 and 103. As in the example of FIG. 1, a tensioning device for adjusting a bias tension of the grinding belt can be provided. The tensioning device may comprise, for example, one or more tension rollers 105 which are located on the belt 102 and which can be moved at approximately a right angle to the grinding belt 102 in order to tension the grinding belt 102. In the present example, the tension rollers 105 are mounted by means of a linear guide 130 on the roller carrier 402 which in turn is rigidly connected to the frame 160. The initial tension can be generated, for example, by means of a spring acting between the roller carrier 402 and the tension roller (or tension rollers) 105.
The forces acting in the grinding belt 102 are designated in FIG. 2 as belt forces FB1 (force in the upper portion 102a of the belt 102), and FB2 (force in the lower part 102b of the belt 102) whereas each of the two forces FB1 and FB2 comprise a force component in x-direction (FB1,x and FB2,x) and a force component in y-direction (FB1,y and FB2,y). The resulting belt force FB,y that acts on the roller 101 in the y direction (i.e. FB,y=FB1,y+FB2,y) is absorbed by the linear guide 140 and the tensioning device. The resulting belt force FB,x that acts on the roller 101 in the x direction (i.e. FB,x=FB1,x+FB2,x), however, also acts on the actuator 302 and thus against the actuator force FA. For the contact force FK, in the stationary case,
FK=FA+FB,x (1)
applies This means that the resulting belt force FB,x must be taken into account when controlling the contact force FK. For this, the belt force FB,x must be known. This may either be measured (for example, by means of a force sensor in the tensioning device and the drive torque of the motor), or estimated with the aid of a mathematical model. By correctly deflecting the grinding belt, however, the influence of the belt forces FB1, FB2 on the contact force FK can be reduced (in the ideal case, eliminated). In other words, actuator force FA, and the resulting belt force FB,X in the operating direction (x-direction) of the actuator 302 are decoupled. An example of a suitable deflection of the grinding belt 102 is illustrated in FIG. 3.
The example shown in FIG. 3 essentially corresponds to the previous example of FIG. 2, wherein in addition to the deflection roller 101, two other deflection rollers 101a and 101b are arranged on the roller carrier 401. Furthermore, two more deflection rollers 121a, 121b are provided which are unslidably mounted on the frame 160. The roller carrier 401 with the rollers 101, 101a and 101b is supported on the frame 160, as in the previous example, by means of the linear guide 140, wherein the linear guide permits a movement of the roller carrier 401 in the horizontal direction (x direction) and blocks other degrees of freedom. The deflection rollers 101a and 101b and the deflection rollers 121a and 121b are arranged so that—at a nominal deflection x0 (target displacement) of the actuator 302—the resulting belt force FB′ acting on the roller carrier 401 stands (at least approximately) in a right angle to the actuator force FA. In other words, the x-components FB,x′ of the resultant belt force FB′ is approximately zero, wherein the linear guide 140 only permits a force transmission from the actuator 302 to the roller carrier 401 in the x-direction. As in the previous example, the resultant belt force FB′ equals the sum of the belt force FB1′ in the upper part 102a of the belt 102 and the belt force FB2′ in the lower part 102b of the belt 102 (FB′=FB1′+FB2′). When the deflection x of the actuator 302 corresponds to the nominal deflection x0, this is referred to as operating point x=x0.
FIG. 4 shows the forces acting on a roller carrier 401 (for example, from FIG. 3) in detail. FIG. 4a shows a displacement x=x0 of the actuator at an operating point. FIG. 4c is a variant of FIG. 4a in which the actuator force FA acts exactly in the center of the roller carrier 401 such that all forces in the operating point are cancelled and no torque acts on the roller carrier 4. At a displacement x≠x0 of the actuator, the x-component FB,x′ of the belt force FB′ is no longer zero, but is instead FB,x′=FB′·sin(φ), wherein φ is the angular deviation of the force vector FB′ with respect to the y-direction. This means that, at an angular deviation of 3 degrees around 5% of the resultant belt force FB′ would react in the x-direction and thus to the actuator 302 as a disturbing force. When designing the grinding machine it can be constructed such that the angular deviation φ in operation is so small that this disturbing force remains negligible. In this context it should be noted that (only) the force FA exerted by the actuator 302 (and thus the contact force FK) is regulated. The actual deflection x of the actuator 302 during the grinding operation depends on the position of the workpiece 200, which in turn is set by the manipulator 150. However, the manipulator is position-controlled and can position the workpiece such that the actuator deflection x corresponds to the desired operating point x0, at which the deviation angle cp is zero.
