EP1725348B1 - Drive spindle for the main drive of a roll stand - Google Patents
Drive spindle for the main drive of a roll stand Download PDFInfo
- Publication number
- EP1725348B1 EP1725348B1 EP06724203A EP06724203A EP1725348B1 EP 1725348 B1 EP1725348 B1 EP 1725348B1 EP 06724203 A EP06724203 A EP 06724203A EP 06724203 A EP06724203 A EP 06724203A EP 1725348 B1 EP1725348 B1 EP 1725348B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- tappet
- drive spindle
- spindle according
- shaft
- drive
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Not-in-force
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- 230000008878 coupling Effects 0.000 claims abstract description 13
- 238000010168 coupling process Methods 0.000 claims abstract description 13
- 238000005859 coupling reaction Methods 0.000 claims abstract description 13
- 230000005540 biological transmission Effects 0.000 claims abstract 3
- 239000000314 lubricant Substances 0.000 claims description 13
- 239000000463 material Substances 0.000 claims description 9
- 239000002826 coolant Substances 0.000 claims description 4
- 238000010276 construction Methods 0.000 claims description 3
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 claims description 2
- 229910002804 graphite Inorganic materials 0.000 claims description 2
- 239000010439 graphite Substances 0.000 claims description 2
- 238000005096 rolling process Methods 0.000 abstract description 10
- 238000001816 cooling Methods 0.000 description 7
- 238000006073 displacement reaction Methods 0.000 description 5
- 230000000903 blocking effect Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 239000004519 grease Substances 0.000 description 2
- 238000005461 lubrication Methods 0.000 description 2
- 229920000049 Carbon (fiber) Polymers 0.000 description 1
- 240000006829 Ficus sundaica Species 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 239000004917 carbon fiber Substances 0.000 description 1
- 239000002131 composite material Substances 0.000 description 1
- 239000000498 cooling water Substances 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 239000003925 fat Substances 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000020347 spindle assembly Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B35/00—Drives for metal-rolling mills, e.g. hydraulic drives
- B21B35/14—Couplings, driving spindles, or spindle carriers specially adapted for, or specially arranged in, metal-rolling mills
- B21B35/141—Rigid spindle couplings, e.g. coupling boxes placed on roll necks
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B35/00—Drives for metal-rolling mills, e.g. hydraulic drives
- B21B35/14—Couplings, driving spindles, or spindle carriers specially adapted for, or specially arranged in, metal-rolling mills
- B21B35/147—Lubrication of spindle couplings
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/14—Rotary member or shaft indexing, e.g., tool or work turret
- Y10T74/1471—Plural operators or input drives
Definitions
- the invention relates to a drive spindle for the main drive of a roll stand, comprising: a first shaft for transmitting torque from a drive motor to a coupling element, in particular to a splined profile, and a second shaft for transmitting the torque from the coupling element, in particular the splined profile over a hinge to a roll of the roll stand, wherein the rotary joint comprises a roller hit, which is rotatably connected to the roller, and a second spindle head, which is rotatably connected to the second shaft, and wherein the rotational connection between roller hit and spindle head by sliding blocks and a Pin is made, which is rotatably connected to the spindle head, but a tilt angle between the axis of rotation of the roller and the axis of rotation of the second shaft is mounted to allow.
- Drive spindles for the mainframe main drive of this type must often be designed as Axialverschiebesystem to accomplish a length compensation can.
- drive shafts are usually used with universal joints.
- the DE 29 26 710 C2 a shaft assembly with universal joints for roll drive before.
- a propeller shaft without restriction the rotation diameter so that the flexion angle of each universal joint during standstill of the propeller shaft can be limited to an arbitrary value it is proposed that one end of a bolt located in the universal joint is angularly movably received in a radially movable to the coupling axis element of a yoke, while the movable member is fixable in any position with a locking device.
- connection hit with automatic clearance compensation for connecting a roll neck with a drive spindle for a rolling stand known.
- wedge-shaped drivers for the roll neck are provided, which are arranged slidably on two pairwise cooperating, in the connection piece after the inside inclined towards the center and prism angle corresponding to the wedge angle of the driver prism surfaces. This is intended that the play compensation is effective on all sides of the roll neck and able to compensate automatically by wear or when replacing rolls resulting dimensional differences.
- Cardan shafts with universal joints are filigree and thus expensive. Furthermore, it is usually necessary that they have to be maintained in special workshops, which represents a high logistical effort.
- the invention is therefore based on the object, a drive spindle for the main drive of a rolling stand of the type mentioned with a flat-pin spindle equip so that the disadvantages mentioned are prevented. It should also be in the execution of the function of length compensation of the drive spindle a robust, simple design and thus inexpensive and easy to maintain arrangement can be created. The aim is also that the hit with the roller can remain firmly connected.
- the solution of this problem by the invention is characterized in that between the roller hit and the spindle head, which is arranged near the roller, a bearing element for receiving forces in the direction of the axes of the second shaft and the roller is arranged, wherein between the two bearing elements a plunger for transmitting axial forces between the roller hit and the spindle head is arranged.
- a plunger is integrated into the rotary joint, which provides in cooperation with special bearing elements for the Axialkraftübertragung.
- an axial balancing force can thus be transmitted via the ram, whereby the articulated stones in the spindle head only have to transmit the drive torque and are not loaded by the axial force.
- the drive spindle can thus be charged the same, as would be the case without length compensation.
- the hit can remain on the roller.
- An additional spindle head holder is not required.
- a first development of the invention provides that the bearing elements are arranged concentrically to the respective axes of rotation of the roller and the second shaft.
- the bearing elements preferably together with the plunger form a plain bearing point.
- the bearing elements in the contact region with the plunger may have a concave shape in section and the end regions of the plunger may have a convex shape corresponding to the concave shape. It is particularly advantageous if the bearing elements in the contact region with the plunger have, in section, essentially the shape of a hemisphere.
- the pin may be substantially plate-shaped and have a recess for the passage of the plunger.
- the recess preferably has a conical shape, so that the plunger is movable in certain angular limits.
- means may be provided with which the plunger is connected captive with the roller hit and / or with the spindle head.
- the plunger is pin-shaped, d. H. he then has a circular cross-section.
- the ratio of its length to its diameter is preferably between 4 and 10, preferably between 5.5 and 8.5.
- the radius of the hemisphere of bearing elements and plunger is preferably between half and twice the plunger diameter. In general, it applies here that the radii of the contact regions between the bearing elements and the plunger should be made sufficiently large in order to keep wear low. Although the relative movement increases substantially linearly with the radius, the surface pressure decreases quadratically with increasing radius. Therefore, the radius is preferably chosen large.
- a lubricant channel passing through the spindle head opens, via which lubricant can be supplied to the contact region.
- a particularly preferred embodiment of the invention provides that only in the contact region between one of the bearing elements and the plunger of the lubricant channel opens and that the plunger has a longitudinal bore passing through it for conveying lubricant in the region of the other bearing element.
- the bearing elements are made of a self-lubricating material, in particular of such having graphite.
- Balancier For the known application of Balancier concludedn can be arranged on or on the first shaft, a bearing body which is suitable for applying these Balancier mechanism on the second shaft.
- the plunger consists of several interconnected components.
- the plunger may consist of a rod member, at the ends of each a plunger head is arranged.
- the components can be connected to each other with a screw.
- multi-part design of the plunger has the advantage that only one head of the plunger can be replaced when worn.
