JPS5944124B2 - Inclined roll rolling equipment for reducing the internal or hollow cross section - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention is a U40-type rolling device, in which a driven roll support (rotating body) is provided on a hollow shaft that allows the rolling material to pass through, This roll support has three conical work rolls oriented relative to the axis of the rolled material, offset by 120° with respect to each other, each of which carries a drive via a planetary gear. The invention relates to a type in which the planetary gears are movable on the sun gear together with the rotation of the roll support, and the sun gear is mounted on a hollow shaft.

Planetary gear #A@ roll mills are suitable for significantly deforming semifinished products, ie solid cross sections, as well as for reducing hollow cross sections.

A work roll is applied to the rolled material in order to obtain a cross-section of the desired dimensions or a hollow cross-section of the desired outer diameter, the inner diameter being defined by the mandrel.

The feed movement of the rolled material is produced by the oblique position of the rolls, so that the axis of the shaft holding the working roll intersects the rolled material axis at a short distance.

In order to adjust this crossing angle, a roll head supporting the working roll shaft is mounted on the roll support so as to be pivotable about an axis parallel to the axis of the rolled material.

In order to drive the work roll and the associated planetary gear,
An intermediate shaft is supported in the roll head parallel to the rolling material, and this intermediate shaft has an intermediate gear that engages with a planetary gear and a bevel pinion, and the bevel pinion is attached to the roll shaft. It is engaged with the bevel gear.

Due to the inclination position of the rolls that defines the feed movement of the rolled material, if the roll reduction is constant and the resulting rolled material diameter is constant and the rolled material attempts to pass through the rolling device without rotation, then A predetermined ratio between the roll rotation speed and the roll support rotation speed is determined.

In order to avoid rotation of the rolled material even in the other reduction or tilted positions of the rolls, a hollow shaft can be rotated together with a sun gear mounted on this hollow shaft, thus changing the roll speed and the roll support. The ratio between rotational speed and speed is controllable.

In known planetary gear inclined roll rolling mills constructed as described above, the adjustment of the rolls is carried out by moving the rolls in the axial direction, the axis of the rolls moving together with the rolls in the axial direction. (German Patent Application No. 1 602 153), or a slide bushing inserted in the shaft and holding the roll can be adjusted by means of a threaded screw thread. (DE 2009867), whereas the adjustment of the roll inclination position is carried out by a rotation of the roll head casing, which for this purpose is moved relative to the intermediate axis. The rollers are mounted with concentric extensions in concentric bores of the same size in the roll support and are pivotable about the axis of the intermediate shaft.

Adjustment mechanisms, especially those provided in the roll head to adjust the roll axially, require a large construction outlay of the roll head itself and the space required for mounting the adjustment mechanism is limited to bevel gears and bearings. Structurally matched with space for a robust configuration of the roll axis with.

SUMMARY OF THE INVENTION It is an object of the present invention to improve a unidirectional adjustment device for a roll,
The adjustment device is mounted outside the space occupied by the bearing of the roll shaft and the drive, ie outside the roll head casing.

In order to achieve this object, the configuration of the present invention is such that, in the type described above, each roll head casing is parallel to the end face of the roll support (rotating body) and has a sun gear, a planetary gear and an intermediate gear. It is designed as a rocking arm that can be pivoted along a plane perpendicular to the axis of the gear, the pivot axis of which swings out of the axis of the intermediate gear supported on the rocker arm, allowing the intermediate gear and the associated planetary gear to move. in or near a common plane of the axes of the gears, supported in guides extending perpendicularly to this common plane and ensuring meshing of the intermediate gear and the planetary gear on both sides of this common plane. It can be adjusted to the extent that it is possible.

In the known device, when the roll head is pivoted about the axis of the intermediate shaft, the inclination position of the rolls is also strongly changed - the pivoting is carried out in this case for the purpose of changing the inclination position, which causes a change in the distance of the rolls with respect to the axis of the rolled material. Always requires modification of the axial adjustment of the rolls to compensate.
On the other hand, according to the present invention, the rotation of the roll head about the rotation axis provided outside the axis of the intermediate gear causes a slight change in the inclination position of the rolls compared to a change in the spacing of the rolls with respect to the axis of the rolled material. I can only let it grow.

