DOME DEVICE AND ROLL FORMING MACHINE

Description

[0001] The present disclosure relates to a coupling device for connecting a drive block to at least one working shaft of a roll forming stand, which comprises at least one universal joint shaft with a drive-side end and an output-side end, wherein the output-side end is connectable to an input section of a working shaft of the roll forming stand, and an automated actuation unit for engaging and disengaging the universal joint shaft. Furthermore, the present disclosure relates to a roll forming system with such a coupling device.

[0002] From EP 3 311 932 A1, on which the preamble of patent claim 1 is based, 2 a coupling device for a profiling machine is known which comprises a movement device for compensating the axial offset and the vertical offset between a cardan shaft and an output shaft, wherein the movement device has two drives in the form of linear cylinders. During coupling, the output side of the cardan shaft is initially moved axially until, in the event of a vertical offset, a vertical sliding surface of the cardan shaft strikes a coupling pin of the output shaft. This is followed by a vertical movement of the output side of the cardan shaft until a coupling sleeve on the output side of the cardan shaft and the coupling pin of the output shaft can engage with one another. In other words, two drives are required for the coupling process of a cardan shaft.

[0003] A coupling device with at least partially automated operation is known from EP 2 452 760 A1. During coupling processes for coupling and uncoupling working shafts of roll forming stands, it is often necessary to compensate for both an axial offset and a radial offset (also: parallel offset) between a drive shaft and the working shaft. For this purpose, universal joints are usually provided, designed, for example, as cardan shafts. One drive-side end of such a universal joint is usually connected to the drive shaft. An opposite output-side end is connected to an working shaft of the roll forming stand during operation of the roll forming stand.

[0004] EP 0 365 976 A2 discloses a general design of a profiling machine (also known as a roll forming machine) that has several so-called coupling stands that enable a connection between a gear block of a drive and roll forming stands. Profiling machines and roll forming systems are regularly used for processing and machining metal strips and similar materials. A semi-finished product in the form of a metal strip or starting profile is transformed into a target profile by means of longitudinal forming. Roll forming systems can also enable additional processing steps, such as punching, welding, and the like. After the desired forming and machining, the target profile can be cut to length to produce workpieces of the desired length.

[0005] Roll forming stands for roll forming systems are typically adjustable to accommodate a variety of rolled profiles. A roll forming stand typically comprises two stacked working shafts (upper shaft and lower shaft), whose vertical position is adjustable both absolutely and relative to each other. Roll forming stands can also be adjusted along a transfer direction of the semi-finished product to be processed, thus allowing the production process to be influenced. Drive blocks typically comprise a plurality of drive shafts that can be driven by one or more drives. The drive shafts are often stationary within a drive block, so that compensation is often required between the position of the working shafts of a roll forming stand and the position of their associated drive shafts in the drive block.

[0006] A coupling process typically requires compensation for the axial and radial offsets between the shafts involved. Therefore, multiple degrees of freedom of movement are often provided, which must be taken into account for automated operation. Manual coupling and uncoupling is also conceivable, but this involves a considerable amount of work, especially with a large number of roll forming stands. This complicates, for example, the conversion of a roll forming system when switching between two different workpieces.

[0007] Against this background, the present disclosure is based on specifying a coupling device for a roll forming system and a roll forming system equipped with such a coupling device, in which automated coupling and uncoupling of the working shafts is possible, so that any setup and adjustment processes can be carried out quickly and with minimal effort. The engagement and disengagement should be as simple and reliable as possible. A high repeatability of the coupling process is desired. The coupling device should be manufacturable with minimal effort. The coupling device should also be suitable for retrofitting older profiling machines and roll forming systems, at least in exemplary embodiments.

[0008] This object is achieved in a coupling device of the type mentioned at the outset in that the actuating unit has a coupling mechanism with a guide slot which, at least when the cardan shaft is engaged, compensates for an axial offset and a radial offset between the output-side end of the cardan shaft and the input section of the working shaft, wherein the guide slot has a section which is inclined both with respect to a direction of the axial offset and with respect to a direction of the radial offset, and wherein the output-side end and the input section are movable relative to one another along the inclined section in order to couple the cardan shaft to the working shaft.

[0009] In other words, the coupling mechanism helps ensure that both offset components are taken into account and compensated for, at least during engagement. Ideally, a relatively complex compensating movement can be performed with just a few drive components. This simplifies the automated coupling and uncoupling of the working shafts of the roll forming stand. In an exemplary embodiment, it is conceivable that the coupling mechanism restores the original offset upon disengagement, for example, when transferring the drive shafts to a rest position.

[0010] Wherever compensation for axial and / or radial misalignment is discussed within the scope of this disclosure, the primary focus is on ensuring that such compensation is carried out to a degree that enables simple and reliable engagement / coupling. In other words, this means that, depending on the tolerance insensitivity of the coupling components involved, absolutely complete compensation may not be necessary. However, due to the degrees of freedom in the design and positioning of the roll forming stands and their output shafts, a significant axial and / or radial misalignment is regularly to be expected, which must at least be sufficiently compensated to enable coupling of the output-side end of the cardan shafts and the input section of the output shafts. The coupling mechanism also facilitates the disengagement / uncoupling of cardan shafts and output shafts.In other words, the coupling mechanism can also provide defined orientations in an immediately released state, for example for the respective output-side end of the cardan shafts.