- a design with a large plunger head may require demountability, because only then can the plunger with its slender central part be inserted through the passage bore in the journal.
- ribs have proven to be preferred, which are preferably arranged in the region of at least one axial end of the plunger.
- the cooling of the spindle and turn the contact point between the plunger and bearing elements is further improved by the fact that the plunger has at least one bore for passing a cooling medium; It is advantageously arranged at least one bore in the axial end region of the plunger. By passing a cooling medium, such as water, so that efficient cooling can be achieved.
- Fig. 1 a and 1 b two drive spindles 1 for driving two rollers 6 can be seen in a rolling stand.
- the drive spindles 1 are driven (right) by drive motors 2.
- the torque of the motors is transmitted to the rollers 6 (left).
- Both drive spindles 1 have two shafts 3 and 5.
- the roller 6 rotates about an axis of rotation 10, which is arranged horizontally.
- the second axis of rotation 11 of the shafts 3 and 5 is present at a small tilt angle ⁇ to the horizontal, the z. B. between 2 ° and 12 °.
- a rotary joint 4 is arranged between the roller 6 and the second shaft. This is done in the manner of a flat pin joint.
- the rotary joint 4 consists of two elements, namely from the roller hit 7 and the spindle head 8, the torsionally stiff, but are pivotally connected to each other.
- a pin (flat pin) 9 is formed, which extends into a corresponding recess in the spindle head 8 and is stored there.
- the second shaft 5 is connected at its end facing away from the rotary joint 4 via a coupling element in the form of a splined profile (see Fig. 2) with the first shaft 3.
- a coupling element in the form of a splined profile (see Fig. 2) with the first shaft 3.
- each bearing element 12, 13 has a dome-shaped concave recess, d. H. a hemispherical shape, as best seen in FIG.
- the radius R of the calotte is between half and twice the ram diameter D. As already mentioned above, the radius R is chosen to be large enough to keep wear low. The surface pressure between the bearing element 12, 13 and plunger 14 is thus kept low.
- a plunger 14 is arranged, which is suitable for transmitting axial forces from one spindle head to the other. This ensures that the pin 9 itself is not acted upon by axial forces; this only has the sliding blocks 9a and 9b, s. Figs. 3 and 4, hold.
- the plunger 14 is designed as a cylindrical pin and formed in its two end regions 15 and 16 corresponding to the dome shape of the bearing elements 12, 13.
- a conical recess 17 is provided, which is suitable for the axial passage of the plunger 14 (see Fig. 5). So that the plunger 14 does not fall apart at separate parts roller hit 7 and spindle head 8, it is arranged captive in the spindle head 8.
- means 18 are provided. As can be seen from Fig. 5, these means 18 consist of a ring 22 which is fixed by means of a securing element 23 on the plunger 14. By a screwed-locking element 24 and by a projection 25 so that the axial freedom of movement of the plunger 14 is limited relative to the spindle head 8.
- a lubricant channel 19 is arranged, the mouth of which lies on the dome surface of the bearing element 13 with the intersection of this surface with the axis of rotation 11.
- grease is supplied under pressure, so that the contact surface between the (right) end 16 of the plunger 14 with the bearing element 13 is well lubricated.
- the plunger 14 is provided with a complete and centrally passing through longitudinal bore 20. Through this hole, grease can get from the right tappet end to the left.
- the plunger 14 undergoes no rotation during operation of the spindle assembly, but it performs a tumbling motion about its longitudinal axis.
- the intended lubricant supply ensures good lubrication of the bearings.
- the friction situation in the bearing point can be favored by the fact that self-lubricating materials are used.
- one of the two pivot points is arranged on the hemispherical ends of the plunger 14 on the roll axis and the other on the spindle axis. Furthermore, it is provided that the radii R are kept small at the ends of the plunger 14 (the above explanations on the choice of radii is made, according to which on the other hand a sufficiently large radius R must be provided to a low surface pressure between the parts and thus a low wear to obtain). On the other hand, the length of the plunger 14 must be sufficiently large. In the exemplary embodiment, it is 400 to 600 mm.
- the two ends of the plunger are close to the center of rotation of the roller-side spindle head.
- a bearing body 21 is arranged (shown in detail in Fig. 6).
- the so-called. Balancing With the balancing, which is already known as such, vertical and horizontal forces can be applied.
- the spindle head 8 With axial displacement of the roller 6 in the direction of the center of the roll stand (to the left), there is a risk that the spindle head 8 is pulled down by the flat pin 9 of the roll impact 7.
- one part of the articulated spindle is pressed with balancing in the direction of the roller 6. Those compressive forces that are not consumed by the friction in length compensation, are forwarded via the plunger 14 to the roller 6. After the axial displacement is finished towards the middle of the frame, the axial Balancierkraft can be reduced.
- the axial balancing force should act in full only at an axial displacement towards the center of the frame. Otherwise, the force on the plunger 14 would double when displaced in the opposite direction. In case of incorrect control of this process, the wear on the plunger 14 and at the bearing points of the bearing elements 12, 13 increases. Slipping of the roller-side spindle head from the hit is, however, unlike previously known solutions not to be feared when the cylinder for horizontal balancing so constructed is that it can only apply pressure forces and when its hydraulic pressure is coupled to the hydraulic pressure on the Axialverschiebezylinder the roller 6.
- the plunger 14 need not only be designed as in FIGS. 3 and 5.
- the plunger 14 consists of several parts, namely of a rod element 26, at the two axial end depending a plunger head 27 and 28 is mounted.
- the two plunger heads 27, 28 are by means of screw 29 on Rod member 28 attached. This results in the possibility of replacing only individual parts, ie only a plunger head when worn.
- the bolted to the rod member 26 plunger head 27 and 28 can be secured with a fuse 31 against unintentional release.
- the friction between the spherical plunger ends and the bearing elements 12, 13 resulting frictional heat can be reduced by a favorable design of the plunger or removed by an internal and / or external cooling with a medium (cooling air, cooling water, etc.).
- Bronzes can be envisaged as material for the bearing elements 12, 13 since they can dissipate the heat very well. However, this material has its limit in wear resistance.
- Carbon fiber composite materials may also be provided as material for the bearing elements 12, 13, which have high-strength properties. However, there are limits due to the relatively poor thermal conductivity of this material. For cooling or lubrication fats can be used, however, should be as temperature stable as possible because of the high temperatures at the contact point between bearing elements 12, 13 and plunger 14.
- the proposed invention is characterized by a perfect kinematics of the components and by a simple and spatially compact design. Thus, a cost-effective implementation is possible.
