Patent Application
20080184766
The invention relates to a straightening rotor, a rotor straightener and a corresponding straightening method.
Such a straightening rotor is known from U.S. Pat. No. 1,936,679, DE 10 34 576 B or DE 39 10 221 A1, for example. A rod or similar work piece is here guided through the rotating frame of a straightening rotor, and radially aligned by means of separate straightening elements in such a way as to lose its previous curvature and receive a desired progression, preferably a straight progression. U.S. Pat. No. 1,936,679 here shows an inlet-side straightening element as well as two outlet-side straightening elements, which coaxially grip a work piece in the frame, while three actively bending central straightening elements are provided between the inlet and outlet-side straightening elements, of which a central straightening element is radially offset. By contrast, the rotor straightener described in DE 39 10 221 A1 exhibits two inlet-side straightening elements as well as two outlet-side straightening elements, which are also mounted in the rotating frame of a straightening rotor, but the respective outside straightening elements are rigidly secured to the rotating frame, wherein the straightening elements are formed by roll barrels. The straightening rotor according to DE 39 10 221 A1 also exhibits three interior additional straightening elements, but these are all radially offset. The straightening rotor according to DE 10 34 576 B works with a central straightening element and two outlet- and two inlet-side straightening elements, which are all mounted in a rotating frame.
While the straightening rotor according to U.S. Pat. No. 1,936,679 uses roller units as the straightening elements throughout, DE 39 10 221 A1 and DE 10 34 576 B suggest the use of straightening dies throughout.
Such rotor straighteners are not to be construed with non-rotating straightening apparatuses, e.g., of the kind known from DE 195 03 850 C1 or DE 43 25 492 A1, and in which a high level of automation in adjusting the straightening elements has already been achieved, as described in these publications and also by Marcus Paech in his article “Innovative Straightening Technique” in Draht 2/1999, pages 46 to 51.
Accordingly, efforts are also underway to increase the level of automation for straightening impeller rotors or rotor straighteners, for example, as disclosed in DE 197 09 733 C2, DE 25 23 831 B2, DE 43 11 566 A1 and WO 03/084695 A1. However, the respective measures are here initially confined to attempts at positioning straightening elements in an appropriate manner. In pursuing these approaches, it was discovered that these adjusting devices necessitate significant structural measures in the straightening rotor or corresponding straightening machine, which would make such a straightening rotor or straightening machine extremely expensive on the one hand, and, owing to considerable centrifugal forces, give rise to balancing problems, and allow operationally safe use only with the rotor shut down on the other.
The object of the present invention is to further develop a straightening rotor or a rotor straightener as well as a straightening method with a straightening rotor in such a way as to enable operation at higher speeds.
To achieve the object, the invention proposes a straightening rotor characterized by at least two freely positionable balancing means that are essentially arranged symmetrical to a central plane, axially relative to a rotational axis of the straightening rotor.
By contrast to prior art, freely positionable balancing means make it possible to address changes in mass distribution in the straightening rotor, in particular those caused by work piece, for example. Fixed balancing means, such as balancing boreholes or prescribed and assessable balancing masses that can be assessed ad a function of a working position of the straightening elements, e.g., as disclosed in DE 35 46 029 C2, are unable to accomplish this in particular. Such measures can also generally not be used to effect a precision adjustment, for example, of the kind necessary for an individual readjustment of the straightening means.
Only the freely positionable balancing means according to the invention enable the optimal alignment of the center of gravity, and also the center-of-gravity axis, since the balancing means are arranged essentially symmetrical to the central plane, axially relative to a rotational axis of the straightening rotor, and only this is what in the end even allows high speeds.
Depending on specific requirements, the balancing means can essentially be aligned in mirror symmetry relative to the central plane on the one hand, or essentially in point symmetry relative to a center of gravity of the straightening rotor or relative to the midpoint of the straightening rotor on the other. While the center of gravity here represents the theoretical or actual result of a mass distribution of the straightening rotor in an idealized state, the latter is a computed variable based on the spatial distribution of the straightening rotor. It is here understood that deviations from these points can be offset accordingly by the balancing means. Such a symmetrical arrangement is relatively easy to set up, and in particular enables an alignment of both the center of gravity and also a center-of-gravity axis, so as to minimize any unbalances, and thereby permit a maximum speed.