According to an embodiment of the invention, the guide of the pivot shaft is advantageously arranged in such a way that this guide intersects the axis of the planetary gear.

Therefore, the rotation axis and the axis of the planetary gear are always close to each other,
This is advantageous for the state of engagement between the intermediate gear and the planetary gear, and in special cases the pivot axis coincides with the axis of the planetary gear.As already mentioned, the degree of change in the tilt position of the roll is It is related to the degree of change in the distance of the rolls relative to the axis.

If the spacing between the rolled material axis and the roll changes within a narrow limit, the change in the roll inclination position is negligibly small.

Adjustment of the pivot axis is then unnecessary, and the pivot axis can be located within the axis of the planetary gear.

According to a further embodiment of the invention, it is advantageous if the pivot axis is arranged diametrically in relation to the intermediate gear with respect to the point of contact of the pitch circle of the intermediate gear and the planetary gear.

This is because the guide of the pivot axle is thereby moved to the outside where there is sufficient space for mounting the pivot axle and the adjustment mechanism.

Such an arrangement therefore provides a simple construction.

In a further embodiment of the invention, each roll head casing is mounted in an opening in the roll support allowing movement of the roll head casing with an extension receiving a bearing of the intermediate shaft and with a flange. The flange of the roll-to-roll casing can thus be tightened against the end face of the roll-support, which closes the opening of the roll-to-roll casing in any pivoted position of the roll-to-roll casing.

In a preferred embodiment of the invention, the roll support is provided with an extension, which is closed by an end ring so that the roll can be placed between mutually opposite parallel faces of the end ring and the roll support. The head casing is guided so that it can pivot like a rocking arm.

Next, embodiments of the present invention will be specifically described using the drawings.

In FIG. 1, the frame of the inclined roll rolling mill, also called a stationary roll, is designated by the reference numeral 1.

A hollow shaft 2, which freely passes through the rolled material 3 in the axial direction, is rotatably supported in the frame 1, and a sun gear 4 is mounted on this hollow shaft.

The hollow shaft 2 and thus the sun gear 4 are connected to a shaft 5 with a bevel gear 6
and a bevel gear 7 that is non-rotatably attached to the hollow shaft 2 and engages with the bevel gear 6, and is driven by a motor (not shown) whose rotation speed is adjustable.

The drive via shaft 5 is an auxiliary drive, via which the rotational speed ratio between roll 17 and roll support rotor 8 can be controlled.

A rotor support 8 is further rotatably supported on the pedestal 1 and the hollow shaft 2.

In order to rotate the roll support 8, a crown-shaped bevel gear 9 is connected to the end face of the roll support 8, which has a shaft 1 driven by a drive (not shown).
1 small gear 10 is engaged.

The shaft 13 of the roll support 8 has planetary gears 12a, 12b,
12c (a, b, c indicate position) are rotatably mounted, and these planetary gears engage the sun gear 4.

The roll support 8 is provided with three openings 14, each of which protrudes with an extension 15 of the roll head casing 16a, 16b, 16c.

Each casing 16a, 16b, 16c is a conical roll 17a1 shifted by 120° from each other around the rolling material 3.
7b and 17c, respectively.

Roll 17, shaft 18 holding this roll, this shaft 18
A bevel gear 19 is non-rotatably attached to the bevel gear 19, a bevel gear 20 is engaged with the bevel gear 19, and a bevel gear 20 is supported within the additional portion 15 of the roll head casing 16 to connect the bevel gear 20 and the intermediate gear 21. The intermediate shafts 22 and 22 are assembled into a roll head by a 16-hole rad casing 16.

(In order to make the location of these individual components easier to understand, the individual components, as well as the casing and rolls, have been further labeled a, b and C.