- An internal and / or external cooling in particular of the contact point between the bearing element 12, 13 and plunger 14 supports the performance of the construction.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolls And Other Rotary Bodies (AREA)
- Rolling Contact Bearings (AREA)
- Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
- Automatic Tape Cassette Changers (AREA)
- Chairs Characterized By Structure (AREA)
- Turning (AREA)
Abstract
Description
Die Erfindung betrifft eine Antriebsspindel für den Hauptantrieb eines Walzgerüsts, die aufweist: eine erste Welle zur Übertragung eines Drehmoments von einem Antriebsmotor zu einem Kupplungselement, insbesondere zu einem Vielkeilprofil, und eine zweite Welle zur Übertragung des Drehmoments von dem Kupplungselement, insbesondere dem Vielkeilprofil, über ein Drehgelenk zu einer Walze des Walzgerüsts, wobei das Drehgelenk einen Walzentreffer aufweist, der mit der Walze drehfest verbunden ist, sowie einen zweiten Spindelkopf aufweist, der mit der zweiten Welle drehfest verbunden ist, und wobei die Drehverbindung zwischen Walzentreffer und Spindelkopf durch Gleitsteine und einen Zapfen hergestellt wird, der mit dem Spindelkopf drehfest verbunden ist, jedoch einen Kippwinkel zwischen der Drehachse der Walze und der Drehachse der zweiten Welle zulassend gelagert ist.The invention relates to a drive spindle for the main drive of a roll stand, comprising: a first shaft for transmitting torque from a drive motor to a coupling element, in particular to a splined profile, and a second shaft for transmitting the torque from the coupling element, in particular the splined profile over a hinge to a roll of the roll stand, wherein the rotary joint comprises a roller hit, which is rotatably connected to the roller, and a second spindle head, which is rotatably connected to the second shaft, and wherein the rotational connection between roller hit and spindle head by sliding blocks and a Pin is made, which is rotatably connected to the spindle head, but a tilt angle between the axis of rotation of the roller and the axis of rotation of the second shaft is mounted to allow.
Antriebsspindeln für den Walzgerüst-Hauptantrieb dieser Art müssen häufig als Axialverschiebesystem ausgebildet sein, um einen Längenausgleich bewerkstelligen zu können. Hierfür werden meist Gelenkwellen mit Kreuzgelenken eingesetzt.Drive spindles for the mainframe main drive of this type must often be designed as Axialverschiebesystem to accomplish a length compensation can. For this purpose, drive shafts are usually used with universal joints.
Aus der
Gleichermaßen schlägt die
Aus der
Eine andere Gestaltung einer Gelenkwelle zum Antrieb einer Walze eines Walzwerks ist aus der
Gelenkwellen mit Kreuzgelenken sind filigran aufgebaut und damit teuer. Ferner ist es meist erforderlich, dass sie in speziellen Werkstätten gewartet werden müssen, was einen hohen logistischen Aufwand darstellt.Cardan shafts with universal joints are filigree and thus expensive. Furthermore, it is usually necessary that they have to be maintained in special workshops, which represents a high logistical effort.
Grundsätzlich kommen statt Kreuzgelenken auch Flachzapfenspindeln in der Antriebsspindel zum Walzen-Antrieb in Frage. Eine solche Lösung geht aus der
Bei dieser Lösung ist es jedoch problematisch bzw. unmöglich, effizient axiale Kräfte über die Flachzapfenspindel zu übertragen, ohne diese über Gebühr zu belasten. Bei einer solchen Konzeption wäre es zwecks Längenausgleichs der Antriebsspindel erforderlich, den motorseitigen Spindelkopf mit Bewegungszylindern auszustatten und diese so zu regeln, dass die Walzen-Axialverschiebung parallel nachgeführt wird. Nur damit wäre sichergestellt, dass der walzenseitige Spindelkopf nicht von der Walze abrutschen kann. Dies stellt nicht nur einen unakzeptablen Aufwand dar; im Falle einer Fehlfunktion wären auch größere Schäden an der Walzanlage zu befürchten.In this solution, however, it is problematic or impossible to transmit efficient axial forces on the flat-pin spindle, without burdening them over charge. In such a design, it would be necessary for the purpose of length compensation of the drive spindle to equip the motor-side spindle head with moving cylinders and to regulate them so that the roller axial displacement is tracked parallel. Only then would it be ensured that the roller-side spindle head can not slip off the roller. This not only represents an unacceptable expense; in the event of a malfunction, greater damage to the rolling mill would be expected.
Der Erfindung liegt daher die Aufgabe zugrunde, eine Antriebsspindel für den Hauptantrieb eines Walzgerüsts der eingangs genannten Art mit einer Flachzapfenspindel so auszustatten, dass die genannten Nachteile verhindert werden. Es soll also auch bei der Ausführung der Funktion des Längenausgleichs der Antriebsspindel eine robuste, einfach aufgebaute und damit preiswerte und einfach zu wartende Anordnung geschaffen werden. Angestrebt wird weiterhin, dass der Treffer mit der Walze fest verbunden bleiben kann.The invention is therefore based on the object, a drive spindle for the main drive of a rolling stand of the type mentioned with a flat-pin spindle equip so that the disadvantages mentioned are prevented. It should also be in the execution of the function of length compensation of the drive spindle a robust, simple design and thus inexpensive and easy to maintain arrangement can be created. The aim is also that the hit with the roller can remain firmly connected.
Die Lösung dieser Aufgabe durch die Erfindung ist dadurch gekennzeichnet, dass zwischen dem Walzentreffer und dem Spindelkopf, der nahe der Walze angeordnet ist, ein Lagerelement zur Aufnahme von Kräften in Richtung der Achsen der zweiten Welle und der Walze angeordnet ist, wobei zwischen den beiden Lagerelementen ein Stößel zur Übertragung von Axialkräften zwischen dem Walzentreffer und dem Spindelkopf angeordnet ist.The solution of this problem by the invention is characterized in that between the roller hit and the spindle head, which is arranged near the roller, a bearing element for receiving forces in the direction of the axes of the second shaft and the roller is arranged, wherein between the two bearing elements a plunger for transmitting axial forces between the roller hit and the spindle head is arranged.
Erfindungsgemäß wird also ein Stößel in das Drehgelenk integriert, der im Zusammenwirken mit speziellen Lagerelementen für die Axialkraftübertragung sorgt.According to the invention, therefore, a plunger is integrated into the rotary joint, which provides in cooperation with special bearing elements for the Axialkraftübertragung.
Wie noch zu sehen sein wird, kann damit eine axiale Balancierkraft über den Stößel weitergeleitet werden, wodurch die Gelenksteine im Spindelkopf lediglich das Antriebsdrehmoment übertragen müssen und nicht von der Axialkraft belastet werden. Die Antriebsspindel kann dadurch gleich hoch belastet werden, wie es ohne Längenausgleich der Fall wäre.As will be seen, an axial balancing force can thus be transmitted via the ram, whereby the articulated stones in the spindle head only have to transmit the drive torque and are not loaded by the axial force. The drive spindle can thus be charged the same, as would be the case without length compensation.
Von Vorteil ist es weiterhin, dass der Treffer auf der Walze verbleiben kann. Eine zusätzliche Spindelkopfhalterung ist nicht erforderlich.It is also advantageous that the hit can remain on the roller. An additional spindle head holder is not required.
Im Falle eines Walzenwechsels ist es schließlich in vorteilhafter Weise nicht erforderlich, ein zusätzliches Sperrelement zu betätigen, z. B. einen Bolzen, wie es im oben diskutierten Stand der Technik gelegentlich vorgesehen ist.In the case of a roll change, it is finally advantageously not necessary to actuate an additional blocking element, for. As a bolt, as provided in the prior art discussed above, occasionally.
Eine erste Fortbildung der Erfindung sieht vor, dass die Lagerelemente konzentrisch zu den jeweiligen Drehachsen der Walze bzw. der zweiten Welle angeordnet sind.A first development of the invention provides that the bearing elements are arranged concentrically to the respective axes of rotation of the roller and the second shaft.