As a consequence, it is advantageous, regardless of the precise arrangement of balancing means, for the latter to be active on the second order, i.e., in particular in relation to the center-of-gravity axis, which should be alignable in its absolute position and direction. The latter can be implemented accordingly in a structurally especially simple manner by using exactly two balancing means that are correspondingly active on the second order.
The balancing means are preferably adjustable during rotation, so that any fluctuations that might arise as the result in particular of migration effects or fluctuations in the work piece can be picked up directly and promptly. It is here understood that adjustable balancing means can also be advantageously used in a straightening rotor during rotation even independently of the remaining features of the present invention.
The balancing means can preferably encompass balancing masses that can be adjusted accordingly during rotation. Such balancing masses can be used to realize an alignment of the center-of-gravity axis in an especially simple and precise manner.
The latter applies in particular when the balancing masses can be shifted in a circumferential direction, which in particular enables a more operationally reliable adjustment even at high speeds than possible for devices according to prior art, since centrifugal forces acting on the balancing masses play no role in motion in the circumferential direction. Accordingly, it is understood that balancing masses that can be shifted in the circumferential direction are advantageous even apart from the remaining features of the present invention.
Balancing masses that can be shifted in the circumferential direction are especially easy to realize by means of balancing disks, wherein an especially simple configuration allows such a balancing disk to exhibit a recess asymmetrically to its central axis, so that the center of gravity or center-of-gravity axis of the balancing disk differs from the central axis. Two such balancing disks can then be used to align the overall center of gravity as desired within a maximum radius defined by the mass eccentricity of the balancing disks. In particular, these types of balancing disks can be correspondingly adjusted in a relatively precise manner, even at high speeds, if required.
The invention further proposes a rotor straightener with a straightening rotor characterized by a device for measuring the unbalance of the straightening rotor. By contrast to prior art, such a device can be used to acquire the unbalance of the straightening rotor in the rotor straightener, so as to also determine influences exerted by the bearings and the like. This ensures a significantly more accurate determination of unbalance, thereby enabling higher speeds.
In particular, it is advantageous for the measuring device to be operational or be able to operate during the straightening process, so that influences arising during the straightening process can also be acquired accordingly.
The measuring device preferably determines unbalances of the second order, so that appropriate balancing means can be used to optimally align the center-of-gravity axis of the straightening rotor.
Since several rotor straighteners are usually utilized in machinery, the measuring device can preferably encompass a decoupleable measurement evaluator, so that the measurement evaluator can be used on several rotor straighteners. This makes it possible to save on costs, wherein even the sensors can be decoupleable in design, if needed.
In addition, the invention proposes a straightening method with a straightening rotor, which is characterized in that the unbalance of the straightening rotor is measured during the straightening process. This makes it possible in particular to determine influences exerted by the work piece or fluctuations arising during the straightening process, so that a center-of-gravity axis can be optimally aligned, as a result of which the speeds can be increased accordingly.
Balancing masses are preferably also adjusted during the straightening process based on the measuring results, so that the straightening motor is, optimally balanced in the appropriate manner during the straightening process.
The latter preferably takes place by defining a center-of-gravity axis, which is then aligned accordingly relative to the rotational axis, preferably via balancing masses.
It is understood that the present invention cannot be used for increasing speeds. At identical speeds, the present invention relieves the material, thereby potentially increasing the service life and allowing operation with lower stabilities. In particular, on-site measurements of unbalance or on-site balancing also makes it possible to significantly reduce the set-up time for a corresponding straightening rotor. In addition, coupling on-site measurement and on-site balancing permits the formation of a corresponding control circuit, which enables an especially precise balancing, in particular without complex theoretical deliberations, but rather based on actually obtained measurement results and unbalances.
In a special embodiment, the straightening rotor preferably encompasses balancing elements that can be positioned by means of a balancing drive relative to the straightening rotor axis, and fixed into position by means of a fixation device, wherein the co-rotating balancing drive and fixation device are linearly accessible from outside, and can be actuated via motion directed around or along this path. In this way, the straightening rotor can be reliably and quickly balanced as needed.
