JPS6010805B2 - cluster mill - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION In contrast to multi-roll mills such as 20-roll mills, for example, in cluster mills called six-tier mills, the drive is directly driven because there is no intermediate roll between the work roll and the rear casters. The work roll is saturated.

It is clear that in a normal drive, the spindle that transmits torque from the pinion stand to the work roll can only be used up to the same diameter as the work roll, so the neck of the work roll must be small, so the torque produced by this drive is It is subject to severe limitations as far as its ability to communicate is concerned. This difficulty can be overcome in part by motors placed on either side of the mill, driving each work roll separately from its own motor through a spindle.

However, this imposes the difficulty of changing rolls and also wastes space. These difficulties are solved with an individual roll drive that transmits torque to each work roll through a pair of bevel gears from a vertical shaft coupled to a motor mounted directly on the top of the mill housing.

However, this is because the elongated work roll cannot withstand the reaction force from the tooth pressure of the bevel gear, and on top of that the weight of the gearbox itself, which must of course follow the axial movement of the work roll dictated by the screw down. There is a problem because there is no way to withstand it. In accordance with the present invention, a fully floating right angle gearbox, preloaded to make the gearbox weightless and thus transmitting only pure torque to the work rolls, is suspended from the housing by a floating lever structure.

The present invention allows the mill to be instantaneously converted to roll work-hardened strips that would normally be unable to be further rolled without being anchored.

This is done by inserting an additional roll opposing the rear casters on one side of the mill, and by adding a floating roll between the additional roll mentioned above and the two work rolls, so that the strip has three This is achieved by having a continuous roll path. This roll geometry allows the use of work rolls of the required diameter for rolling hard materials.
The mill of the invention comprises two class mills and two additional rolls juxtaposed one on top of the other and in the plane of symmetry of each mill and preferably mounted on rotatable cylindrical bearings. It can be converted into a high-capacity tandem mill by placing a bag rack inside.

This type of mill is self-inserting, i.e. the feed V feed button allows the strip to enter the mill inlet straight, and once it has passed through to the winder, the bearings of both mills are simultaneously rotated 180 degrees to the left and right.
0 times, making the strip material mirror double S-shaped. In this way, six continuous passages are created in one strip through the mill. The pinion 12 (Fig. 3) is connected to its drive motor (
(not shown) and is shown integrally with its splined shaft 12' for connection with a suitable spindle.

This meshes with a bevel gear 13, the shaft 14 of which is hollow to accommodate the end of the roll 1', and is provided with a keyway 15 for a key 16, through which torque is transferred from the drive motor to the work roll 1'. tell to. Appropriate bearings are provided on both sides within the transmission box 20.

The vertical freedom of movement of the box 20, so that it follows the position of the work roll 1', is ensured by the fact that it is rotatably mounted on the bracket 17 by means of two pins 21. The bracket 17 is attached to the mill housing 5 (first and second
It is supported by its trunnion 18 in two bearings 19 mounted on the trunnion 18 (see figure). The trunnion 18 is also free to slide in its bearing 19 in the track line direction to follow any lateral movement of the work roll 1'. It is noted that this suspension, in addition to freely following the position of the work roll 1', also absorbs two torque reactions: [1] from the work roll and [2] from the motor.

A lever 23 is attached to one of the trunnions 18 to prevent the work roll from carrying the weight of the transmission box.
The spring 24 based on the mill housing is attached to the bracket 1.
Test bar 23 for applying torque that can be easily controlled to 7.
, which in turn exerts an appropriate lifting force through the two pins 21 to counteract the weight of the box 20'. This drive method has the advantage of transmitting torque to the work roll 1' with one or more keys without the limitations of having to provide a small diameter section in the neck of the roll. This arrangement allows the use of the smallest work roll that the mill geometry allows.

In this configuration, the diameter of the work roll is caster 3 (5th
It can be made smaller than 40% of the diameter of
This 40% is the normal limit for class mills. By comparison, conventional mill spindles require small diameter work roll necks which reduce the maximum transmittable torque. This can be tolerated with large diameter work rolls, but severely reduces capacity in mills with small work rolls. Moreover, this transmission makes it possible to change the working roll very far by pulling it straight through the hole provided in the shaft 14.

Moreover, this concept makes it possible to attach to the reaction box 20 a device for slowly vibrating the work roll in the track direction.

This solves the vexing problem of using spaced casters with fixed supports in between to support the rolls, somewhat reducing the value of cluster and other mills. Such casters rub the surface of the roll to a matte finish, while those places facing the support where nothing touches the roll are likewise not matte. By vibrating the roll, depending on its hardness and quality, over a small distance, say every 5 minutes, about half the width of the caster, these matting spots are eliminated and the entire roll has a uniform finish. As a result, the strip produced by the mill also has a uniform finish across its entire cross section, rather than the conventional matte strip. This oscillation is achieved by mounting on the work roll a screw 26 rotating therewith and connected in the ratchet direction with a nut 27 to a box 25 firmly bolted to the shaft 14.