Die Lagerelemente bilden vorzugsweise zusammen mit dem Stößel je eine Gleitlagerstelle. Hierbei können die Lagerelemente im Kontaktbereich mit dem Stößel im Schnitt eine konkave Form und die Endbereiche des Stößels eine zu der konkaven Form korrespondierende konvexe Form aufweisen. Besonders vorteilhaft ist es, wenn die Lagerelemente im Kontaktbereich mit dem Stößel im Schnitt im wesentlichen die Form einer Halbkugel aufweisen.The bearing elements preferably together with the plunger form a plain bearing point. In this case, the bearing elements in the contact region with the plunger may have a concave shape in section and the end regions of the plunger may have a convex shape corresponding to the concave shape. It is particularly advantageous if the bearing elements in the contact region with the plunger have, in section, essentially the shape of a hemisphere.
Der Zapfen kann im Wesentlichen plattenförmig ausgebildet sein und eine Aussparung zum Durchtritt des Stößels aufweisen. Die Aussparung hat dabei bevorzugt eine Kegelform, so dass der Stößel in gewissen Winkelgrenzen beweglich ist.The pin may be substantially plate-shaped and have a recess for the passage of the plunger. The recess preferably has a conical shape, so that the plunger is movable in certain angular limits.
Um einen Walzenwechsel zu erleichtern, können Mittel vorgesehen werden, mit denen der Stößel verliersicher mit dem Walzentreffer und/oder mit dem Spindelkopf verbunden ist.To facilitate a roll change, means may be provided with which the plunger is connected captive with the roller hit and / or with the spindle head.
Mit Vorteil ist der Stößel stiftförmig ausgebildet, d. h. er weist dann einen kreisförmigen Querschnitt auf. Das Verhältnis seiner Länge zu seinem Durchmesser liegt bevorzugt zwischen 4 und 10, vorzugsweise zwischen 5,5 und 8,5. Der Radius der Halbkugel von Lagerelementen und Stößel liegt bevorzugt zwischen dem halben und dem doppelten Stößeldurchmesser. Generell gilt hierbei, dass die Radien der Kontaktbereiche zwischen den Lagerelementen und dem Stößel ausreichend groß ausgebildet sein sollten, um Verschleiß gering zu halten. Zwar vergrößert sich die Relativbewegung im wesentlichen linear mit dem Radius, aber die Flächenpressung nimmt mit wachsendem Radius quadratisch ab. Daher wird der Radius bevorzugt möglich groß gewählt.Advantageously, the plunger is pin-shaped, d. H. he then has a circular cross-section. The ratio of its length to its diameter is preferably between 4 and 10, preferably between 5.5 and 8.5. The radius of the hemisphere of bearing elements and plunger is preferably between half and twice the plunger diameter. In general, it applies here that the radii of the contact regions between the bearing elements and the plunger should be made sufficiently large in order to keep wear low. Although the relative movement increases substantially linearly with the radius, the surface pressure decreases quadratically with increasing radius. Therefore, the radius is preferably chosen large.
Für eine lange Lebensdauer und eine gute Funktionsweise kann vorgesehen werden, dass in den Kontaktbereich zwischen zumindest einem der Lagerelemente und dem Stößel ein den Spindelkopf durchsetzender Schmiermittelkanal mündet, über den dem Kontaktbereich Schmiermittel zugeführt werden kann. Eine besonders bevorzugte Ausgestaltung der Erfindung sieht dabei vor, dass nur in den Kontaktbereich zwischen einem der Lagerelemente und dem Stößel der Schmiermittelkanal mündet und dass der Stößel eine ihn durchsetzende Längsbohrung zum Fördern von Schmiermittel in den Bereich des anderen Lagerelements aufweist.For a long service life and a good mode of operation it can be provided that in the contact region between at least one of the bearing elements and the plunger, a lubricant channel passing through the spindle head opens, via which lubricant can be supplied to the contact region. A particularly preferred embodiment of the invention provides that only in the contact region between one of the bearing elements and the plunger of the lubricant channel opens and that the plunger has a longitudinal bore passing through it for conveying lubricant in the region of the other bearing element.
Auch die Materialauswahl der Komponenten kann so getroffen werden, dass sich gute Reibungseigenschaft ergeben. Mit Vorteil sind daher die Lagerelemente aus einem selbstschmierenden Werkstoff hergestellt, insbesondere aus einem solchen, der Graphit aufweist.The material selection of the components can be made so that good friction property arise. Advantageously, therefore, the bearing elements are made of a self-lubricating material, in particular of such having graphite.
Zur an sich bekannten Aufbringung von Balancierkräften kann auf oder an der ersten Welle ein Lagerkörper angeordnet sein, der zum Aufbringen dieser Balancierkräfte auf die zweite Welle geeignet ist.For the known application of Balancierkräften can be arranged on or on the first shaft, a bearing body which is suitable for applying these Balancierkräfte on the second shaft.
Eine Fortbildung sieht vor, dass der Stößel aus mehreren miteinander verbundenen Bauteilen besteht. Insbesondere kann der Stößel aus einem Stangenelement bestehen, an dessen Enden jeweils ein Stößelkopf angeordnet ist. Die Bauteile können dabei mit einer Schraubverbindung miteinander verbunden sein. Bei mehrteiliger Ausführung des Stößels besteht der Vorteil, dass bei Verschleiß nur ein Kopf des Stößels ausgetauscht werden kann. Eine Ausführung mit großem Stößelkopf setzt unter Umständen eine Demontierbarkeit voraus, weil nur dann der Stößel mit seinem schlanken Mittelteil durch die Durchtrittsbohrung im Zapfen gesteckt werden kann.A training provides that the plunger consists of several interconnected components. In particular, the plunger may consist of a rod member, at the ends of each a plunger head is arranged. The components can be connected to each other with a screw. With multi-part design of the plunger has the advantage that only one head of the plunger can be replaced when worn. A design with a large plunger head may require demountability, because only then can the plunger with its slender central part be inserted through the passage bore in the journal.
Zur besseren Abfuhr von Wärme insbesondere von der Kontaktstelle zwischen Stößel und Lagerelementen haben sich Verrippungen bewährt, die bevorzugt im Bereich mindestens eines axialen Endes des Stößels angeordnet sind. Die Kühlung der Spindel und wiederum der Kontaktstelle zwischen Stößel und Lagerelementen wird ferner dadurch verbessert, dass der Stößel mindestens eine Bohrung zum Durchleiten eines Kühlmediums aufweist; dabei ist mit Vorteil mindestens eine Bohrung im axialen Endbereich des Stößels angeordnet. Durch Durchleiten eines Kühlmediums, beispielsweise von Wasser, kann damit eine effiziente Kühlung erreicht werden.For better dissipation of heat in particular from the contact point between the plunger and bearing elements ribs have proven to be preferred, which are preferably arranged in the region of at least one axial end of the plunger. The cooling of the spindle and turn the contact point between the plunger and bearing elements is further improved by the fact that the plunger has at least one bore for passing a cooling medium; It is advantageously arranged at least one bore in the axial end region of the plunger. By passing a cooling medium, such as water, so that efficient cooling can be achieved.
Mit dem Erfindungsvorschlag wird eine Möglichkeit geschaffen, vorbekannte Flachzapfenspindeln auch für Walzenaxialverschiebesysteme in großen Walzgerüsten besonders gut tauglich zu machen.With the proposed invention, a possibility is created to make well-known flat-pin spindles particularly well suited for Walzenaxialverschiebesysteme in large rolling stands.