In like manner, the straightening rotor can encompass at least one straightening element that can be radially adjusted by means of an adjustment device, wherein the adjustment device exhibits a co-rotating actuator and a fixation device, and the co-rotating actuator and fixation device can be linearly accessed from outside, and activated via motion directed around or along this path.
Regardless of the features of the present invention, this approach differs from the deliberations regarding automation thus far as to which relatively complex adjustments are required for the rotor. This approach hence falls back on the straightening rotors already known since 1933 from U.S. Pat. No. 1,936,679, and makes it possible to reliably actuate the latter even from an automatic device via the suitable configuration of the co-rotating actuator and fixation unit.
The straightening rotor according to U.S. Pat. No. 1,936,679 hence exhibits lateral clamping screws provided deep inside the rotating frame, which cannot be reliably acquired and activated by an automatic device with a justifiable outlay. A fixation unit for the straightening elements can also not be activated by means of an automatic device in DE 39 10 221 A1 either, since opening the screws that adjust the straightening elements would result in a complete load loss for the screws or straightening elements themselves. Therefore, additional measures are required for activation, for example intermediate fixation of the straightening elements or attachment clamps and screws or the like.
As opposed to considerations relating to prior art, this approach consequently is based on the basic knowledge that, for purposes of automatic adjustment, and hence to achieve a significant improvement and reproducibility of the straightening result, a straightening rotor just be moved into an adjustment position in which an automatic device of the corresponding straightening machine then performs an adjustment from outside. It is understood that such an approach is not necessary in straightening rotors that enable balancing during rotation.
Even independently of the remaining features of the present invention, this approach consequently also proposes a rotor straightener with a straightening rotor having at least one straightening element that can be radially adjusted by means of an adjustment device, wherein the adjustment device encompasses a co-rotating actuator drive and fixation device along with a stationary drive, the straightening of which is characterized in that both the straightening rotor and stationary drive exhibit an adjustment position in which the stationary drive is linked with the actuator drive and/or fixation device, and the stationary drive exhibits an operating position deviating from the adjustment position, in which the straightening rotor can freely rotate. In this way, the straightening element can be adjusted in the adjustment position by the stationary drive, while the stationary drive does not impede rotation of the rotor in the operating position.
Independently of the remaining features of the present invention, this approach consequently also proposes a method for adjusting a straightening element of a straightening rotor, characterized in that, with the straightening rotor shut down, a stationary drive is linked with an actuator drive and/or fixation device of the straightening element, then adjusts, detaches or fixes the straightening element through specific drive actuation, after which the drive and actuator drive are separated.
In regard to the above, this approach differs from the stipulations according to prior art, and also from the balancing means described above, which can be adjusted during rotation, and enable or attempt to enable a die adjustment given a rotating rotor. As a result, the present invention makes it possible to configure a corresponding straightening machine significantly less expensively by comparison to prior art, even though a potential balancing during rotation can also be cost-effectively realized using balancing disks. In addition, the corresponding straightening rotor can be designed to be significantly lighter and better balanced, since a co-running drive is not required for the balancing drive, ensuring higher speeds, and hence a higher performance of the straightening rotor. Further, this approaches provides a relatively more cost-effective way to adjust several, if not all straightening elements by means of an automatic device, if required, which can only be done with considerable outlay, if at all, in known devices.
The actual adjustment process can here take place in such a way that the straightening rotor is initially kept in its adjustment position. The stationary drive can then be correspondingly moved into its adjustment position. Active interaction between the stationary drive and actuator drive or fixation device can then detach the straightening element, shift or adjust it as needed, and/or reattach it.
Accordingly, a rotor straightener with straightening rotor having at least one straightening element that can be radially adjusted by means of an adjustment device is cumulatively or alternatively proposed, in which the adjustment device encompasses a co-rotating actuator drive and a fixation device, as well as a stationary drive, and which is characterized in that the drive train is provided with a separation device between the stationary drive and co-rotating actuator drive or fixation device.
For example, a corresponding separation device can be realized via the head of a screw and the complementary counterpart of a screwdriver. On the other hand, use can also be made of any other detachable connection with which a drive can be detachably linked with a corresponding actuator drive or a corresponding fixation device.