[0011] The drive shafts are designed as cardan shafts, for example, with two universal joints, one located at the drive end and one at the output end. A sliding joint is installed between them to achieve the required longitudinal compensation.

[0012] An axial offset is, for example, a (frontal) distance between facing coupling parts of the output end of the cardan shafts and the input section of the output shafts. A radial offset is, for example, a distance between longitudinal axes through the output end of the cardan shafts and the input section of the output shafts.

[0013] In an exemplary embodiment, during operation of the coupling device, in particular during coupling and uncoupling, an at least substantially parallel orientation is maintained between the longitudinal axis of the output-side end of the cardan shaft and the longitudinal axis of the input section of the working shaft.

[0014] During operation of the roll forming system, a drive with at least one associated drive block is arranged essentially stationary. The drive block has a plurality of drive connections, each of which can drive a working shaft via a cardan shaft. The roll forming stands that support the working shafts are adjustable with various degrees of freedom. For processing with a high degree of forming, a plurality or multiplicity of roll forming stands with corresponding working shafts is required. Therefore, when changing between different workpieces, the roll forming system must be reconfigured. An automated coupling device significantly simplifies this process.

[0015] In an exemplary embodiment, only a single actuator is required to engage and disengage the drive shaft with the output shaft. In other words, only a single actuator is required to operate the coupling device, at least for engaging and disengaging a drive shaft, while still allowing for offset compensation in two directions. This significantly reduces the structural and control-related complexity of the coupling device.

[0016] The guide slot provides positive guidance during the relative movement between the output end of the drive shaft and the input section of the output shaft, at least when the drive shaft is engaged. It goes without saying that the positive guidance may also be effective during disengagement.

[0017] The guide slot can deflect the drive movement and the resulting movement. This allows the output end of the cardan shafts to be brought closer to the input section of the drive shafts, even with a significant offset.

[0018] The guide slot provides positive guidance. In other words, in the case of a resulting movement in multiple axes, no complex drive control or similar is required to compensate for axial and radial misalignment. As long as a given axial and / or radial misalignment lies within a tolerable range, the positive guidance can ensure that the respective misalignment is overcome.

[0019] The guide slot has a section that is inclined relative to both the axial and radial offset directions. This allows both the axial and radial offsets to be at least partially compensated with a single drive movement provided by an actuator.

[0020] In general, the guide slot and the entire coupling device can also be designed to compensate for a certain (minor) angular misalignment between the output end of the cardan shaft and the input section of the output shaft. This can be achieved, for example, by appropriate insertion aids and / or an angular misalignment-compensating coupling.

[0021] According to another exemplary embodiment, the guide slot has a section extending parallel to a longitudinal axis of the output shaft adjacent to the inclined section. In this way, the inclined section can be used to overcome a radial offset. Provided sufficient concentricity is established between the output-side end of the cardan shaft and the input section of the output shaft, the subsequent section, which is oriented parallel to the longitudinal axis of the output shaft, can be used to overcome the remaining axial offset.

[0022] According to another exemplary embodiment, the guide slot is arranged adjacent to the input section of the working shaft on the roll-forming stand. In other words, in this embodiment, the guide slot serves as an insertion aid for the output-side end of the cardan shaft as it approaches the input section of the working shaft. The guide slot is thus at least temporarily fixed to the roll-forming stand.

[0023] According to another exemplary embodiment, the coupling mechanism has at least one guide roller that can be moved along the guide slot, which can be moved together with the output-side end of the cardan shaft. This allows the output-side end of the cardan shaft to be supported on the guide slot during engagement and disengagement and to be moved relative to the guide slot. A guide roller enables low-friction movement. As an alternative to the guide roller, a guide pin, a guide skid, or similar element could serve as the guide element. The use of two spaced-apart guide elements is also conceivable, for example, two axially offset guide rollers. This reduces susceptibility to transverse forces.

[0024] In principle, a reverse arrangement is also conceivable, in which the guide slot is located at the output end of the cardan shaft and is movable together with it relative to the input section of the output shaft. Accordingly, a guide roller associated with the guide slot would then be located at the input section of the output shaft.

[0025] According to another exemplary embodiment, the coupling mechanism comprises a movable bearing piece arranged at the output end of the cardan shaft and interacting with the guide slot at least when the cardan shaft is engaged. The movable bearing piece carries, in particular, a guide roller or a guide pin. The movable bearing piece is moved by an actuator of the automated actuation unit. The movable bearing piece is coupled to the guide slot, so that the resulting movement is redirected.