In der Zeichnung sind Ausführungsbeispiele der Erfindung dargestellt.
Es zeigen:
- Fig. 1a
- zwei Antriebsspindeln für den Hauptantrieb zweier Walzen eines Walzgerüsts in der Seitenansicht,
- Fig. 1b
- die Draufsicht auf die Antriebsspindeln gemäß Fig. 1 a,
- Fig. 2
- eine vergrößerte Darstellung der beiden Antriebsspindeln gemäß Fig. 1 a,
- Fig. 3
- die Einzelheit "X" gemäß Fig. 2,
- Fig. 4
- den Schnitt B-B gemäß Fig. 1 a,
- Fig. 5
- eine vergrößerte Darstellung des oberen Teils von Fig. 3,
- Fig. 6
- die Einzelheit "Z" gemäß Fig. 2,
- Fig. 7
- eine alternative Ausgestaltung der Erfindung in einer Darstellung gemäß Fig. 5 und
- Fig. 8
- den Stößel in perspektivischer Ansicht.
Show it:
- Fig. 1a
- two drive spindles for the main drive of two rolls of a roll stand in side view,
- Fig. 1b
- the top view of the drive spindles according to FIG. 1 a,
- Fig. 2
- an enlarged view of the two drive spindles according to FIG. 1 a,
- Fig. 3
- the detail "X" of FIG. 2,
- Fig. 4
- the section BB according to FIG. 1 a,
- Fig. 5
- an enlarged view of the upper part of Fig. 3,
- Fig. 6
- the detail "Z" according to FIG. 2,
- Fig. 7
- an alternative embodiment of the invention in a representation of FIG. 5 and
- Fig. 8
- the plunger in perspective view.
In Fig. 1 a und 1 b sind zwei Antriebsspindeln 1 zum Antrieb zweier Walzen 6 in einem Walzgerüst zu sehen. Es sei angemerkt, dass die untere Spindel in den Fig. 1 a, 2, 3 und 4 in einer relativ zur oberen Spindel um 90° verdrehten Lage skizziert ist, um den Aufbau des Systems leichter erkennen zu können. Die Antriebsspindeln 1 werden (rechts) von Antriebsmotoren 2 angetrieben. Das Drehmoment der Motore wird auf die Walzen 6 (links) übertragen. Beide Antriebsspindeln 1 weisen dabei zwei Wellen 3 und 5 auf. Die Walze 6 dreht um eine Drehachse 10, die horizontal angeordnet ist. Indes liegt die zweite Drehachse 11 der Wellen 3 und 5 vorliegend unter einem kleinen Kippwinkel α zur Horizontalen, der z. B. zwischen 2° und 12° beträgt.In Fig. 1 a and 1 b, two drive spindles 1 for driving two
Damit das Drehmoment trotz Kippwinkel α übertragen werden kann, ist zwischen der Walze 6 und der zweiten Welle ein Drehgelenk 4 angeordnet. Dies ist nach Art eines Flachzapfengelenks ausgeführt. Das Drehgelenk 4 besteht dabei aus zwei Elementen, nämlich aus dem Walzentreffer 7 und dem Spindelkopf 8, die drehsteif, jedoch relativ zueinander schwenkbar miteinander verbunden sind. An dem Walzentreffer 7 ist ein Zapfen (Flachzapfen) 9 angeformt, der in eine entsprechende Ausnehmung im Spindelkopf 8 hineinreicht und dort gelagert ist.So that the torque can be transmitted despite the tilt angle α, a
Die zweite Welle 5 ist an ihrem vom Drehgelenk 4 abgewandten Ende über ein Kupplungselement in Form eines Vielkeilprofils (s. Fig. 2) mit der ersten Welle 3 verbunden. Damit kann eine axiale Verschiebung zwischen den Wellen 3 und 5 und damit auch der Walzen 6 realisiert werden.The
Der detaillierte Aufbau des Drehgelenks 4 geht aus den Figuren 3, 4 und 5 hervor.The detailed structure of the
Der Walzentreffer 7 und der Spindelkopf 8 weist im Bereich der jeweiligen Drehachse 10 bzw. 11 ein Lagerelement 12 bzw. 13 auf, das blockförmig ausgebildet und in den Walzentreffer 7 bzw. in den Spindelkopf 8 eingesetzt ist. An der dem jeweils anderen Teil zugewandten Seite weist jedes Lagerelement 12, 13 eine kalottenförmig ausgebildete konkave Ausnehmung auf, d. h. eine Halbkugelform, wie es am besten aus Fig. 5 hervorgeht. Der Radius R der Kalotte beträgt dabei zwischen dem halben und dem doppelten Stößeldurchmesser D. Wie bereits oben erwähnt, wird der Radius R ausreichend groß gewählt, um Verschleiß gering zu halten. Die Flächenpressung zwischen Lagerelement 12, 13 und Stößel 14 wird damit gering gehalten.The roller hit 7 and the
Zwischen den beiden Lagerelementen 12, 13 ist ein Stößel 14 angeordnet, der zur Übertragung von Axialkräften von dem einen Spindelkopf auf den anderen geeignet ist. Damit wird erreicht, dass der Zapfen 9 selber nicht von Axialkräften beaufschlagt wird; dieser muss lediglich die Gleitsteine 9a und 9b, s. Fig. 3 und 4, halten.Between the two bearing
Der Stößel 14 ist als zylindrischer Stift ausgebildet und in seinen beiden Endbereichen 15 und 16 korrespondierend zur Kalottenform der Lagerelemente 12, 13 ausgeformt.The
Im Zapfen 9 ist dabei eine kegelförmig ausgebildete Aussparung 17 vorgesehen, die zum axialen Durchtritt des Stößels 14 geeignet ist (s. Fig. 5). Damit der Stößel 14 bei voneinander getrennten Teilen Walzentreffer 7 und Spindelkopf 8 nicht herausfällt, ist er verliersicher im Spindelkopf 8 angeordnet. Hierfür sind Mittel 18 vorgesehen. Wie Fig. 5 entnommen werden kann, bestehen diese Mittel 18 aus einem Ring 22, der mittels eines Sicherungselements 23 auf dem Stößel 14 festgelegt ist. Durch ein angeschraubtes Sperrelement 24 sowie durch einen Vorsprung 25 ist damit die axiale Bewegungsfreiheit des Stößels 14 relativ zum Spindelkopf 8 beschränkt.In the
Um einen zuverlässigen Betrieb des Systems zu gewährleisten, ist sicherzustellen, dass die Gleitpaarung Lagerelement - Stößel hinreichend mit Schmierstoff versorgt wird. Im Spindelkopf 8 ist hierzu ein Schmiermittelkanal 19 angeordnet, dessen Mündung an der Kalottenoberfläche des Lagerelements 13 mit dem Schnittpunkt dieser Oberfläche mit der Drehachse 11 liegt. Dort wird Schmierfett unter Druck zugeführt, so dass die Kontaktfläche zwischen dem (rechten) Ende 16 des Stößels 14 mit dem Lagerelement 13 gut geschmiert wird. Damit auch die andere Lagerstelle, d. h. die Kontaktfläche zwischen dem (linken) Ende 15 des Stößels 14 mit dem Lagerelement 12 mit Schmiermittel versorgt wird, ist der Stößel 14 mit einer ihn komplett und zentrisch durchsetzenden Längsbohrung 20 versehen. Durch diese Bohrung kann Schmierfett vom rechten Stößelende zum linken gelangen.In order to ensure reliable operation of the system, it must be ensured that the sliding bearing bearing element ram is adequately supplied with lubricant. In the
Der Stößel 14 erfährt im Betrieb der Spindelanordnung keine Drehung, sondern er vollzieht eine Taumelbewegung um seine Längsachse. Die vorgesehene Schmiermittelversorgung stellt eine gute Schmierung der Lagerstellen sicher. Begünstigt kann die Reibungssituation in der Lagerstelle dadurch werden, dass selbstschmierende Werkstoffe verwendet werden.The
Beim Ein- und Ausbau der Walze 6 wird der Flachzapfen 9 des Walzentreffers 7 in den Spindelkopf 8 geschoben. Der Stößel 14 wird - wie erläutert - verliersicher im Spindelkopf 8 gehalten. Beim Einfahren einer neuen Walze zentriert sich das eine (linke) Ende des Stößels 14 in der Kalotte des Lagerelements 12.When installing and removing the