The approach described above can also be used in an immediately understandable manner for a balancing drive and its fixation device.
The actuator drive and/or balancing drive and the fixation device preferably exhibit an identical connection, so that the stationary drive can be shifted as needed to the fixation device and/or actuator drive or a balancing drive and linked thereto. In this way, a single stationary drive can be used for various actuator drives, balancing drives and/or fixation devices. Let it be emphasized in this conjunction that the term “stationary” refers only to the rotation of the straightening rotor. Otherwise, the stationary drive can be shifted along the straightening rotor, for example. For example, this can be accomplished in a particularly easy way from a structural standpoint by means of a linear actuator. In addition, means can also be provided to shift the stationary drive radially in relation to the straightening rotor, so that, when axially positioned in relation to the respective actuator drive or balancing drive and/or the respective fixation device, it can be brought into its adjustment position while linked with the actuating drive or balancing drive and/or fixation device, in which the separation device is closed or linked, for example.
Depending on the specific configuration of the actuator and/or balancing drives and/or fixation device, the latter can also exhibit an identical connection. This can be true in particular when self-locking threads or other self-locking devices are used for the actuator and/or balancing drives, which correspondingly can also serve as the fixation device. On the other hand, somewhat more complex arrangements are conceivable, in which an adjustment, or shifting, along with sufficient fixation tailored to the operating environment can be ensured by way of an identical connection.
As an alternative, the actuator and/or balancing drive and fixation device can also be separate. For example, oppositely acting screws or other threaded arrangements are conceivable, in which loosening one screw makes it possible to shift and/or adjust the straightening element by means of the other screw. Various, specific implementations are possible here as well, based on which a straightening element and/or balancing means or a balancing mass can be adjusted in a structurally simple manner, meaning suitably adjusted and fixated.
Since such straightening rotors rotate at up to 8,000 RPM and more, straightening times are crucial for the adjustment of the straightening elements and/or balancing masses. This holds true in particular when an adjustment takes place with the straightening rotor shut down, since it takes a considerable time before the corresponding speed differences are traversed. This is evidently also the reason behind the efforts to enable adjustment with the straightening rotor running. Contrary to these considerations, this approach led to the realization that the time losses incurred by adjustment with the straightening rotor shut down can be held within limits if the rotational direction of the straightening rotor is retained before and, if necessary, even during the adjustment. In particular, the goal is to avoid a reversal in rotational direction during adjustment. Proceeding in this way makes it possible in particular for an adjustment of straightening elements or balancing masses to take place even with a work piece present in the straightening rotor. Consequently, the work piece is aligned given both an increase and a decrease in speed, but at a lowered throughput, during the acceleration phase already.
However, using an automatic device for adjustment purposes in this approach makes it possible to keep the down time to a minimum, so that adjustment during a shutdown only requires minimal time losses, which only negligibly diminish the advantages described above, in particular an elevated speed, and hence an elevated throughput. It is understood in this conjunction that maintaining the rotational direction before, after and/or during adjustment given a shutdown, as well as adjustment with the work piece already inserted is advantageous for adjusting the straightening elements of a straightening rotor using an automatic device that initiates the adjustment, whether taken separately or together, regardless of the remaining features of the present invention.
Both the straightening rotor and a stationary drive of the straightening machine can preferably exhibit positioning positions in which the stationary drive can link with the balancing drive, so that the drive enables a positioning of the balancing element.
According to the process followed during adjustment, balancing can also take place with the straightening rotor shut down. A drive can here be linked with a balancing drive of a balancing element, after which the balancing element can be positioned by specifically actuating the drive, and the drive and balancing drive can finally be separated again. It is understood that such a balancing process with the straightening rotor built in is advantageous even independently of the remaining features of the present invention. In particular, proceeding in this way involves a minimal intervention in the actual straightening process as already described relative to straightening element adjustment.
As already disclosed with respect to the actuator drive and/or fixation device, it is advantageous for the stationary drive to exhibit an operating position that differs from the balancing position, and allows the straightening rotor to freely rotate. It is also advantageous to provide a separation device in the drive train between the stationary drive and co-rotating balancing drive, so that the stationary drive can be easily separated form the balancing drive.
