Abstract:
An overload protector has an input element, an output element juxtaposed with the input element, and a clamping plate. Fasteners fix the clamping plate to one of the elements against relative movement. A coupling between the clamping plate and the other of the elements permits only limited relative movement of the elements through a stroke having a predetermined length in a predetermined direction. A connector between the clamping plate and the other element fixes the clamping plate and the other element together against relative movement until an overload force greater than a predetermined critical limit is exerted shifting either of the elements toward or away from the other element in the predetermined direction.

Description:
CROSS REFERENCE TO RELATED APPLICATIONS 
     This application is the US-national stage of PCT application PCT/DE2008/000203, filed 5 Feb. 2008, published 12 Sep. 2008 as WO2008/106916, and claiming the priority of German patent application 102007011489.5 itself filed 7 Mar. 2007, whose entire disclosures are herewith incorporated by reference. 
     FIELD OF THE INVENTION 
     The invention relates on the one hand to an overload protector having a force input element and a force output element rigidly and nonpositively connected to one another using a positive connection and movable relative to one another when the overload protector is actuated. On the other hand, the invention relates to a drive train having a first drive train link and having at least one further drive train link between a drive and a tool fixedly connected to one another as the drive train, an overload protector being between the first drive train link and the further drive train link. The invention also relates to a device having a lifting tool for producing and/or processing a workpiece, in which the lifting tool is mounted so it is movable in the device using a drive train having an overload protector. The invention also relates to a method for applying working forces to a lifting tool, which is driven using drive links guided on predetermined movement paths, and in which, in the event of a driving force overload, an overload protector is actuated and drive links are thus disconnected from one another. 
     BACKGROUND OF THE INVENTION 
     Overload protectors according to the species are known from the prior art in numerous designs and are used in particular in punch machines for protecting components and/or component groups from irreparable destruction in the event of a malfunction, because enormous working forces are generated in machines of this type. 
     OBJECT OF THE INVENTION 
     It is the object of the present invention to refine known overload protectors in such a way that damage can be reduced or even avoided on a device for producing and/or processing a workpiece, in particular on a drive train of such a device. 
     SUMMARY OF THE INVENTION 
     The object of the invention is achieved by an overload protector having a force input element and a force output element rigidly and nonpositively connected to one another using a positive connection and movable relative to one another when the overload protector is actuated, the overload protector having an emergency coupling allowing the force input element and the force output element to move relative to one another when the overload protector is actuated while remaining connected to one another so they are guided with control relative to one another. 
     Known overload protectors do not have an emergency coupling of this type, so that in the event of an actuated overload protector, drive train links of a drive train move uncoordinated with one another so that they may severely damage themselves and/or surrounding areas of a machine. This is avoided in the present case. 
     The term “actuated overload protector” describes in the present case that the overload protector was triggered because of an overload situation, for example, in a transmission of a press, so that a drive side and an output side are disconnected from one another in regard to working forces. 
     The term “force input element” describes a component of the overload protector in the present case with which working forces are introduced on the drive side into the overload protector. In any case having a particularly simple construction, the force input element is identical to a first drive train link provided on the drive side in the drive train. 
     Correspondingly, the term “force output element” refers to a component of the present overload protector with which drive forces may be transmitted on the output side to a tool. In an embodiment having a particularly simple construction, the force output element thus forms a further drive train link associated on the output side with a tool, for example, such as a lifting tool. 
     The present emergency coupling can be implemented in various ways, as long as the force input element and the force output element are guided securely to one another when the overload protector is actuated. In order that the force input element and the force output element are guided particularly operationally reliably to one another when the overload protector is actuated, it is advantageous if the emergency coupling comprises corresponding guides, along which the force input element and the force output element may execute a controlled guided relative movement to one another when the overload protector is actuated. 
     In particular in regard to gear links for transmitting pressure and/or traction forces, it is advantageous if the overload protector has linear guides along which the force input element and the force output element may execute translational relative movements guided to one another, in particular an exclusively translational relative movement, because in this way the two elements may be moved translationally to one another along their main force-transmitting axes. 
     The present described positive connection with which the force input element and the force output element are nonpositively connected to one another, can be embodied many ways. A positive connection is already known from the prior art, so that in the present case it will only be discussed in that it is advantageous if the positive connection has a bias-tensioned triggering component and/or a shear pin, because a shear pin can be exchanged cost-effectively and easily and thus replaced in case of an actuated overload protector. Alternatively to the shear pin, for example, a component group having a bias-tensioned ball or another bias-tensioned triggering part may be used as the positive connection. 