Wie aus Fig. 5 zu entnehmen ist, ist vorgesehen, dass einer der beiden Drehpunkte an den halbkugelförmigen Enden des Stößels 14 auf der Walzenachse und der andere auf der Spindelachse angeordnet ist. Weiterhin ist vorgesehen, dass die Radien R an den Enden des Stößels 14 klein gehalten werden (auf die obigen Ausführungen zur Radienwahl wird hingewiesen, wonach andererseits ein hinreichend großer Radius R vorgesehen werden muss, um eine geringe Flächenpressung zwischen den Teilen und damit einen geringen Verschleiß zu erhalten). Andererseits muss die Länge des Stößels 14 hinreichend groß sein. Im Ausführungsbeispiel beträgt sie 400 bis 600 mm. In vorteilhafter Weise liegen auch die beiden Enden des Stößels nahe am Drehzentrum des walzenseitigen Spindelkopfes. Die Relativbewegungen in den Kontaktbereichen zwischen Lagerelementen 12, 13 und Stößel 14 sind am kleinsten, wenn der Stößel 14 mittig zum Drehzentrum des Spindelkopfes eingebaut wird. Ein kalottenförmiges Stößelende, das genau in diesem Drehzentrum liegen würde, würde eine Relativbewegung in Form einer Taumelbewegung entsprechend dem Kippwinkel α der Spindel erfahren, während das andere Stößelende keiner Relativbewegung unterliegen würde. Sind die Stößelenden mittig zum bzw. gleich weit entfernt vom Drehzentrum des Spindelkopfes angeordnet, erfahren sie jeweils Relativdrehungen entsprechend dem halben Spindelwinkel.As can be seen from Fig. 5, it is provided that one of the two pivot points is arranged on the hemispherical ends of the
Um einerseits eine hohe Funktionssicherheit des Systems zu erreichen und andererseits die Gefahr von Knickung des Stößels 14 zu verhindern, liegt das Verhältnis der Länge L des Stößels 14 zu seinem Durchmesser D - s. Fig. 5 - zwischen 4 und 10, vorzugsweise zwischen 5,5 und 8,5.On the one hand to achieve high reliability of the system and on the other hand to prevent the risk of buckling of the
In Fig. 1 a bzw. 1 b ist zu sehen, dass im (rechten) Endbereich der axial beweglich angeordneten Welle 5 ein Lagerkörper 21 angeordnet ist (im Detail in Fig. 6 dargestellt). Auf den nicht mitdrehenden Teil des Lagerkörpers 21, also auf den außen angeordneten Teil des Körpers, wirkt ein nicht dargestelltes Hebelwerk, die sog. Balancierung. Mit der Balancierung, die als solche vorbekannt ist, können vertikale und horizontale Kräfte aufgebracht werden. Bei axialer Verschiebung der Walze 6 in Richtung Mitte des Walzgerüsts (nach links) besteht die Gefahr, dass der Spindelkopf 8 vom Flachzapfen 9 des Walzentreffers 7 heruntergezogen wird. Um dies zu vermeiden, wird der eine Teil der Gelenkspindel mit der Balancierung in Richtung Walze 6 gedrückt. Diejenigen Druckkräfte, die nicht von der Reibung im Längenausgleich aufgezehrt werden, werden über den Stößel 14 auf die Walze 6 weitergeleitet. Nachdem die Axialverschiebung in Richtung Gerüstmitte beendet ist, kann die axiale Balancierkraft vermindert werden.In Fig. 1 a and 1 b can be seen that in the (right) end portion of the axially
Die axiale Balancierkraft sollte in voller Höhe nur bei einer Axialverschiebung in Richtung Gerüstmitte wirken. Bei der Verschiebung in die Gegenrichtung würde sich ansonsten die Kraft auf den Stößel 14 verdoppeln. Bei fehlerhafter Steuerung dieses Vorgangs erhöht sich der Verschleiß am Stößel 14 bzw. an den Lagerstellen der Lagerelemente 12, 13. Ein Abrutschen des walzenseitigen Spindelkopfes vom Treffer ist jedoch im Gegensatz zu vorbekannten Lösungen nicht zu befürchten, wenn der Zylinder für die horizontale Balancierung so konstruiert ist, dass er nur Druckkräfte aufbringen kann und wenn sein Hydraulikdruck mit dem Hydraulikdruck auf den Axialverschiebezylinder der Walze 6 gekoppelt ist.The axial balancing force should act in full only at an axial displacement towards the center of the frame. Otherwise, the force on the
In Fig. 7 und Fig. 8 ist zu sehen, dass der Stößel 14 nicht nur wie in Fig. 3 und Fig. 5 ausgeführt sein muss. Bei der Lösung gemäß Fig. 7 und 8 besteht der Stößel 14 aus mehreren Teilen, nämlich aus einem Stangenelement 26, an dessen beiden axialen Ende je ein Stößelkopf 27 bzw. 28 angebracht ist. Die beiden Stößelköpfe 27, 28 sind dabei mittels Schraubverbindungen 29 am Stangenelement 28 befestigt. Dadurch ergibt sich die Möglichkeit, bei Verschleiß nur einzelne Teile, d. h. nur einen Stößelkopf auszutauschen.It can be seen in FIGS. 7 and 8 that the
Der am Stangenelement 26 angeschraubte Stößelkopf 27 bzw. 28 kann dabei mit einer Sicherung 31 vor unbeabsichtigtem Lösen gesichert werden.The bolted to the
Eine Verbesserung der Kühlung wird bei der Lösung gemäß Fig. 7 und Fig. 8 dadurch erreicht, dass eine Verrippung 30 - hier nur für den Stößelkopf 27 realisiert - am Stößelkopf 28 angeordnet ist. Damit wird, wie bekannt, die wärmeabführende Fläche vergrößert.An improvement in the cooling is achieved in the solution according to FIG. 7 and FIG. 8 in that a ribbing 30 - realized here only for the plunger head 27 - is arranged on the
Die zwischen den sphärischen Stößelenden und den Lagerelementen 12, 13 entstehende Reibwärme kann durch eine günstige Gestaltung des Stößels vermindert oder durch eine Innen- und/oder Außenkühlung mit einem Medium (Kühlluft, Kühlwasser, etc.) abgeführt werden. Es können Bronzen als Material für die Lagerelemente 12, 13 ins Auge gefasst werden, da diese sehr gut die Wärme ableiten können. Allerdings hat dieses Material seine Grenze in der Verschleißfestigkeit. Es können auch Kohlefaserverbundwerkstoffe als Material für die Lagerelemente 12, 13 vorgesehen werden, die hochfeste Eigenschaften aufweisen. Dort bestehen jedoch Grenzen aufgrund der relativ schlechten Wärmeleitfähigkeit dieses Materials. Zur Kühlung bzw. Schmierung können Fette eingesetzt werden, die allerdings wegen der hohen Temperaturen an der Kontaktstelle zwischen Lagerelementen 12, 13 und Stößel 14 möglichst temperaturstabil sein sollten.The friction between the spherical plunger ends and the bearing
Der Erfindungsvorschlag zeichnet sich durch eine einwandfreie Kinematik der Komponenten und durch eine einfache und räumlich kompakte Bauart aus. Somit ist eine kostengünstige Realisierung möglich. Eine Innen- und/oder Außenkühlung insbesondere der Kontaktstelle zwischen Lagerelement 12, 13 und Stößel 14 unterstützt die Leistungsfähigkeit der Konstruktion.The proposed invention is characterized by a perfect kinematics of the components and by a simple and spatially compact design. Thus, a cost-effective implementation is possible. An internal and / or external cooling in particular of the contact point between the bearing