The balancing drive and actuating drive preferably exhibit the same connection. In this way, the stationary drive can be linked with an actuator drive and/or a fixation device as well as with a balancing drive and, if necessary, its fixation device. As a result, the overall arrangement is cost effective in structural design, and the straightening rotor can be both adjusted and balanced relative to its straightening elements when shut down.
It is understood that the stationary drive can exhibit several different adjustment positions and/or balancing positions, depending on the axial position of the actuator and/or balancing drives or fixation devices. It may also be advantageous for the stationary drive to have a linear actuating device, with which a drivable connecting unit of the stationary drive that can connect the stationary drive with an actuator drive, a fixation device and/or a balancing drive can be axially shifted along the straightening rotor.
Depending on the specific arrangement of the actuator and/or balancing drives or fixation devices and/or balancing drives, the straightening rotor can also exhibit several adjustment positions and/or balancing positions. In this way, an automatic device can be used to easily actuate differently arranged actuator drives, fixation devices and/or balancing drives in the circumferential direction. It is understood that a straightening machine and/or an adjustment method for a straightening machine that provides one or more adjustment positions and/or balancing positions in which an automatic device can execute an adjustment and/or balancing process is also advantageous independently of the remaining features of the present invention.
The straightening rotor preferably encompasses at least one balancing mass, which can be shifted by means of an actuator drive of an adjustable straightening element. In this way, a balancing mass can be shifted at the moment a straightening element is adjusted, thereby countering an unbalance caused by a shifting of the straightening element, at least within certain limits. Even independently of the remaining features, it is understood that such a coupling between the actuator drive and balancing drive is advantageous for a straightening rotor with adjustable straightening elements to minimize the appearance of an unbalance and/or the time needed to compensate for such an unbalance when the straightening element is adjusted. It is also understood that such a balancing mass differs precisely from the freely positionable balancing means.
For example, the actuator drive can encompass a threaded bolt, which shifts both the straightening element and the balancing mass. Such an arrangement is structurally extremely compact, which is advantageous in particular taking into account the structural circumstances and high speeds.
Such a threaded bolt can also exhibit an oppositely running thread with two partial threads, wherein the straightening element is linked with the first of the two partial threads, and the balancing mass is linked with the second of the two partial threads. As the bolt rotates, the straightening element and balancing mass then move in opposite directions, wherein this opposite motion can be used to offset unbalance given a suitable arrangement. Depending on the specific configuration of the straightening rotor, the two partial threads can exhibit varying pitches. Various bolt thicknesses are also possible.
In particular at high rotational speeds, known rotors exhibit weaknesses, regardless of whether the straightening elements can be adjusted or not. These result in an impaired surface of the work piece, so that these straightening rotors cannot be operated at the desired speed, and hence at the desired throughput. To counter this disadvantage, it is proposed that the straightening rotor encompass at least one inlet-side and one outlet-side straightening element, as well as a central straightening element that can be eccentrically arranged in between the two, wherein the inlet-side or the outlet-side straightening element exhibits a multilateral guide, and the central straightening element exhibits a straightening die. This type of arrangement guides the work piece on the inlet side and/or outlet side well enough in particular to avoid oscillations that are generated and increase in strength in rotors in prior art that are operated at increasing speeds and can damage the work piece. On the other hand, the use of a straightening die in the central straightening element that executes the actual bending and straightening process makes it possible to avoid an unnecessarily high material load on the work piece.
In the present conjunction, inlet- and/or outlet-side straightening elements are correspondingly characterized in that they are not radially adjustable in relation to a rotational axis of the straightening rotor and/or are situated on the rotational axis of the straightening rotor. By contrast, central straightening elements are provided eccentrically or adjustably in relation to the rotational axis.
This measure leads to a straightening rotor differing from the straightening rotors in DE 39 10 221 A1 and U.S. Pat. No. 1,936,679, which simply cannot be operated at very high speeds. This is only made possible by the combination of inlet-side and/or outlet-side multilateral guides and the use of a central straightening die, as proposed above. It is here understood that multilateral guides provided both on the inlet side and outlet side are especially advantageous starting at specific speeds.