     In order that a shear pin does not have to be oversized for transmitting the required working forces, it is advantageous in the present case if the force input element and the force output element are nonpositively and rigidly connected to one another using a friction-locked connection. The required force transmission preferably occurs via the shear pin—or another element for the removable retention of a force equilibrium—and additionally via a friction lock. 
     An advantageous embodiment variant in this regard provides that the friction-locked connection comprises two clamping elements, between which the force input element and the force output element are clamped. 
     It is ensured by the friction-locked connection that the working forces do not have to be completely transmitted by the positive connection between the input element and the output element. Rather, the positive connection can also be dimensioned as a function of the friction-locked connection. 
     In order that a drive side and an output side of a drive train may be moved guided relative to one another undamaged, in is particular on a main force axis, when an overload protector is actuated, it is advantageous if the force input element and the force output element are connected spaced apart from one another by a gap. 
     In the present case, the term “gap” describes a spacing between the force input element and the force output element, so that both elements may move relative to one another. For example, this ensures that a drive side can perform a working stroke without the output side having to follow the movement of the working stroke as in normal working operation. In particular, it is conceivable that the gap in the overload protector is configured as a free stroke between the force input element and the force output element, so that after triggering of the overload protector, the incoming working stroke is relayed in a limited way to the force output element or the incoming stroke is eliminated completely, so that in the second case the drive rotates “freely”. 
     In an embodiment of particularly simple construction, the force input element and the force output element are on the head side toward one another. If the two force elements of the overload protector lie opposite in such a way, the overload protector has a particularly compact construction, because the force main axes of the force input element and the force output element are advantageously parallel to one another or even coaxial. 
     Correspondingly, a particularly preferred embodiment variant provides that the force input element and the force output element form tension rods and/or pressure rods in a drive train. 
     In particular, the gap described in the present case is between the force input element and the force output element can be provided in a particularly simple construction if the force input element and the force output element form a push rod of a drive train. 
     In order that an overload and thus an actuation of the overload protector can be signaled immediately and a drive of the working machine can be turned off, it is advantageous if the overload protector comprises sensors that register relative movement between the force input element and the force output element. If relative movements between the force input element and the force output element exceed a critical level in the present case, this is ascertained immediately by the sensors and an emergency shutdown operation of a machine is started, for example. The present sensors may be implemented in manifold ways, in particular using microswitches, strain gauges, or arbitrary contacts. 
     The above object is achieved according to a second aspect of the invention by a drive train having a first drive train link and at least one second drive train link fixedly connected to one another between a drive and a tool, an overload protector being between the first drive train link and the second drive train link, and the drive train links being connected to one another and movably guided relative to one another when the overload protector is actuated. 
     The drive train links between which the overload protector is provided advantageously remain connected to one another even when the overload protector is actuated in such a way that they are guided to one another—in particular in a defined way—and thus remain connected to one another. Drive train links that are disconnected from one another in regard to working forces are thus prevented from smashing around uncontrolledly. 
     In order that the drive train links disconnected from one another in regard to working forces may be guided movably to one another, it is advantageous if the drive train links are spaced apart from one another by a safety gap. Using a safety gap of this type ensures that the drive train links on the input side may execute a working stroke unchanged even after an overload event, without causing further damage in this way. The safety distance is ideally selected as a function of the gap in such a way that the drive train links on the output side execute no or only a negligible stroke. 
     In order that a lifting tool transmits no or only insignificant working forces to a workpiece when the overload protector is actuated, although the drive is still active, it is advantageous if the gap at least corresponds to a working stroke which the drive or a component of the drive, such as a cam disk, provides during a working movement cycle. If the gap is selected as greater than the working stroke, the danger that a tool will still execute a stroke as long as the drive is still revolving is decreased. 
     In order to be able to dimension it economically, it is proposed that the gap be no more than 120% of the working stroke. 
     In order to protect the tool from damage in an is incorrectly running machine in particular, it is advantageous if the gap corresponds to at least 80%, preferably at least 95% of a working stroke of the lifting tool. 
     The gap between the input-side drive train link and the output-side drive train link preferably corresponds at least to a longitudinal extension of the overload protector in the shortest extension thereof, i.e. the longitudinal extension when the overload protector is triggered. 
     The drive train described in the present case, in particular the overload protector described, can advantageously be used in particular everywhere large tractive and/or pressure forces occur between components which interact with one another. Thus, it is advantageous if the drive train comprises a toggle lever mechanism. Toggle lever mechanisms are usually used in connection with large working forces, so that the present invention can be combined particularly advantageously with toggle lever mechanisms. 