) The intermediate gear 21 is engaged with the planet gear 12, so that when the roll support 8 rotates, the planet gear 12 is displaced on the sun gear 14, thereby causing the roll 17 to rotate.

This basic construction is the same in both embodiments, and therefore the same parts in FIG. 5 are designated with the same reference numerals followed by a ''.

In the embodiments of FIGS. 1, 2, 3, 4 and 9, the roll head casing 16 has a pivot point for the purpose of varying the distance between the roll 17 and the axis of the rolled material 3. 25, for which the roll head housing 16 is provided with a rocker plate 26, which is particularly shown in FIG.

The rotation of the roll head casing 16 is effected by an eccentric body 27.

For this purpose, the rocking arm plate 26 of the roll head casing 16 is provided with a support surface 29 on which a corresponding bearing of the g-roll support 8 rests, in contact with a slide 30 mounted on the eccentric 27. 34 and an end ring 46 maintain contact between the roll head casing 16 and the slide 30 of the (adjusting) eccentric 27.

The eccentric body 27 is connected to the roll head casing 1.
6 is supported against the rolling pressure, and is arranged such that the rolling pressure is mainly absorbed by the end ring 46.

The rotation of the eccentrics 270 is effected in each case by means of worm gears (not shown) which are electrically coupled to one another and are driven together by a motor.

With a self-locking worm gear, special fastening devices are not required.

By rotating the roll head casing 16 about the pivot shaft 25, the inclination position of the roll 170 with respect to the axis of the rolled material 3 is changed and the state of engagement between the intermediate gear 21 and the planetary gear 12 is changed.

To compensate for such variations, the pivot shaft 25 is moved perpendicularly to the common plane of the axes of the associated intermediate gear 21 and planetary gear 12.

For this purpose, the pivot shaft 25 is equipped with a guide pin 39, which is inserted into a guide groove 40 formed in the roll support 8 and the end ring 46.

The pivot shafts 25 are each connected to push rods 35, which are moved together by an eccentric 36 of the shaft 37.

The shafts 37 can be dynamically connected to each other via a worm gear (not shown) and can be driven together by a motor for adjusting the pivot shaft 25.

The end ring 46 is held by an extension 45 and is connected to the roll support 8.

FIG. 9 shows the principle of operation of the embodiment described above.

The principle of operation of another embodiment is shown in FIG.

This example (Figures 5, 6, 7, 8 and 10)
In FIG. 1, the roll casing 16 is also constructed as a rocking arm suspended on a pivot shaft 25 in order to change the distance between the roll 17 and the axis of the rolled material 3, and for this purpose the roll head The casing 16 is provided with an eye 26'.

In particular, FIGS. 6 and 8 show the parts numbered.

The pivot axis 25' can only be changed within a relatively narrow range if the distance between the roll 17 and the axis of the rolled material 3 can be varied only within a relatively narrow range.
In contrast to the illustrated embodiment, it may also be arranged in a stationary manner.

The pivoting of the rad casing 16 onto the roll is effected by an eccentric 27'.

For this purpose, the roll head casing 16 is provided with a bracket arm 28', on the support surface 29' of which a slide 30' attached to an eccentric 27' rests.

A spring 33' supported on a corresponding bearing 34' of the end ring 46' maintains contact between the Calor head casing 16 and the slide 30' of the eccentric 27'.

The eccentric 27' is arranged in such a way that it supports the roll head casing 16 against the rolling pressure, which is substantially absorbed by the end ring 46'.

As shown in FIG. 7, the rotation of each eccentric 27' is effected by a worm gear 31 which is electrically connected to one another and is driven together by a motor 32.

The use of a self-locking worm gear eliminates the need for special fastening devices.

By pivoting the roll head casing about the pivot axis 25' which approximately coincides with the axis of the planetary gear 12, the helical position of the roll 170 with respect to the axis of the rolled material 3 changes, but this change is negligible for small pivots. Moderately small.