In FIG. 4a and FIG. 4b, the relevant forces on the rollers 101, 101a, 101b supported on the roller carrier 401 are shown once again in detail. For clarity, only the rollers 101, 101a and 101b that are supported slidably in the x direction, as well as the grinding belt 102 and the workpiece 200 are shown. The position of the rotational axes of the rollers 101, 101a and 101b relative to one another is fixed and does not change during operation. The actuator force FA and the contact force FK act in x-direction on the rollers (actuator and contact forces in other directions are absorbed by the linear guide 140). In FIG. 4a, the actuator deflection x corresponds to the operating point x0 and consequently the belt forces FB1′ and FB2′ acting on the rollers 101a and 101b are oriented in the vertical direction and have no components in the horizontal direction (x-direction). Consequently, actuator force FA and the resulting belt force FB′=FB1′+FB2′ are decoupled. This means that the belt forces FB1′ and FB2′ do not react on the actuator 302. In FIG. 4b a situation is shown in which the workpiece is moved out of the operating point, that is, the actuator deflection is not equal to x0 and, consequently, the belt forces FB1′ and FB2′ acting on the rollers 101a and 101b are no longer (exclusively) oriented in a vertical direction but are instead tilted at an angle φ with respect to the y-direction. This has—as already mentioned—the consequence that the resulting belt force FB′ has a component in the x-direction i.e. FB,x′=|FB′ sin (φ). This force component FB,x′ reacts on the actuator and is either compensated by the force control or a control error in the amount of the belt force component FB,x′ arises. As long as the workpiece is guided and positioned by a manipulator 150, it can be ensured that the workpiece will always be located at the operating point and, consequently, that the actuator force FA and the belt forces FB1′, FB2′ acting on the roller 101 will be decoupled. Here it should be mentioned again that the actuator 302 only acts on the roller carrier 401 that carries the deflection rollers 101, 101a, 101b, and not on the entire grinding device. In the variation of FIG. 4c, the actuator force engages exactly at the center C, so that the tensioning forces FB1′, FB2′ and the friction force FR cancel each other. Similarly, contact force FK and actuator force FA cancel each other. The fact that the “lever” between the point of engagement of the respective forces FB1′, FB2′ and FR and the center C is always the same, no torques are applied (the sum of all torques is zero). Thus, no—potentially disturbing—torque load acts on the actuator.
FIG. 5 shows an alternative embodiment of the grinding device 100, which is also suitable for decoupling the actuator force FA and the belt forces FB1, FB2. In essence, the grinding device 100 is constructed in the same manner as in the previous example shown in FIG. 4. However, the linear guide 140 of the roller carrier 401 and the actuator 302 are turned by 90 degrees as compared to the example of FIG. 4. The frame 160 includes for this purpose an arm 402 on which the roller carrier 401 is rotatably supported (by means of the linear guide 140). The actuator 302 acts in the vertical direction (x-direction) between the arm 402 of the frame 160 and the roller carrier 401. The coordinate system is also turned by 90 degrees with respect to the previous example, so that the operating direction of the actuator 302, as in the previous example, is the x-direction. Additional deflection rollers are not necessarily needed in this embodiment. The grinding belt 102 is only led around the deflection roller 101 and the roller 103 (driven by the motor 104). As in the previous examples, a tensioning device with a tensioning roller 105 provides the necessary tension of the grinding belt 102.