     The present drive train and the present overload protector are also particularly well suitable in connection with a drive with a cam disk or an eccentric disk, because cam and/or eccentric disks of this type initially continue to rotate nearly unchecked because of their high masses even in the event of a malfunction in a drive train. Using the present overload protector and/or the present drive train, however, cam and/or eccentric disks of this type revolve further until they reach a standstill and, on the one hand, a tool no longer exerts working forces on a workpiece and, on the other hand, drive-side drive train links may be moved is guided relative to output-side drive train links on the overload protector without damaging their surroundings. 
     The drive train is constructed in a particularly simple construction if the drive train links form a push rod. Particularly high working forces may be transmitted without problems using a push rod. 
     Because of the advantages of the present overload protector, a preferred embodiment of the drive train provides an overload protector according to at least one of the features explained in the present case. 
     According to a third aspect of the invention, the object is achieved by a device having a lifting tool for producing and/or processing a workpiece, in which the lifting tool is mounted movably in the device using a drive train having an overload protector, the device being distinguished by a drive train according to one of the features and/or feature combinations explained above and/or by an overload protector according to one of the features and/or a feature combination explained above. The advantages of the present overload protector and/or the present drive train may thus also be used in connection with a device having a lifting tool. 
     The object is achieved in regard to the method by a method for applying working forces to a lifting tool driven using drive links guided on predetermined movement paths, and in which an overload protector is actuated in the event of a drive force overload, whereby drive links are disconnected from one another solely in regard to working forces when the overload protector is actuated, and guide forces interacting between the disconnected drive links on the overload protector. 
     The drive links disconnected from one another with respect to working forces are advantageously connected to one another in such a way that guide forces act between them, so that the disconnected drive links are not unguided in the disconnected area. 
     A method variant provides that the disconnected drive links are guided essentially along the predetermined movement paths in the disconnected area. 
     It is particularly advantageous if the lifting tool executes no stroke or a secondary stroke when the overload protector is actuated. 
     The term “secondary stroke” refers to a movement of the lifting tool which does not describe a complete working stroke, so that the danger that the lifting tool will be damaged when the overload protector is actuated is decreased. In addition, the lifting tool can still be moved in spite of the actuated overload protector, in order to move it into a starting or maintenance position, for example. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWING 
       The invention is explained in greater detail below with reference to an exemplary device for producing and processing workpieces having an overload protector in a drive train. In the figures: 
         FIG. 1  is a rough schematic view of a molding facility having an overload protector between a drive side and an output side, 
         FIG. 2  is a schematic perspective view of the overload protector from  FIG. 1 , 
         FIG. 3  is a schematic side view of the overload protector from  FIGS. 1 and 2 , and 
         FIG. 4  is a schematic exploded view of the overload protector from  FIGS. 1 through 3 . 
     
    
    
     DETAILED DESCRIPTION 
     The molding facility  1  having a fixed top tool  2  in turn having a molding and punching tool top part  3 , and translationally movable bottom tool  4  itself having a molding and punching tool bottom part  5 , is used, for example, for the purpose of molding plastic cups via a first working stroke partial step and, after the cooling of the molding compound used for this purpose, punching them out as the plastic cups via a further working partial stroke. The working stroke described above is performed as shown by the double arrow  6  in a movement direction along which the translationally movable bottom tool  4  is moved. 
     The molding facility  1  is driven by a motor (not shown) that drives an eccentric disk  8  in a rotational direction  9  via a drive shaft  7 . In order to convert the rotational movement in the direction  9  of the eccentric disk  8  into translational movement as shown by the double-headed arrow  6 , a transmission  10  is provided between the eccentric disk  8  and the translationally movable bottom tool  4  and essentially comprises a toggle lever mechanism  11  and a push rod  12 . 
     In the present case, a first toggle lever  13  is pivoted on the translationally movable bottom tool  4  and a second toggle lever  14  is pivoted on a machine housing  15 . The two toggle levers  13  and  14  are connected to one another at a toggle joint  16 , the push rod  12  also being fastened to the toggle joint  16 . 
     The pushrod  12  is in two parts and comprises a first pushrod link  17  and a second pushrod link  18 , between which an overload protector  19  is situated. 
     The overload protector  19  is used for the purpose of protecting the transmission  10  and the molding and punching tool parts  3  and  5  from damage in the event of an overload. 