[0026] The output end of the drive shaft is mounted on / in the bearing piece so that it can rotate relative to the bearing piece. The drive shaft can therefore move within the bearing piece as it rotates. The movable bearing piece moves the output end of the drive shaft as it moves. The movable bearing piece also defines an orientation of the longitudinal axis through the output end of the drive shaft. In one exemplary embodiment, the movable bearing piece accommodates the output end of the drive shaft, which is rotatably mounted within it.

[0027] According to a further exemplary embodiment, the coupling mechanism has a first guide and a second guide oriented at an angle to the first guide, wherein the second guide is displaceably held on the first guide, and wherein the bearing piece is displaceable along the second guide. The first guide and the second guide are, for example, linear guides. The first guide and the second guide in combination provide a (for example two-dimensional) travel range for the movable bearing piece, which in turn is coupled to the forced guidance provided by the guide slot. At least in exemplary embodiments, the first guide is referred to as a vertical linear guide and the second guide as a horizontal linear guide.

[0028] For example, the first guide is oriented vertically. For example, the second guide is oriented horizontally. A reverse assignment is conceivable. The designations "first guide" and "second guide" are primarily used for differentiation purposes. In an example configuration, the first guide is the guide that is located closer to a frame / base of the roll forming system than the second guide.

[0029] In the context of the present disclosure, a guide is typically a unit with two components, comprising a rail and a carriage, which are movable relative to each other. This may include a linear movement of the carriage along the rail. However, this may also include a linear movement of the rail along the carriage.

[0030] According to a further exemplary embodiment, at least the second guide is coupled to a pretensioning element that urges the second guide into a rest position. For example, the pretensioning element compensates for the force of gravity acting on the second guide along the degree of freedom of movement provided by the first guide. In an exemplary embodiment of the coupling device for a roll forming stand with two working shafts arranged one above the other, the pretensioning element urges the second guide of an upper bearing piece for the upper cardan shaft upwards. In an exemplary embodiment of the coupling device, the rest position of the second guide of a lower bearing piece for a lower cardan shaft is reached automatically with the aid of gravity. Nevertheless, the use of a pretensioning element is also conceivable for a lower unit.

[0031] According to another exemplary embodiment, the actuating unit has a common actuator for movement along the first guide and along the second guide. Thus, a single drive movement in a single direction on the bearing piece is sufficient to result in a two-dimensional movement of the bearing piece in two directions. This is made possible by the guide slot, which redirects the movement of the bearing piece. The first guide and the second guide provide a corresponding range of motion for the bearing piece.

[0032] The common actuator could be, for example, a common fluid cylinder with an extendable rod. This could be a pneumatic cylinder, a hydraulic cylinder, or something similar. An electric actuator, such as a spindle drive and / or a linear motor, is also conceivable.

[0033] According to a further exemplary embodiment, the coupling device comprises the following: a first cardan shaft having a drive-side end and an output-side end, wherein the output-side end is connectable to a first working shaft of the roll-forming stand, a second cardan shaft having a drive-side end and an output-side end, wherein the output-side end is connectable to a first working shaft of the roll-forming stand, wherein the actuating unit has a first actuating section for engaging and disengaging the first cardan shaft and a second actuating section for engaging and disengaging the second cardan shaft, and wherein the first actuating section and the second actuating section each have a coupling mechanism which compensates for an axial offset and a radial offset between the output-side end of the cardan shaft and the input section of the working shaft, at least when the cardan shaft is engaged.

[0034] The coupling device thus comprises a first unit and a second unit. The first unit can be referred to, for example, as the lower unit and can be designed to couple a lower cardan shaft to a lower working shaft of the roll-forming stand. The second unit can be referred to, for example, as the upper unit and can be designed to couple an upper cardan shaft to an upper working shaft of the roll-forming stand. In this way, an at least fundamentally symmetrical design with a horizontal plane of symmetry can be achieved. It is understood that a non-symmetrical design is also conceivable.

[0035] According to a further exemplary embodiment, the actuating unit engages or disengages the first propeller shaft and the second propeller shaft together. This can comprise a suitable joint control of a first actuator for the first propeller shaft and a second actuator for the second propeller shaft. It is also conceivable in principle to provide a single actuator that jointly acts on the movable bearing pieces of the first propeller shaft and the second propeller shaft. In this way, a complex, multi-dimensional movement can be realized for both the first propeller shaft and the second propeller shaft with only two actuators or even with a single actuator.

[0036] According to another exemplary embodiment, the first actuating section and the second actuating section have a common actuator for engaging or disengaging the first propeller shaft and the second propeller shaft. Thus, there is a common actuator for both propeller shafts.

[0037] According to another exemplary embodiment, the first actuating section comprises a first actuator for engaging or disengaging the first propeller shaft, and the second actuating section comprises a second actuator for engaging or disengaging the second propeller shaft. Thus, there is one actuator for each propeller shaft.

[0038] According to another exemplary embodiment, the output-side end of the at least one cardan shaft can be connected to the input section of the output shaft via a curved-tooth coupling. A design as a toothed coupling or claw coupling is generally conceivable. The coupling should ensure a certain degree of robustness against (possibly minor) tolerance deviations.