- 11
- Antriebsspindeldrive spindle
- 22
- Antriebsmotordrive motor
- 33
- erste Wellefirst wave
- 44
- Drehgelenkswivel
- 55
- zweite Wellesecond wave
- 66
- Walzeroller
- 77
- WalzentrefferWalz hits
- 88th
- walzenseitiger Spindelkopfroller-side spindle head
- 99
- Flachzapfenflat journal
- 9a9a
- Gleitsteinslide
- 9b9b
- Gleitsteinslide
- 1010
- Drehachse der WalzeRotary axis of the roller
- 1111
- Drehachse der zweiten WelleRotary axis of the second shaft
- 1212
- Lagerelementbearing element
- 1313
- Lagerelementbearing element
- 1414
- Stößeltappet
- 1515
- Endbereich des StößelsEnd region of the plunger
- 1616
- Endbereich des StößelsEnd region of the plunger
- 1717
- Aussparungrecess
- 1818
- Mittel zum verliersicheren Anordnen des StößelsMeans for captive placing the plunger
- 1919
- Schmiermittelkanallubricant channel
- 2020
- Längsbohrunglongitudinal bore
- 2121
- Lagerkörper für BalancierungBearing body for balancing
- 2222
- Ringring
- 2323
- Sicherungselementfuse element
- 2424
- Sperrelementblocking element
- 2525
- Vorsprunghead Start
- 2626
- Stangenelementbar member
- 2727
- Stößelkopfram head
- 2828
- Stößelkopfram head
- 2929
- Schraubverbindungscrew
- 3030
- Verrippungribbing
- 3131
- Sicherungfuse
- αα
- Kippwinkeltilt angle
- LL
- Länge des StößelsLength of the plunger
- DD
- Durchmesser des StößelsDiameter of the plunger
- RR
- Radiusradius
Claims (21)
- Drive spindle (1) for the main drive of a roll stand, which comprises:a first shaft (3) for transmission of a torque, drive motor (2) to a coupling element, particularly to a spline, anda second shaft (5) for transmitting the torque from the coupling element, particularly the spline, by way of a rotary joint (4) to a roller (6) of the roll stand,wherein the rotary joint (4) comprises a coupling sleeve (7), which is connected in rotationally fast manner with the roll (6), as well as a spindle head (8), which is connected in rotationally fast manner with the second shaft (5), and
wherein the rotary connection between coupling sleeve (7) and spindle head (8) is produced by slide blocks and a pin (9), which is connected in rotationally fast manner with the spindle head (8), but is mounted to permit a tilt angle (α) between the axis (10) of rotation of the roll (6) and the axis (11) of rotation of the second shaft (5),
characterised in that
a bearing element (12, 13) for acceptance of forces in the direction of the axes of the second shaft (5) and the roll (6) is arranged between the coupling sleeve (7) and the spindle head (8), wherein a tappet (14) for transmission of axial forces between the coupling sleeve (7) and the spindle head (8) is arranged between the two bearing elements (12, 13). - Drive spindle according to claim 1, characterised in that the bearing elements (12, 13) are arranged concentrically with respect to the respective axes (10, 11) of rotation of the roll (6) and the second shaft (5).
- Drive spindle according to claim 1 or 2, characterised in that the bearing elements (12, 13) together with the tappet (14) each form a respective slide bearing point.
- Drive spindle according to one of claims 1 to 3, characterised in that the bearing elements (12, 13) have in section a concave form in the contact region with the tappet (14) and the edge regions (15, 16) of the tappet (14) have a convex form corresponding with the concave form.
- Drive spindle according to claim 4, characterised in that the bearing elements (12, 13) have in section substantially the form of a hemisphere in the contact region with the tappet (14).
- Drive spindle according to one of claims 1 to 5, characterised in that the pin (9) is of substantially plate-shaped construction and has a cut-out (17) for passage of the tappet (14).
- Drive spindle according to claim 6, characterised in that the cut-out (17) has a conical form.
- Drive spindle according to one of claims 1 to 7, characterised by means (18) by which the tappet (14) is captively connected with the coupling sleeve (7) and/or with the spindle head (8).
- Drive spindle according to one of claims 1 to 8, characterised in that the tappet (14) is of pin-shaped construction.
- Drive spindle according to claim 8, characterised in that the ratio of the length (L) of the tappet (14) to its diameter (D) lies between 4 and 10, preferably between 5.5 and 8.5.
- Drive spindle according to one of claims 5 to 10, characterised in that the radius (R) of the hemisphere of bearing elements (12, 13) and tappet (14) lies between half and twice the tappet diameter (D).
- Drive spindle according to one of claims 1 to 11, characterised in that communicating with the contact region between at least one of the bearing elements (12, 13) and the tappet (14) is a lubricant channel (19) which penetrates the spindle head (8) and by way of which lubricant can be fed to the contact region.
- Drive spindle according to claim 12, characterised in that the lubricant channel (19) opens only in the contact region between one of the bearing elements (13) and the tappet (14) and that the tappet (14) has a longitudinal bore (20), which passes through it, for conveying lubricant to the region of the other bearing element (12).
- Drive spindle according to one of claims 1 to 13, characterised in that the bearing elements (12, 13) consist of a self-lubricating material, particularly of a material comprising graphite.
- Drive spindle according to one of claims 1 to 14, characterised in that a bearing body (21) is arranged on or at the first shaft (3) and is suitable for applying balancing forces to the second shaft (5).
- Drive spindle according to one of claims 1 to 15, characterised in that the tappet (14) consists of several components (26, 27, 28) connected together.
- Drive spindle according to claim 16, characterised in that the tappet (14) consists of a rod element (26), at each of the ends of which a respective tappet head (27, 28) is arranged.
- Drive spindle according to claim 16 or 17, characterised in that the components (26, 27, 28) are connected together by a screw connection (29).
- Drive spindle according to one of claims 1 to 18, characterised in that the tappet (14) has ribs (30) particularly in the region of its axial ends.
- Drive spindle according to one of claims 1 to 19, characterised in that the tappet (14) has at least one bore for conducting through a coolant.