     In the present case, the motor, the drive shaft  7 , the eccentric disk  8 , and the first pushrod link  17  represent a drive side  20  of the machine  1 , while the translationally movable bottom tool  4 , the toggle lever mechanism  11 , and the second pushrod link  18  essentially form an output side  21  of the molding facility  1  relative to the overload protector  19 . 
     The overload protector  19  ensures that the eccentric disk  8  can revolve, at least as long as its inherent kinetic energy allows it, without moving the toggle lever mechanism  11  when the overload protector  19  is actuated in such a way that the working forces act on the translationally movable bottom tool  4 . 
     For this purpose, the overload protector  19  is constructed as follows (cf.  FIGS. 2 through 4 ): 
     The overload protector  19  has a force input element  22  formed by the first pushrod link  17  (cf.  FIG. 1 ). In addition, the overload protector has a force output element  23  formed by the second pushrod link  18  (cf.  FIG. 1 ). The force input element  22  is pivoted by a first bearing eye  24  on the eccentric disk  8 , while the force output element  23  is pivoted by a second bearing eye  25  on the toggle joint  16 . Intermediate elements may be provided between both the force input element  22  and eccentric disk  8  and also between the force output element  23  and toggle joint  16 . 
     The force input element  22  and the force output element  23  are juxtaposed at a gap  26  at their heads to one another and are clamped between a first clamping plate  27  and a symmetrical second clamping plate  28 . To apply the required clamping forces between the two clamping plates  27  and  28  and the force input element  22 , on the one hand, and the two clamping plates  27  and  28  and the force output element  23 , on the other hand, a plurality of clamping screws  29  is provided on the overload protector  19 . 
     In order that the force input element  22  and the force output element  23  are securely held and guided relative to the clamping plates  27  and  28 —and thus also to one another—first horizontal keys  30  and first vertical keys  31  are on the force input element  22  and second horizontal keys  32  and second vertical keys  33  are on the force output element  23 . All keys  30  through  33  are screwed onto the respective force input element  22  or the force output element  23  on both sides and in a known way using key screws  34 . 
     The first horizontal keys  30  fit in first horizontal key grooves  35 , the first vertical keys  31  fit in first vertical key grooves  36 , the second horizontal keys  32  fit in second horizontal key grooves  37 , and the second vertical keys  33  fit in second vertical key grooves  38 , so that all components, i.e. force input element  22 , force output element  23 , first clamping plate  27 , and second clamping plate  28  are retained and guided in a defined way relative to one another. 
     In order that the overload protector  19  can be actuated in case of an overload and the force input element  22  can perform a guided relative movement relative to the force output element  23 , namely in the framework of the gap  26 , the first horizontal key grooves  35  and the first vertical key grooves  36  are made bigger by the gap  26  in an axial direction  39  of the overload protector  19  than the respective horizontal keys  30  and vertical keys  31  corresponding thereto, i.e. the first horizontal key grooves  35  are longer and the first vertical key grooves  36  are wider (cf.  FIG. 3  in particular, in which the force input element  22  and the force output element  23  having the second clamping plate  28  are shown schematically one above another). 
     If the frontal distance of the force input element from the force output element is greater or less than the play of the keys in their grooves, the gap  26  is defined as the lesser of the two dimensions. The two dimensions are preferably at least approximately equal, however. 
     Relative movement of the force input element  22  to the force output element  23  and the two clamping plates  27  and  28  is only possible when a shear pin  40  of the overload protector  19  has been sheared off because of overload forces. The force input element  22  is first free in this case, in order to execute a free stroke  26 A relative to the force output element  23  according to the gap  26 . 
     The shear pin  40  can also be on both sides on the force input element  22 , so that one shear pin interacts with the first clamping plate  27  and one shear pin interacts with the second clamping plate  28 . 
     In order that the actuation of the overload protector  19  can be displayed immediately on the motor and/or drive console of the present compression and punching machine  1 , movement sensors  41  and  42  are provided in particular in the area of the first vertical key grooves  36  and the corresponding first vertical keys  31 , which immediately register and relay a corresponding signal when the first vertical keys  31  of the force input element  22  move relative to the first vertical key grooves  36  of the first clamping plate  27  and the second clamping plate  28 . 
     The first horizontal keys  30 , the first vertical keys  31 , the first horizontal key grooves  35 , and the first vertical key grooves  36  form the emergency coupling of the overload protector  19  in their interaction with which the force input element  22  and the force output element  23  may execute a guided relative movement to one another when the overload protector  19  is actuated. In particular, linear guides are provided in a way having a particularly simple construction by these components, so that the force input element  22  and the force output element  23  may move translationally relative to one another in a guided way.