[0039] A curved-tooth coupling is at least sufficiently tolerant of rotational deviations and, if applicable, angular misalignment. A curved-tooth coupling is also sufficiently tolerant of axial deviations. Thus, a curved-tooth coupling can help ensure that the highest precision in the approach between the output end of the cardan shafts and the input section of the drive shafts is not required.

[0040] According to another exemplary embodiment, the curved-tooth coupling comprises a first coupling part with curved teeth configured as internal gearing and a second coupling part with curved teeth configured as external gearing. It is understood that a reverse arrangement is also conceivable in an alternative embodiment.

[0041] According to another exemplary embodiment, the at least one universal joint shaft can be driven in a rotationally oscillating manner in an engagement mode to facilitate engagement between the first clutch part and the second clutch part. Thus, when the two clutch parts approach each other, the universal joint shaft is driven in a rotationally oscillating manner by small angular amounts so that the teeth and gaps of the clutch can locate each other. The drive block, which drives the universal joint shafts and thus ultimately the working shafts of the roll forming system, is typically coupled to a drive control system that can perform appropriate control interventions.

[0042] According to a further exemplary embodiment, a combination of a coupling device according to at least one of the embodiments described herein and a drive block is therefore provided, to which a drive control is assigned, wherein the drive control is designed to drive the at least one cardan shaft in an engagement mode in a rotationally oscillating manner in order to simplify the engagement of the curved tooth clutch.

[0043] According to a further aspect, the present disclosure relates to a roll forming system comprising a plurality of roll forming stands and a drive block with at least one drive for driving working shafts of the roll forming stands, and with at least one coupling device according to at least one of the embodiments described herein, which is arranged between the drive block and at least one of the roll forming stands. The coupling device connects the drive block and the at least one roll forming stand, as needed, to drive working shafts of the roll forming stand. Coupling and uncoupling can be automated.

[0044] Further features and advantages will become apparent from the following description of several preferred embodiments with reference to the drawings. They show: Fig. 1: a schematic view of a modular roll forming system; Fig. 2: a perspective view of a coupling device arranged between a drive block and a roll forming stand; Fig. 3: an enlarged perspective view of the coupling device according to Fig. 2 ; Fig. 4: a further enlarged perspective view based on the illustration according to Fig. 3 to illustrate an actuating section of the coupling device; Fig. 5: a frontal view of the arrangement according to Fig. 2 ; Fig. 6: a partial view of the arrangement according to Fig. 5 in plan view; Fig. 7: a sectional view along the line VII-VII in Fig. 6 ; and Fig. 8: a sectional view along the line VIII-VIII in Fig. 6 with opposite cutting direction compared to the representation in Fig. 7 .

[0045] Fig. 1 illustrates, using a simplified schematic diagram, a roll forming system designated as a whole by 10. The roll forming system 10 is used to process flat material or strip material. A material flow through the roll forming system 10 is Fig. 1 by a block file 12 for the input and a block file 14 for the output. Roll forming systems 10 are typically used to process sheet metal.

[0046] The roll forming system 10 has a modular design. However, this is not to be understood as limiting. In the exemplary embodiment, the roll forming system 10 comprises a material feed module 18, which is arranged at the entrance. From there, a metallic semi-finished product in the form of a flat material or strip material can be provided for further processing. Module 18 is followed by a module 20, which in the exemplary embodiment is designed as a punching module. This is followed by one or more roll forming modules 22, 24, in which forming processes take place. In the exemplary embodiment, a trend module 26 for separation is also connected, followed by a handling module 28 for handling the resulting workpieces. At least the roll forming modules 22, 24 each have a plurality of roll forming stands 30. It is understood that the roll forming system 10 in Fig. is shown as representative of a variety of configurations. Roll forming systems 10 can be used purely for forming processes.However, it is also conceivable to integrate further processing steps, such as punching, welding, assembly and the like.

[0047] The present disclosure relates to the design of coupling devices for connecting a drive to working shafts of roll forming stands 30 of a roll forming system 10. Fig. 2 illustrates, by way of example and in a perspective view, a part of one of the roll forming modules 22, 24 of the roll forming system 10. A coupling device 40 is installed between a drive block 42 and at least one roll forming stand 30. It is understood that for each of the Fig. 2 A separate coupling device 40 is conceivable for the three roll forming stands 30 shown. For illustrative purposes, only one coupling device 40 is shown.

[0048] The roll forming stands 30 are mounted on a common base 44. The coupling device 40 and the drive block 42 are coupled directly or indirectly to the base 44 on the frame side. The coupling device 40 comprises a first universal joint shaft 50 and a second universal joint shaft 52. The first universal joint shaft 50 can be connected to a first working shaft 56 of the roll forming stand 30 by the coupling device 40. The second universal joint shaft 52 can be coupled to a second working shaft 58 of the roll forming stand 30 by the coupling device 40.