Turning the nut 27 with respect to the screw 26 causes the roll 1' attached to the screw 26 to move in the axial direction. This rotation is accomplished using a modified ratchet-claw principle. The nut 27 is a double stationary gear 2 rotatably mounted on the box 25.
9 by a key 28. The teeth on the left side 29' are cut in the opposite direction to the teeth on the right side 29'' (FIG. 3).

Turning the gear 29 with the nut 27 with respect to the screw 26 occurs in one direction with the two elbow-shaped pawls 30 and in the opposite direction with the other pawl 31. Each pawl consists of two legs 30', 30^ with an elbow joint 36 between them, and a spring 35 tensioning the two legs together. This results in rotation about the elbow joint 36 and contact of the legs with each other. The pawl 31 is shown in the "closed" position, here attached to the fulcrum pin 32 on the monopod.
and the tooth 33 of the other leg is the shortest.

The cam-shaped outer surface of the pawl 30 engages the roller 37 once per revolution of the work roll 1, and the bag is rotatably mounted on a shaft 38 mounted in a bracket 39 mounted on the box 2. It is suspended. This kind of engagement means that the teeth of the claw are on the left side 2.
The pawl 30 is first rotated about the fulcrum pin 32 and against the effect of the spring 34 until it engages the teeth of 9. The roller 37 then straightens the elbow of the pawl 30, thereby increasing the distance between the pin 32 and the tooth 33. This causes the nut 27 to rotate relative to the screw 26 by one or more teeth, depending on the adjustment of the respective parts. When the mill operates as a reversing mill, and when the rolls are reversed at the end of the coil, the rotation of the gear 29 together with the nut 27 with respect to the screw 26 is in the same direction regardless of whether the working roll turns to the right or to the left. can be continued. In order to start the work roll in the opposite direction, the roller 37 is moved by the opposite pawl 3.
1 and move it in the direction of the marquee line to the position where it engages with 1.

This can be done either by moving the knob 40 by hand or by means of well-known controlled or automated equipment. The drive described above, besides solving the problems outlined at the beginning, makes it possible to rearrange the roll geometry of the cluster mill and thereby obtain unexpected additional benefits.

For example, the beam-backed cluster mill shown in U.S. Pat. No. 3,691,81 is capable of rolling the metal strip only up to a certain gauge where it becomes very work hardened.

Therefore, before the thickness is reduced further, the moth becomes dull and soft, and the pongee does not become soft. The present invention allows such a mill to be converted into a dual-purpose mill capable of further reducing the thickness of the work-hardened strip.
Referring to FIG. 5, rough rolling is being carried out between rolls la and 1'a.

When the strip is work hardened beyond the capacity of these rolls, the mill rolls la, 1'a with 4 diameter rolls 1, 1
' is replaced, the intermediate roll 11 is inserted, and the billy roll 8 is rotated to a position where it bears on both the upper and lower casters 3 and further rolled. The outgoing component of the strip S (above) is guided over suitable rollers (not shown) on the top of the beam 5 of the mill housing;
It must then be attached to the tension reel through this billy roll 8.

In order to obtain this advantage, the roll 8 can be used as a pilly roll 8' when the strip S is being roughly rolled between the roll 8 and the working rolls la, 1'a, or as an additional roll 8 as described above. A fulcrum axis 10 is provided on the lever 9 of the roll 8 at a point where it can act on both sides. Since the driving rolls are as long as rolls 1 and 1', the three passages [between rolls 1' and 11, between rolls 8 and 11, and between rolls 11 and 1] are relatively light, but 3 The total reduction thickness of all individual rolls is high, typically 40 to 60%.

Central roll 1 1 carries the roll pressure from three sides of rolls 1, 8 and 11 and is therefore at risk of destruction if pressure is applied only from the two opposite sides for cooling purposes with fluid circulation. A large central hole is provided. In another embodiment shown in FIG. 6, the roll 11 is mounted on a conventional bearing - this bearing 46 - is placed between the mill columns in the plane of symmetry of the work roll 1' to allow more freedom in the selection of the roll diameter. Preferably placed within - placed within.
However, it is stiff enough to support the tension in the strip,
The diameter must be sufficiently large with respect to the face of the weave.
This configuration also requires guiding the emerging strip over the top of the mill, as in the embodiment shown in FIG. 5, and is well suited for rolling strips of hard material.

In the S-curve and in the same plane of symmetry, add another roll 1a (Fig. 7) in the first half of the periphery of roll 11a and then roll 1.
By guiding the strip S around 1, the strip undergoes a three-pass thinning and exits in the same direction as it enters without having to guide it over the top of the mill.

Automatic insertion of such a mill is obtained by adding, instead of roll 11, a special roll 11'.

The bearings 46' of both rolls are placed on a common slide, which, when shifted, places either roll 11 or 11' in the plane of symmetry of the mill, which allows it to take a longitudinal path over the strip. Something happens. This automatic insertion takes place in two stages. First step: Roll 11' is moved to the position in which roll 11 was initially located, while roll 11 is in the play position (on the left) shown by the dotted line.