- Drive spindle according to claim 20, characterised in that at least one bore for conducting through a coolant extends in the axial end region of the tappet (14).
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102005016629 | 2005-04-12 | ||
DE102005054742A DE102005054742A1 (en) | 2005-04-12 | 2005-11-17 | Drive spindle for the main drive of a rolling stand |
PCT/EP2006/003271 WO2006108596A1 (en) | 2005-04-12 | 2006-04-10 | Drive spindle for the main drive of a roll stand |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1725348A1 EP1725348A1 (en) | 2006-11-29 |
EP1725348B1 true EP1725348B1 (en) | 2008-01-16 |
Family
ID=36686042
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06724203A Not-in-force EP1725348B1 (en) | 2005-04-12 | 2006-04-10 | Drive spindle for the main drive of a roll stand |
Country Status (10)
Country | Link |
---|---|
US (1) | US7784380B2 (en) |
EP (1) | EP1725348B1 (en) |
JP (1) | JP4040670B2 (en) |
AT (1) | ATE383917T1 (en) |
BR (1) | BRPI0604834A (en) |
CA (1) | CA2568837C (en) |
DE (2) | DE102005054742A1 (en) |
ES (1) | ES2297824T3 (en) |
RU (1) | RU2339472C2 (en) |
WO (1) | WO2006108596A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102009014101A1 (en) | 2009-03-20 | 2010-09-23 | Sms Siemag Aktiengesellschaft | Safety clutch for e.g. drain chain of roll stand in roller mill, has friction pairs formed between region of component and piston of piston cylinder unit i.e. hydraulic unit, where piston is displaceably arranged in housing |
DE102009014102A1 (en) | 2009-03-20 | 2010-09-23 | Sms Siemag Aktiengesellschaft | Safety clutch e.g. friction ring safety clutch, for protecting drive strand of cutter in rolling mill against overloading, has adjusting unit provided for bracing housing parts relative to each other in axial direction |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102009031324A1 (en) * | 2009-06-30 | 2011-01-05 | Voith Patent Gmbh | Roller drive and rolling stand with such |
ITMI20130287A1 (en) | 2013-02-27 | 2014-08-28 | Danieli Off Mecc | ELASTIC JOINT FOR PUNCHES |
DE102013221593A1 (en) * | 2013-09-19 | 2015-04-02 | Voith Patent Gmbh | Removable clutch hub for work rolls of rolling mill drives with automatic relubrication |
CN104723169B (en) * | 2015-03-27 | 2017-01-04 | 苏州江源精密机械有限公司 | Automatic indexing right-angle head device on gantry machining center |
AU2019202833B2 (en) * | 2018-04-24 | 2024-04-11 | David Robertson | A roll-over protection apparatus |
DE202019104904U1 (en) | 2019-09-05 | 2019-12-09 | Danieli & C. Officine Meccaniche S.P.A. | Articulated device for connecting a spindle to a flange for transferring the drive from a motor to one or more roller rolls |
US20230390816A1 (en) | 2020-11-17 | 2023-12-07 | Primetals Technologies Japan, Ltd. | Gear spindle device for rolling mill, rolling mill facility, and method of cooling gear spindle device for rolling mill |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
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US2332859A (en) * | 1938-08-30 | 1943-10-26 | Kreissig Ernst | Shaft coupling |
US2430683A (en) * | 1945-10-30 | 1947-11-11 | Morgan Construction Co | Wabbler coupling |
NL247235A (en) * | 1959-01-16 | |||
DE2362524A1 (en) | 1973-12-15 | 1975-06-26 | Schloemann Siemag Ag | Coupling of driving spindles to rolls on rolling mills - using socket with radial indexing pegs for rapid coupling |
DE3811790A1 (en) | 1988-01-15 | 1989-07-27 | Schloemann Siemag Ag | ROLLING MACHINE DRIVE WITH ARC TOOTH ARM SPINDLE |
AT405619B (en) * | 1995-04-25 | 1999-10-25 | Voest Alpine Ind Anlagen | ROLLING STAND |
IT1280192B1 (en) * | 1995-06-26 | 1998-01-05 | Danieli Off Mecc | AXIAL TRANSLATION DEVICE FOR ROLLING CYLINDERS AND AXIAL TRANSLATION PROCEDURE WITH CROSSING DISPLACEMENT OF THE |
IT1315121B1 (en) * | 2000-09-25 | 2003-02-03 | Danieli Off Mecc | DEVICE TO ABSORB THE AXIAL LOADS GENERATED ON THE CYLINDERS OF A ROLLING CAGE |
DE10211883C1 (en) | 2002-03-18 | 2003-12-18 | Spicer Gelenkwellenbau Gmbh | Universal joint, for the universal joint shaft in the drive of a rolling mill, has a structured holding bolt at the second base with a support surface against laying surfaces of the bridge at the first fork |
-
2005
- 2005-11-17 DE DE102005054742A patent/DE102005054742A1/en not_active Withdrawn
-
2006
- 2006-04-10 BR BRPI0604834-0A patent/BRPI0604834A/en not_active IP Right Cessation
- 2006-04-10 WO PCT/EP2006/003271 patent/WO2006108596A1/en active IP Right Grant
- 2006-04-10 DE DE502006000297T patent/DE502006000297D1/en active Active
- 2006-04-10 AT AT06724203T patent/ATE383917T1/en active
- 2006-04-10 US US11/596,936 patent/US7784380B2/en not_active Expired - Fee Related
- 2006-04-10 CA CA2568837A patent/CA2568837C/en not_active Expired - Fee Related
- 2006-04-10 ES ES06724203T patent/ES2297824T3/en active Active
- 2006-04-10 RU RU2006139747/02A patent/RU2339472C2/en not_active IP Right Cessation
- 2006-04-10 JP JP2007512225A patent/JP4040670B2/en not_active Expired - Fee Related
- 2006-04-10 EP EP06724203A patent/EP1725348B1/en not_active Not-in-force
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102009014101A1 (en) | 2009-03-20 | 2010-09-23 | Sms Siemag Aktiengesellschaft | Safety clutch for e.g. drain chain of roll stand in roller mill, has friction pairs formed between region of component and piston of piston cylinder unit i.e. hydraulic unit, where piston is displaceably arranged in housing |
DE102009014102A1 (en) | 2009-03-20 | 2010-09-23 | Sms Siemag Aktiengesellschaft | Safety clutch e.g. friction ring safety clutch, for protecting drive strand of cutter in rolling mill against overloading, has adjusting unit provided for bracing housing parts relative to each other in axial direction |
Also Published As
Publication number | Publication date |
---|---|
EP1725348A1 (en) | 2006-11-29 |
BRPI0604834A (en) | 2007-12-18 |
ATE383917T1 (en) | 2008-02-15 |
US20070251349A1 (en) | 2007-11-01 |
DE502006000297D1 (en) | 2008-03-06 |
CA2568837C (en) | 2013-06-04 |
CA2568837A1 (en) | 2006-10-19 |
DE102005054742A1 (en) | 2006-10-19 |
JP2007538204A (en) | 2007-12-27 |
RU2006139747A (en) | 2008-06-20 |
RU2339472C2 (en) | 2008-11-27 |
ES2297824T3 (en) | 2008-05-01 |
JP4040670B2 (en) | 2008-01-30 |
WO2006108596A1 (en) | 2006-10-19 |
US7784380B2 (en) | 2010-08-31 |
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