[0049] The first drive shaft 50 can also be referred to as the lower drive shaft. The second drive shaft 52 can also be referred to as the upper drive shaft. Similarly, the first drive shaft 56 can be referred to as the lower drive shaft, and the second drive shaft 58 can be referred to as the upper drive shaft. A lower element is positioned closer to a base or floor than an upper element. Typically, in a roll forming stand, the first drive shaft 56 and the second drive shaft 58 are arranged one above the other, each horizontally aligned. This determines the basic orientation of the first drive shaft 50 and the second drive shaft 52.

[0050] The drive block 42 typically comprises a plurality or multiplicity of drives for a corresponding number of cardan shafts 50, 52. The drive block 42 can also be referred to as a transfer case. Typically, a drive block 42 is designed such that a plurality or multiplicity of working shafts 56, 58 of several roll forming stands 30 can be driven with only one drive (drive motor).

[0051] The roll forming stands 30 with their working shafts 56, 58 can be positioned differently along the base 44. Furthermore, a respective vertical position (e.g., distance from the base 44) of at least some of the working shafts 56, 58 can be adjusted. In this way, for example, an axial offset or a radial offset to the cardan shafts 50, 52 can result, which must be overcome by the coupling device 40 when connecting to the drive block 42.

[0052] Based on the representation according to Fig. 2 shows Fig. 3 an enlarged detailed view of the same orientation. Fig. 4 illustrates a further perspective view omitting the drive block 42 and partially omitting the cardan shafts 50, 52.

[0053] The first cardan shaft 50 has a drive-side end 62 ( Fig. 3 ) and an output end 68 ( Fig. 4 ) which can be coupled to a first input section 74 of the first working shaft 56. The second drive shaft 52 has a drive-side end 64, Fig. 3 ) and an output end 70 ( Fig. 4 ) which can be coupled to a second input section 76 of the second output shaft 58. The drive-side ends 62, 64 serve for connection to the drive block 42. The output-side ends 68, 70 serve for connection to the output shafts 56, 58. Between the respective drive-side end 62, 64 and the associated output-side end 68, 70, the cardan shafts 50, 52 in the exemplary embodiment have two universal joints, between which a sliding joint extends. In this way, the cardan shafts 50, 52 are fundamentally designed to compensate for an axial offset and a radial offset. Other designs of the cardan shafts 50, 52 are nevertheless conceivable.

[0054] The coupling device 40 further comprises an actuating unit 78, which comprises a first actuating section 80 for the first propeller shaft 50 and a second actuating section 82 for the second propeller shaft 52. In the illustrations according to the Figuren 2-8 The actuating sections 80, 82 are constructed essentially symmetrically to a horizontal plane. It is understood that this symmetrical basic structure is important during operation of the coupling device 40 or the roll forming system 10 ( Fig. 1 ) cannot necessarily be maintained if the two drive shafts 50, 52 must compensate for different amounts of axial and / or radial misalignment. Therefore, the term "symmetrical design" is not intended to be limiting.

[0055] The actuating unit 78 comprises a coupling mechanism 86, 88 for each of the two drive shafts 50, 52. A coupling mechanism 86 is assigned to the first drive shaft 50. A coupling mechanism 88 is assigned to the second drive shaft 52. The purpose of the coupling mechanisms 86, 88 is to redirect movement for the purpose of compensating for an offset between the drive shafts 50, 52 and the working shafts 56, 58 assigned to them.

[0056] The output end 68 of the first cardan shaft 50 is seated in a movable bearing piece 92, compare again Fig. 4 The output-side end 70 of the second cardan shaft 52 sits in a movable bearing piece 94. The first bearing piece 92 can be moved via the actuating section 80. The first bearing piece 92 is coupled to the first coupling mechanism 86. The linear drive movement of the first bearing piece 92 is converted into a redirected output movement by the coupling mechanism 86. The second bearing piece 94 can be moved via the actuating section 82. The second bearing piece 94 is coupled to the second coupling mechanism 88. The linear drive movement of the second bearing piece 94 is converted into a redirected output movement by the coupling mechanism 88.

[0057] Fig. 4 With the drive shafts 50, 52 largely hidden, it illustrates a stand 98 which, in the exemplary embodiment, supports components of the first actuating section 80 and the second actuating section 82 of the actuating unit 78. Furthermore, a first guide 102 is arranged on the stand 98, which in the exemplary embodiment comprises a vertically oriented first rail 104. The guide 102 and the rail 104 are jointly assigned to the first actuating section 80 and the second actuating section 82.

[0058] In the first actuating section 80, a (first) first carriage 108 sits on the first rail 104. In the second actuating section 82, a (second) first carriage 110 sits on the first rail 104. A support 114 is arranged on the carriage 108, which supports an actuator 120 for moving the first bearing piece 92. A support 116 is arranged on the carriage 110, which supports an actuator 122 for moving the second bearing piece 94.