To minimize the load on the work piece, a roll guide can be provided for the inlet-side and/or the outlet-side straightening element, depending on the specific speed and the speeds encountered there. On the other hand, a crank guide or rigid guide is also conceivable. A roll guide can be realized, for example, by two toroidal rolls, which can also reliably and gently grasp various work piece diameters in an especially simple and uncomplicated manner. As an alternative, three or more oppositely directed rolls can be provided. Several rolls then correspondingly enable the realization of a multilateral guide as well.
Under certain conditions, a multilateral guide can be omitted for an inlet-side and/or outlet-side straightening element, wherein a straightening die is especially suitable in such cases, wherein the latter in particular can have a clearance of under 0.4 mm, preferably under 0.3 mm, so that sufficient guiding can be ensured under certain conditions.
Another central straightening element can preferably be situated between the central straightening element and the inlet-side straightening element or the outlet-side straightening element. This makes it possible to significantly improve the straightening result in relation to simpler arrangements, since more strongly deformed work pieces can be molded to a sufficient extent given a low rotor diameter. This additional central straightening element is preferably also eccentrically mounted to optimize this effect.
To safeguard the material, it is advantageous to design at least one of the central straightening elements, preferably all of them, as a rolling straightening die.
Even independently of the remaining features of the present invention, the configuration of individual straightening elements exhibits the aforementioned advantages, so that the latter also advantageously improve a rotor even independently of these features, in particular when the latter is to be operated at very high speeds.
Further advantages, objectives and characteristics may be gleaned from the following description of attached drawings outline. The drawing shows:
The rotor straightener according to
The straightening elements 7, 8 and 9 are here designed as straightening dies (not numbered) in a manner known in the art. The same also holds true in this exemplary embodiment for the inlet-side and out-let side straightening elements 6 and 10. In the exemplary embodiment according to
Balancing means 20 (exemplarily numbered) are provided at the frame, on the inlet side relative to the inlet-side straightening element 6, and on the outlet side relative to the outlet-side straightening element 10. The balancing means are essentially arranged in mirror symmetry in relation to a central plane (not shown) of the straightening plane (not shown) of the straightening rotor 1, which stands perpendicular on the axis 3, and runs centrally through the straightening element 8.
This makes it possible to manufacture two balancing means that can be aligned and/or positioned freely, in particular independently of the straightening elements. In particular, this makes it possible to easily optimize a center-of-gravity axis in a desired manner relative to the axis 3 on the second order.
In the exemplary embodiments according to
In particular during manual operation, the balancing disks 21A to 21D can be provided with scales, so that the balancing disks 21A to 21D can be set in an operationally reliable manner. The balancing disks 21A to 21D can also be coupled with a motorized drive, which can be fixed into position and act on the balancing disks 21A to 21D from the outside on the one hand, or co-rotate on the other. In this regard, the balancing disks 21A to 21D rotate around the axis 3 of the straightening rotor, so that they can be shifted with nearly no exposure to centrifugal forces.
In addition, the rotor straightener according to
As plainly evident, the measuring device 30 is active during the straightening process, and acquires unbalances of a second order. In particular if the balancing means 20 can be set during rotation, the results of the measuring device 30 can be directly used for balancing, wherein the measurement evaluator 34 should then advantageously not be decoupled. On the other hand, the measurement evaluator can also be used to prescribe an angular setting for the manual adjustment of the balancing disks 21A to 21D.
The straightening machine shown on
In this exemplary embodiment, the straightening elements 107, 108 and 109 are designed as straightening nozzles 115 (exemplarily numbered), wherein these dies are mounted on rolls, in particular to protect the work piece at higher speeds. By contrast, the inlet-side and/or outlet-side straightening elements 106 and 110 exhibit a multilateral guide, which in the present exemplary embodiments is formed by toroidal rolls 111 (exemplarily numbered) with offset axes. Alternatively, a guide with more than two rolls and/or a guide over cranks correspondingly abutting the work piece 2 multilaterally can be provided at this location. The important thing is to provide a multilateral guide on the inlet side or outlet side in the present exemplary embodiment, so that oscillations in the work piece can be avoided, even at high speeds. The axis can also be inclined to impart a feed motion to the work piece 102.