The belt forces acting on the slidably supported deflection roller are designated FB1 (force in the upper belt part) and FB2 (force in the lower belt part). The force components FB1,x and FB2,x in the x-direction compensate for each other at least partially (FB1,x>0 and FB2,x<0), so that the resultant force component in x-direction FB1,x+FB2,x is negligibly small. With a suitable design of the grinding device, the resultant force FB1,x+FB2,x is equal to zero and there is no retroactive effect of the belt forces FB1 and FB2 on the actuator 302. FIG. 6a corresponds to the situation in FIG. 5, in which the grinding belt (in reference to the y-axis) runs at an angle φ2 to, and at an angle φ1 from the deflection roller 101 (clockwise direction of rotation). The force component in the x-direction of the upper belt force FB1 is thus |FB1|·sin (φ1), and the force component in x-direction of the lower belt force FB2 is equal to −|FB2|·sin (φ2). With a suitable design of the grinding device, the resulting belt force disappears in the x-direction |FB1|·sin (φ1)−|FB2|·sin (φ2) and there is no retroactive effect on the actuator 302 (for example, because φ1=φ2 and |FB1|=|FB2|). In the modified example of FIG. 6b two deflection rollers 121a and 121b, fixedly mounted on the frame 160, ensure that the angles φ1 and φ2 equal zero and that the belt thus runs to and from the roller 101 horizontally. Accordingly, in this case the resulting belt forces in the x direction are zero, provided that the workpiece, and thus the actuator 302 are at the operating point (x=x0). However, as explained with reference to the previous example (FIG. 3), this is set by means of the manipulator 150.
FIGS. 7a and 7b show further embodiments that are constructed similarly to the example of FIG. 3. In the example in FIG. 7a two rollers 101a and 101b are provided on the roller carrier 401, on which the actuator 302 acts. The belt 102 runs over the two rollers 101a, 101b substantially perpendicular to the operating direction of the actuator 302. The workpiece 200 can be machined (e.g. ground or polished) between the rollers 101a, 101b; the belt can adapt to the contour of the workpiece 200. Beyond this, the example of FIG. 7a is constructed the same as the embodiment of FIG. 3. In order to avoid repetition, reference is therefore made to the explanations concerning FIG. 3. The alternative of FIG. 7b substantially corresponds to the previous example of FIG. 7a, with the only difference that no rollers are arranged on the carrier 401′. Instead, the carrier 401′ (gliding carriage) has a gliding surface 101c along which the belt can glide at a substantially right angle to the effective direction of the actuator 302. In both examples, the belt 102 runs, in the operating point, substantially perpendicular to the operating direction of the actuator 302. The actuator force FA, and the contact force (retroactive force) FK (FK=−FA) are thus decoupled from the belt forces FB1′, FB2′, in the sense that the belt forces FB1′, FB2′ have not retroactive effect on the actuator 302.
Unlike the preceding embodiments, in the embodiment according to FIG. 8, it is not the workpiece that is guided by the manipulator 150, but the grinding machine. The frame 160 (cf. e.g. FIG. 3) is thus part of the manipulator 150 and/or rigidly attached (to the Tool Center Point TCP) thereof. The workpiece 200 may be arranged on a firm base (not shown). Similarly as in the example of FIG. 3, two further deflection rollers 101a and 101b are arranged on a roller carrier 401 next to the deflection roller 101. Further, two more deflection rollers 105 and 103 are provided which are supported on the manipulator 150 (a, frame 160) by means of the roller carriers 402 and 403. As in the example of FIG. 3, the roller 4 can be driven by a motor. The motor (not explicitly shown) can also be mounted on the carrier 402. The roller 105 on the roller carrier 402 may be designed as a tension roller. Alternatively, a tensioning unit for tensioning the belt 102 may be integrated on the motor. In this case the roller 105 would be a simple deflection roller.