In order to compensate for deviations of the tilting position from the target position that occur in the case of large swivels, the swivel shaft 25' is mounted in a push rod 35', by means of which the pitch of the intermediate gear 21 and the associated planetary gear is adjusted. slightly movable in a direction parallel to the common tangent of the circle, thereby causing the planetary gear 12
The engagement between the intermediate gear 21 and the intermediate gear 21 is not impaired.

This parallel movement moves the roll to the eighth position.
As can be seen, the tilt angle α shown in the figure is also returned to the target position.

In order to adjust the push rod 35', the push rod has an eccentric body 36' on one side.
The eccentric body is fixed to the shaft 37' in a non-rotatable manner.

The shaft 37' is rotatably supported in a bearing 38 by a drive (not shown).

The push rod 35' has a slide 39 and a slide guide 40 extending parallel to the direction of movement of the push rod 35', i.e. to the tangent line.
’.

As shown in the embodiment of FIGS. 7 and 8, the eccentrics 41 for adjusting the push rod 35' are part of a worm gear 42 that is transmission-coupled to each other and driven together by a motor 43. It is.

To support an eccentric 36' or an eccentric 41 with an axle 37', a push rod 35' and a slide guide 40' of the bearing part of the eccentric 27' receive a worm gear 3142 and an adjusting motor 32, 43. For this purpose, the extension 45' of the roll support 8 is connected to the end ring 46.

[Brief explanation of the drawing]

The drawings show an embodiment of the present invention, in which FIG. 1 is a sectional view taken along the line II in FIG. 3, and FIG. 2 is a sectional view taken along the line II in FIG.
■A sectional view taken along the line, FIG. 3 is an end view of the first embodiment, FIG. 4 is an enlarged view of the adjustment mechanism of the embodiment in FIG. 3, and FIG. 5 is taken along the line V-V in FIG. 6 is a schematic perspective view of the main components for driving and adjusting the roll, FIG. 7 is an end view of the second embodiment, and FIG. 8 is an adjustment mechanism of the embodiment of FIG. 7. 9 is a diagram showing the principle of operation of the adjustment mechanism of FIG. 4, and FIG. 10 is a diagram illustrating the principle of operation of the adjustment mechanism of FIG. 8. 1... Frame, 2... Hollow shaft, 3...
...Rolled material, 4...Sun gear, 5...
...Shaft, 6...Bevel gear, 7...Bevel gear, 8...
...Roll support. 9...Bevel gear, 10...Small gear, 11...
...Axis, 12...Planetary gear, 13...
...Shaft, 14...Opening, 15...Additional part, 16...Roll head casing, 17...
...Roll, 18...Axis, 19...
...Bevel gear, 20...Bevel gear, 21...
...Intermediate gear, 22...Intermediate shaft, 25...
...Swivel axis, 26...Rocking arm plate, 27.
... Eccentric body, 29 ... Support surface, 30 ...
... Slider, 33 ... Spring, 34 ... Corresponding support part, 35 ... Push rod, 36 ... Eccentric body, 37 ... Shaft, 39... Guide pin,
40... Guide groove, 41... Eccentric body, 4
2...Worm transmission device, 45...Additional part, 46...End face ring.

Claims (1)