[0059] The carrier 114 further carries a (first) second guide 126, which in the exemplary embodiment comprises a carriage 132 fixed to the carrier 114 and a rail 138 movable along the carriage 132. The carrier 116 further carries a (second) second guide 128, which in the exemplary embodiment comprises a carriage 134 fixed to the carrier 116 and a rail 140 movable along the carriage 134. The first bearing piece 92 is mounted on the (first) second rail 138. The second bearing piece 94 is mounted on the (second) second rail 140. The first actuator 120 comprises an extendable rod 144, which acts on a driver 150 fixed to the first bearing piece 92. The second actuator 122 includes an extendable rod 146 that acts on a driver 152 that is fixed to the second bearing piece 94.

[0060] The first bearing piece 92 is coupled to the first coupling mechanism 86 (see also Fig. 5 ). The first coupling mechanism 86 comprises a guide slot 156, which includes an inclined section 160 and a parallel section 166. The inclined section 160 is inclined relative to a longitudinal axis through the drive-side end 68 and / or through the first output shaft 56. The parallel section 166 is oriented parallel or substantially parallel to the longitudinal axis through the drive-side end 68 and / or through the first output shaft 56. The guide slot 156 is formed on a bracket 172, which is associated with and adjacent to the input section 74 of the first output shaft 56 with a defined orientation. The first bearing piece 92 moves along the guide slot 156 with a guide roller 176.

[0061] The second bearing piece 94 is coupled to the second coupling mechanism 88. The second coupling mechanism 88 includes a second guide slot 158, which includes an inclined section 162 and a parallel section 168. The inclined section 162 is inclined relative to a longitudinal axis through the drive-side end 70 and / or through the second output shaft 58. The parallel section 168 is oriented parallel or substantially parallel to the longitudinal axis through the drive-side end 70 and / or through the second output shaft 58. The guide slot 158 ​​is formed on a bracket 174, which is associated with and adjacent to the input section 76 of the second output shaft 58 with a defined orientation. The second bearing piece 94 moves along the guide slot 158 ​​with a guide roller 178.

[0062] To illustrate the movements during the interaction between the bearing pieces 92, 94 and the guide slots 156, 158, reference is made to the (lower) first actuating section 80 with the first bearing piece 92 and the first guide slot 156. When the rod 144 of the first actuator 120 fixed to the first carrier 114 is extended, the bearing piece 92 and the drive-side end 68 of the first cardan shaft 50 received therein are moved linearly along the (first) second guide 126. This movement is a horizontal linear movement in the exemplary embodiment; compare the double arrow 182 in Fig. 4 .

[0063] The drive movement pushes the bearing piece 92 with its guide roller 176 along the guide slot 156. This initially includes a movement along the inclined section 160, compare the double arrow 188 in Fig. 4 . When moving into the parallel section 166, the orientation of the movement changes, compare the double arrow 190 in Fig. 4 . Along the inclined section 160, a radial offset between the output end 68 and the input section 74 can be compensated. Along the parallel section 166 and at least partially along the inclined section 160, an axial offset between the output end 68 and the input section 74 can be compensated. Furthermore, the parallel section 166 facilitates the final engagement (and, if necessary, disengagement) between the output end 68 and the input section 74.

[0064] The movement of the bearing piece 92 along the inclined section 160 has a vertical component and a horizontal component, again compare the double arrow 188. The original drive movement by extending the rod 144 of the actuator 120 occurs horizontally along the second guide 120 (compare the double arrow 182). However, since the bearing piece 92 is also moved vertically, compensation occurs via the movement of the first carrier 114 along the first guide 102, compare the vertically oriented double arrow 184 in Fig. 4 The amount of movement along the first guide 102 (double arrow 184) can correspond to the amount of the compensated radial offset. Furthermore, the amount of movement along the second guide 126 (double arrow 182) can correspond to the amount of the compensated axial offset.

[0065] The same applies to the movement of the second bearing piece 94 with respect to the second guide slot 158 ​​for coupling the second cardan shaft 52 with the second working shaft 58.

[0066] Fig. 4 further shows a preload element 194, which is supported on the stand 98 and urges the carrier 116 arranged on the (second) first carriage 110 toward a rest position, in the orientation shown upwards. In this way, a downward weight force G can be compensated by components of the second actuating section 82, which the carrier 116 carries, as well as by the carrier 116 itself. Fig. 4 The first actuating section 80 and the second actuating section 82 are each shown in a rest position. In the first actuating section 80, this includes contact with a lower stop for the (first) first carriage 108, which supports the carrier 114. In the second actuating section 82, this includes contact with an upper stop for the (second) first carriage 110, which supports the carrier 116.

[0067] With reference to the Figuren 5-8 Further exemplary design features of the coupling device 40 are illustrated in more detail. Fig. 4 shows a front view of an arrangement of roll forming stand 30, coupling device 40 and drive block 42. Fig. 6 shows a corresponding top view. Fig. 7 shows a sectional view in frontal orientation, with the section line VII-VII in Fig. 6 corresponds. Fig. 8 shows a sectional view in opposite direction Fig. 7 reversed orientation, with the section of line VIII-VIII in Fig. 6 corresponds.