The roller carrier 401 with the rollers 101, 101a and 101b is, similar to the example of FIG. 3, slidably supported on the manipulator, thereby making it possible to move the roller carrier 401 in the x-direction while blocking other degrees of freedom. The carrier 404 is also supported on the manipulator 150. The actuator 302 is arranged on the carrier 404 and acts on the roller carrier 401. Unlike in the preceding examples, in FIG. 8 no grinding belt is used, but rather simple belt. Serving as a tool, a grinding wheel 101′ (or other rotating tool) is connected to the front roller 101. As in the previous examples, at an operating point of the actuator (actuator deflection x=x0) the belt runs substantially perpendicular to the operating direction of the actuator, so that the belt forces FB1′, FB2′ are decoupled from the actuator force and no retroactive effect of the belt forces FB1′, FB2′ is exerted on the actuator 302.
FIG. 9 shows another example in which two rollers 101, 101a are arranged on opposite ends of an elongated roller carrier 401. The roller carrier is slidably supported on the frame 160 (cf. FIG. 3, not shown in FIG. 9). Two additional rollers 103 and 105 are also supported on the frame (carriers 403 and 402), wherein the roller 105 may be driven by a motor (cf. FIG. 3, not shown in FIG. 9) and the other roller 103 may be a part of the tensioning unit for tensioning the circulating belt 102. Alternatively, the tensioning unit can also be integrated in the drive (roller 105). The slidable roller carrier 401 (gliding carriage) is disposed between the rollers 103 and 105; the belt running around the rollers 101, 103, 101a, 105 belt forms, in the cross-sectional view, an approximately convex quadrilateral. Based on the illustration is clear that the belt forces acting on the roller carrier 401 cancel each other in the operating direction of the actuator 302, and have no retroactive effect on the actuator 302 that acts on the roller carrier 401. The actuator presses with a force FA on the roller carrier 401, and thus presses the roller 101 onto the workpiece. The contact force FK (retroactive force) corresponds to the actuator force FA (FK=−FA).
According to FIG. 9, the workpiece is guided by a manipulator 150 and positioned such that the deflection x of the actuator 302 is located in a defined operating point x0. The actuator 302 operates purely force-regulated; the position is determined by the (position-controlled) manipulator 150. Small deviations from the operating point (for example, due to the form and positional tolerances of the workpiece or due to limited positioning accuracy of the manipulator 150) lead to no significant change in the geometry of the device and the belt forces, so that the grinding force can always be set by the force controlled actuator 302.
FIG. 10 shows an example of a control circuit for controlling the contact force FK between the workpiece 200 and the grinding belt 102 on the deflection roller 101. With complete decoupling between actuator force FA and the resulting belt force FB,x in the operating direction of the actuator (x-direction), the actuator force FA and the contact force FK are equal in magnitude, but oppositely oriented, that is, −FK=FA. If a part of the resulting belt force FB reacts back on the actuator 302, the magnitude of the contact force will be the sum of the actuator force FA and the resultant belt force in the operating direction of the actuator FB,x, i.e. −FK=FA+FB,x.
The force measurement (load unit 303) can be conducted directly via a force sensor integrated in or coupled with actuator 302. In a pneumatic actuator, however, the force can also be measured indirectly via the pressure p in the pneumatic actuator, taking into account the deflection x of the actuator 302. That is, the actuator force FA(p, x) is a function of pressure p in the actuator (for example, in the pneumatic piston) and the deflection x of the actuator. From the measured actuator force FA, the sought measurement value FK,m for the contact force can be determined. With a decoupling between the resultant belt force FB and the actuator force FA, FK,m=−FA(p, x) applies. If no complete decoupling between actuator force FA and the resultant belt force FB,x in the operating direction of the actuator 320 is given, an estimation or a separate measurement of the resultant belt force can be taken into account when measuring the contact force. In this case, FK,m=−FA(p, x)−FB,x applies for the measured value. From the measured value FK,m for the contact force and a corresponding reference value FK,s, a control error FE can be calculated (FE=FK,s−FK,m) which is supplied to the controller 301 at the input side. The controller 301 may be, for example, a P controller, a PI controller or a PID controller. However, other types of controllers can also be used.
Patent Grant
10974362