[Scope of Claims] 1. An inclined roll type rolling device for reducing the inner diameter or hollow cross section, comprising: 1 driven roll support (rotating body) on a hollow shaft that allows the rolling material to pass through; A roll carrier is provided, the roll support having three driven conical work rolls tilted to the rolling material axis, offset by 120° to each other and adjustable with respect to the rolling material axis. , a shaft that holds the work roll and intersects the rolling material axis at a short distance is electrically coupled to each intermediate shaft via each bevel gear set, and these intermediate shafts further drive spur gears, respectively. These spur gears are engaged as intermediate gears via planetary gears to a sun gear mounted on a rotatable hollow shaft, and the rotation of this sun gear causes the work roll and roll support to be connected to each other. The rotation speed ratio between them is controlled so that the rolled material can pass through the rolling device without rotating, and the roll support (rotating body) and the hollow shaft of the sun gear are connected to one pedestal (stator). a shaft rotatably supported on which a conical work roll holds the work roll; a first bevel gear mounted on the shaft; and a second bevel gear engaged with the first bevel gear. The gear, the intermediate shaft holding this second bevel gear, and the intermediate gear attached to this intermediate shaft are supported in a roll rad casing and assembled into a roll head, and the roll head is used for rolling. Each roll is rotatably mounted on a roll support (rotating body) for the purpose of adjusting the intersection angle between the roll axis and the rolled material axis about an axis parallel to the material axis. The roll rad casing 16 of the head is rotatable along a plane parallel to the end surface of the roll support (rotating body 8) and perpendicular to the axes of the sun gear 4, the planet gears 12, and the intermediate gear 21. It is configured as a rocking arm, and the pivot axis 25.2 of this rocking arm
5. Outside the axis of the intermediate gear 21 mounted on the rocker arm, in or near a common plane of the axes of the intermediate gear 21 and the associated planetary gear 12, a guide 40 extending perpendicular to this common plane. 40' and is adjustable to the extent that it guarantees the meshing of the intermediate gear 21 and the planetary gear 12 into both IOs of this common plane. Inclined roll type rolling equipment with dam. 2. The inclined roll type rolling apparatus according to claim 1, wherein the guide 40' of the rotating shaft 25' intersects the axis of the planetary gear 12. 3 The guide 40 of the pivot shaft 25 connects the intermediate gear 21 and the planetary gear 1
2. The inclined roll rolling device according to claim 1, wherein the rolling device is arranged diametrically with respect to the contact point of the pitch circle with the pitch circle. 4. To each roll, the rad casing 16 is attached to the roll head casing 1 with an additional part 15 that receives the bearing of the intermediate shaft.
The opening 1 of the roll support 8 is mounted in the opening 14 of the roll support 8 to allow movement of the roll support 8 with a flange to the roll in any pivoted position of the rad casing 16.
2. The inclined roll rolling apparatus according to claim 1, wherein the flange of the roll head casing 16 that closes the roll head casing 16 can be tightened against the end face of the roll support 8. 5. The roll support 8 is provided with an extension 45, 45', which is closed by an end ring 46, 46', and the end ring 46, 46' and the roll support 8 are arranged in mutually opposite parallel directions. 5. The inclined roll rolling apparatus according to claim 4, wherein the roll head casing 16 is rotatably guided as a rocking arm between the faces. 6. The pivot axes 25, 25' of the rocking arms are inserted into the guides 40, 40' of the roll support 8 and the end rings 46, 46' and are aligned uniformly and in the same direction via the push rods 35, 35'. 2. Inclined roll rolling mill according to claim 1, which is adjustable by means of eccentrics 36, 36' acting on the tilting roll. 7. The two eccentrics 36.36' provided for the adjustment of the pivot axis 25.25' are arranged on a common axis 37.37', which is supported in the extension 45.45'. The inclined roll rolling device according to scope 6. 8. Inclined-roll rolling mill according to claim 1, in which the roll head housing 16, which is designed as a rocker arm of the roll head, cooperates with an adjustment device for the pivot movement, for example an eccentric 27, 27'. 9 Adjustment device 27/30. 27'/30' supports the rad casing 16 to the roll against rolling pressure, and
The roll head casing 16 is moved by the adjusting device 27/30. by the spring 33°33'. 9. The inclined roll type rolling apparatus according to claim 8, wherein the plate 7'1 is brought into contact with 27'/30'. 10. Adjustment devices 27/30 are arranged on the end face of the roll support 8 and on the end face ring 46 of the extension 45, which are electrically connected to each other in order to actuate the rad casing uniformly and in the same direction on the roll. Claim No. 9
Inclined roll type rolling device as described in 2. 11 Mechanism 35/ for adjusting the pivot shafts 25, 25'
36/37, 3go/36'/β7' and adjustment device for the swivel sump of the roll head casing 16 of the three rolls of the rolling mill 27/30. 7. The inclined roll type rolling apparatus according to claim 6, wherein the rolls 27' and 30' can be electrically connected to each other.