[0068] Fig. 5 shows the fundamentally already based on the Figuren 2-4 illustrated design of the coupling device 40 for connecting the drive block 42 with working shafts 56, 58 of the roll forming stand 30 via cardan shafts 50, 52. In Fig. 5 Furthermore, longitudinal axes 198, 200 through a respective output-side end 68, 70 of the cardan shafts 50, 52 as well as longitudinal axes 204, 206 of the working shafts 56, 58 are shown.

[0069] The mutually facing output-side ends 68, 70 and input sections of 74, 76 have, when oriented in Fig. 5 each have an axial offset 210, 212, which must be bridged by the coupling device 40. Furthermore, between the longitudinal axes 198 and 204 and the longitudinal axes 200 and 206, there is a radial offset 216, 218, which must also be bridged by the coupling device 40. The previously described configuration of the actuating unit 78 with the actuating sections 80, 82 enables the coupling device 40 to bring about a required compensating movement in several directions in the individual actuating sections 80, 82 with only one actuator 120, 122 each.

[0070] Fig. 6 illustrates, based on a partial view (top view) of the coupling device 40, that in the exemplary embodiment the cardan shafts 50, 52 and the working shafts 56, 58 are arranged one above the other, wherein the associated longitudinal axes 198, 200 and 204, 206 are in a common vertically oriented plane (in Fig. 6 perpendicular to the view plane). This is not to be understood as limiting. Fig. 6 further illustrates the sections VII-VII and VIII-VIII in the following Figures 7 and 8.

[0071] In Fig. 7 und Fig. 8 A section through the axes 198, 200 and 204, 206 is shown. A clutch is formed between the output-side ends 68, 70 of the cardan shafts 50, 52 and the input sections 74, 76 of the working shafts 56, 58 facing them. The output-side ends 68, 70 each form a clutch part 222, 224, and the input sections 74, 76 each form a clutch part 228, 230, which can be combined with one another.

[0072] In Fig. 7 A design as a curved-tooth coupling 220 is indicated, which is formed by the coupling parts 222 and 228. The curved-tooth coupling 220 comprises, in the coupling part 222 in the exemplary embodiment, a curved toothing 234 designed as an internal toothing and, in the coupling part 228, a curved toothing 236 designed as an external toothing. The curved toothings 234, 236 can engage with each other. The curved-tooth coupling 220 is relatively insensitive to (minor) deviations in position and orientation, so that the automated engagement and disengagement is supported by the coupling device 40. It is understood that in the Fig. 7 In the embodiment shown, each of the two cardan shafts 50, 52 can be connected to the associated working shaft 56, 58 via a curved tooth coupling 220.

[0073] In an exemplary embodiment, the coupling parts 222, 224 of the cardan shafts 50, 52 are provided with a rotationally oscillating drive during the coupling process. This allows the teeth and gaps of the coupling parts 222 and 228, as well as 224 and 230, to easily locate each other. A drive control system designated 248 is used to generate the rotational oscillation movement, which accordingly acts on the drive block 42 and its drive.

[0074] Fig. 8 illustrates in addition that in an exemplary embodiment, both actuators 120, 122 can be controlled jointly via a common connecting line 250. In other words, the two actuators 120, 122 are synchronized in terms of control technology in this embodiment. The coupling process of the two cardan shafts 50, 52 with the working shafts 56, 58 takes place in parallel. A control (in Fig. 8indicated by 252) acts on both actuators 120, 122 via the common connecting line 250.

[0075] As already explained above, it is also conceivable in principle to use only a single actuator to move both bearing pieces 92, 94. If necessary, relative movements between the two bearing pieces 92, 94 (usually in the vertical direction) would then have to be compensated for via suitable guides.

[0076] It is also conceivable, in principle, to deviate from the fundamentally "symmetrical" design of the two actuating sections 80, 82 of the actuating unit 84 and choose a similar but offset design. With such an arrangement, there would be no structural symmetry between the actuating sections 80, 82. In other words, with this approach, one of the two actuating sections 80, 82 could be duplicated and offset vertically from the other actuating section. Such a design with a "pattern" of two identical or largely identical actuating sections 80, 82 can also be implemented in principle with two actuators 120, 122, each of which is assigned to one of the actuating sections 80, 82. However, it is also conceivable to provide only one actuator for both actuating sections 80, 82.

Claims

1. A coupling device (40) for connecting a drive block (42) to at least one working shaft (56, 58) of a roll forming stand (30), comprising: - at least one universal shaft (50, 52) having a drive-side end (62, 64) and a driven-side end (68, 70), wherein the driven-side end (68, 70) is connectable to an input section (74, 76) of a working shaft (56, 58) of the roll forming stand (30), - an automated actuating unit (78) for engaging and disengaging the universal shaft (50, 52), characterized in that the actuating unit (78) comprises a coupling mechanism (86, 88) with a guide link (156, 158) which compensates for an axial offset (210, 212) and a radial offset (216, 218) between the driven-side end (68, 70) of the universal shaft (50, 52) and the input section (74, 76) of the working shaft (56, 58), at least when the universal shaft (50, 52) is engaging, wherein the guide link (156, 158) has a section (160, 162) which is inclined both with respect to a direction of the axial offset (210, 212) and with respect to a direction of the parallel offset (216, 218), wherein the driven-side end (68, 70) and the input section (74, 76) are movable relative to one another along the inclined portion (160, 162) in order to couple the universal shaft (50, 52) to the working shaft (56, 58).