The leading end of the strip S is guided between the work roll 1' and the roll 11', and the inserted leading end is deflected upward by a deflector 43 as shown by the dotted line. Second stage: The mill is stopped and the sliding body is moved with rolls 11 and 11' into its working position, ie roll 11' is moved into its idle position and roll 11 into its working position.

Roll 11 picks up the ejector that was in its path of strip S together with it and pulls it into the insertion position between roll 11 and roll 11a at the bottom and between roll 11 and work roll 1 at the top, and then Forms a double S-curve. The rolling operation continues in this position of the rolls, so that the strip S is successively rolled through rolls 1' and 11a, rolls 11a and 11, roll 1.
It undergoes three-pass thickness reduction between 1 and 1.

Alternatively, automatic insertion may be carried out in which the bearings 47, 47a (Figs. 8, 9) of the rolls 11, 11a are held in the vertical grooves 41' of the rotary holder 41, restraining them to the surface of the work roll. This can be done without the aid of a deflector.

The holder 41 is rotatable in an arcuate recess provided in a liner 42, 42' placed between the holder and the mill housing column 5. The strip S is led straight into the mill as shown in FIG. 10, in which two such mills are shown side by side. The holder 41 is then turned half a turn, one to the right and one to the left, to the position shown in FIG. 11 by means of a device not shown. The mill then becomes an automatic insert that takes six consecutive passages in one operation. Maintaining the correct tension during each roll bite is essential in the rolling process, as is known in the art.

The shape of FIG. 11 makes it possible to place load cells 44, 45 (FIG. 9) or similar pressure measuring devices directly on the tension line for the most accurate signal without the customary deflectors or other devices. Make it. It is understood that many modifications can be made without departing from the spirit of the invention.

Therefore, no limitations not expressly stated are intended or included.

[Brief explanation of the drawing]

Fig. 1 is a plan view of the transmission device according to the present invention, Fig. 2 is a side view thereof, Fig. 3 is a longitudinal sectional view passing through the transmission box of Figs. 1 and 2, and Fig. 4 is a part of the transmission box. The cross-sectional rear views, Figures 5, 6, 7, 10 and 11 show the various shapes of rolls that can be added to a basic class (6-stage) mill, all of which 8 is a fragmentary sectional view showing details of a roll bearing for the roll shape shown in FIGS. 10 and 11, and FIG. 9 is an end view of FIG. 8. 1, 1', la, 1'a... work roll, 3.
... Caster, 5 ... Housing, 8, 8' ... Roll, 9 ... Lever, 10 ... Axis line, 11, 11', 1
1a...Roll, 12...Pinion, 12'...Shaft, 1
3... Bevel gear, 14... Shaft, 15... Keyway, 1
6...Key, 17...Flatket, 18...Trunion, 19...Bearing, 20...Transmission box, 21...Pin, 23...Lever, 24
... Spring, 25 ... Box, 26 ... Screw, 27 ... Nut, 28 ... Key, 29 ... Saw gear, 29' ... Left side, 29'' ... Right side, 30, 31 ... ...claw, 30', 3
0″... Leg, 32... Pin, 33... Teeth, 34
... Spring, 36 ... Supporting hand, 37 ... Loaf, 38 ... Shaft, 39 ... Placket, 40 ... Knob, 41 ... Holding body, 41' ... Groove , 42, 42'
...Liner, 43...Deflector, 44,45...
Cell, 46, 46' - bearing, 47, 47a...
··bearing. Figure 1 Figure 2 Figure 3 Figure 4 Figure 5 Figure 6 Figure 7 Figure 8 Figure 9 Figure 0 Figure 11

Claims (1)

[Scope of Claims] 1. A housing, a pair of cooperating work rolls each supported by two parallel caster rows supported by the housing, and a roll drive for each work roll. The roll driver includes a first bevel gear keyed to an end of the work roll, a motor having a shaft and disposed at the top of the housing, and a motor keyed to the shaft of the motor. a second bevel gear that meshes with the first bevel gear; these bevel gears are mounted in a gear box attached to the housing by a swivel linkage, and the linkage is connected to the work roll. a device for absorbing torque reactions with the motor, and a device for applying upward pressure to the gearbox so as to render it weightless, the gearbox being free to follow the axis of the work roll. a cluster mill, the gearbox cooperating with an axial reciprocating mechanism for the work rolls. 2. A housing having upper and lower support beams, each beam supporting two pairs of parallel caster rows, each pair of caster rows supporting one work roll, and each work roll supporting one work roll. Each of the work rolls is independently driven by a motor provided at the top of the beam above the work roll, and a floating bevel gearbox is mounted at the end of the work roll for transmitting torque to the work roll. , the gearbox is equipped with a device for absorbing any torque reaction, thereby forming two independent rolling mill assemblies, each said rolling mill assembly being supported by a pair of cylindrical supports. and two additional rolls located in the plane of the two work rolls; It is equipped with a device for rotating 180 degrees and converts the workpiece fed straight through the center roll meshing part into a double S-shaped curve to perform 6 rollings in succession. tandem mill.