Threaded bolts 112, 113 and 114 (only exemplarily numbered) can be used to adjust the straightening elements 106 to 110 on the frame. In this case, the threaded bolt 112 serves as the actuator drive and fixation device for the rolls 111, while the bolt 113 is used as the actuator unit for the straightening dies 115. The threaded bolt 114 braces the component carrying the respective straightening die 115, as well as the respective threaded bolt 113, thereby fixing the straightening elements 107 to 109 in place. Guiding strips with grooves (not shown) into which sliding projections 116 (exemplarily numbered on
In order to shift the rolls 111, the bolts 112 need only be turned accordingly, wherein the latter have a self-locking design under the present operating conditions. To adjust the straightening dies 115, the threaded bolts 114 are first loosened. The straightening dies 116 are then shifted as desired via the threaded bolt 113. Finally, the threaded bolts 114 are again tightened, and the straightening dies 116 are fixed in position in this way.
In this exemplary embodiment, plates 117 (exemplarily numbered) are provided as the balancing masses for offsetting an unbalance caused by the adjustment, which are also linked with the threaded bolts 113, and guided via projections 118 into the aforementioned grooves. To manifest the corresponding effect, the bolts 113 are provided with a thread in the area of the plates 117 whose pitch deviates form the thread pitch of the remaining bolt. In this way, the plates 117 can perform a movement that is proportional to the straightening dies 116, but varies in strength and/or direction, without a separate drive having to be provided. As a result, an unbalance arising during the adjustment can be compensated with minimal outlay, if only partially depending on the circumstances, so that the set-up time can be minimized.
The ends of the straightening rotor 101 additionally exhibit peripherally distributed balancing elements 119, which are mounted as threaded bolts in radially directed threaded boreholes of lateral walls of the frame 104 used as balancing means 120, and consequently represent actual balancing masses. The straightening rotor 101 can be balanced by turning these balancing elements 119 by the action of the plates 117. The threaded boreholes are here essentially arranged in point symmetry in relation to a central point of the straightening rotor (not shown), wherein the central point lies in a rotational axis of the straightening rotor 101, situated precisely in the middle between the lateral walls.
This makes it possible to provide two balancing means that can be freely aligned and/or positioned, in particular independently of the straightening elements. As a result, a center-of-gravity axis can in particular be easily optimized in the manner desired with respect to the rotational axis.
Bolts 112, 113 and 114 along with bolts 119 each exhibit an identical head, which can be engaged with a connecting piece 121 of the stationary drive 103. To this end, the connecting piece 121 can be shifted radially along the arrow 130 on the one hand, and axially along the arrow 131 relative to the rotor axis by way of a linear actuator device 122 on the other. In this way, the stationary drive 103 can be shifted between an operating position, in which the rotor 101 can freely turn, and various adjustment and balancing positions, in which it engages and/or connects with the respective bolts 112, 113, 114 and 119. As a result, the rotor 101 can present the bolts 112, 113, 114 and 119 to the stationary drive 103 by staying in a suitable rotational position, and be located in the corresponding adjustment or balancing position.
To this extent, the bolts 112, 113, 114 and 119 together with the corresponding threads form the actuator drives, fixation devices and/or balancing drives described above, with which the respective assemblies, straightening elements, fixating elements or balancing elements and/or balancing plates can be shifted and/or fixed in position.
As denoted by an arrow 132, rotating the connecting piece 121 by means of a rotating drive 123 then makes it possible to drive the actuator drives, fixation devices and balancing drives, and shift the bolts 112, 113, 114 and 119 to the extent desired. The connection between the connecting piece 121 and the respective bolt 112, 113, 114 and 119 can be detached again by moving the connecting piece 121 along the arrow 130 away from the rotor 101, wherein the movement along the arrow 130 can be caused solely by the component 123 on the one hand, or by moving the linear actuator device 122 on the other.
| Number | Date | Country | Kind |
|---|---|---|---|
| 10 2007 006 080.9 | Feb 2007 | DE | national |
| 10 2007 026 728.4 | Jun 2007 | DE | national |