2. The coupling device (40) of claim 1, characterized in that for engaging and disengaging the universal shaft (50, 52) with the working shaft (56, 58), only a single actuator (120, 122) is required.

3. The coupling device (40) of claim 1, characterized in that the guide link (156, 158) provides a forced guidance during the relative movement between the driven-side end (68, 70) of the universal shaft (50, 52) and the input section (74, 76) of the working shaft (56, 58), at least when the universal shaft (50, 52) is engaging.

4. The coupling device (40) of any of claims 1-3, characterized in that the guide link (156, 158) has, following the inclined section (160, 162), a section (166, 168) extending parallel to a longitudinal axis (204, 206) of the working shaft (56, 58).

5. The coupling device (40) of any of claims 1-4, characterized in that the guide link (156, 158) is arranged adjacent to the input section (74, 76) of the working shaft (56, 58) at the roll forming stand (30).

6. The coupling device (40) of any of claims 1-5, characterized in that the coupling mechanism (86, 88) has at least one guide roller (176, 178) which can be moved along the guide link (156, 158) and can be moved together with the driven-side end (68, 70) of the universal shaft (50, 52).

7. The coupling device (40) of any of claims 1-6, characterized in that the coupling mechanism (86, 88) has a movable bearing piece (92, 94) which is arranged at the driven-side end (68, 70) of the universal shaft (50, 52) and interacts with the guide link (156, 158), at least when the universal shaft (50, 52) is engaging, and that the movable bearing piece (92, 94) carries in particular a guide roller (176, 178) or a guide bolt.

8. The coupling device (40) of claim 7, characterized in that the coupling mechanism (86, 88) has a first guide (102) and a second guide (126, 128) oriented obliquely to the first guide (102), that the second guide (126, 128) is movably supported on the first guide (102), and that the bearing piece (92, 94) is displaceable along the second guide (126, 128).

9. The coupling device (40) of claim 8, characterized in at least the second guide (126, 128) is coupled to a biasing element (194) that urges the second guide (126, 128) to a rest position.

10. The coupling device (40) according to claim 8 or 9, characterized in that the actuating unit (78) has a common actuator (120, 122) for movement along the first guide (102) and along the second guide (126, 128).

11. The coupling device (40) of any of claims 1-10, characterized by a first universal shaft (50) having a drive-side end (62) and a driven-side end (68), the driven-side end (68) being connectable to a first working shaft (56) of the roll forming stand (30), and a second universal shaft (52) having a drive-side (64) and a driven-side end (70), the driven-side end (70) being connectable to a second working shaft (58) of the roll forming stand (30), wherein the actuating unit (78) has a first actuating section (80) for engaging and disengaging the first universal shaft (50) and a second actuating section (82) for engaging and disengaging the second universal shaft (52), and wherein the first actuating section (80) and the second actuating section (82) each have a coupling mechanism (86, 88) which compensates for an axial offset (210, 212) and a radial offset (216, 218) between the driven-side end (68, 70) of the universal shafts (50, 52) and the input section (74, 76) of the working shafts (56, 58), at least when the universal shafts (50, 52) are engaging.

12. The coupling device (40) of claim 11, characterized in that the first actuating section (80) and the second actuating section (82) have a common actuator (120, 122) for engaging and / or disengaging the first universal shaft (56) and the second universal shaft (58), or the first actuating section (80) has a first actuator (120) for engaging and / or disengaging the first universal shaft (56), and the second actuating section (82) has a second actuator (122) for engaging and / or disengaging the second universal shaft (58).

13. The coupling device (40) of any of claims 1-12, characterized in that the driven-side end (68, 70) of the at least one universal shaft (56, 58) can be connected to the input section (74, 76) of the working shaft (56, 58) via an arcuate toothed coupling (220).

14. The coupling device (40) of claim 13, characterized in that the arcuate toothed coupling (220) has a first coupling part (222) with an arcuate toothing (234) configured as an inner toothing and a second coupling part (228) with an arcuate toothing (236) configured as an outer toothing, and that preferably the at least one universal shaft (50, 52) can be driven in a rotationally oscillating manner in an engagement mode in order to simplify the engagement between the first coupling part (222) and the second coupling part (228).

15. Roll forming line (10) having a plurality of roll forming stands (30) and a drive block (42) for driving working shafts (56, 58) of the roll forming stands (30), characterized by at least one coupling device (40) according to any of claims 1-14 that is arranged between the drive block (42) and at least one of the roll forming stands (30).