JP5912571B2 - Horizontal roll device with variable trunk width - Google Patents

Description

The present invention relates to a variable-roller-width horizontal roll apparatus capable of arbitrarily adjusting the roll-roller width of a pair of drive-side and work-side-side horizontal rolls used in a finish rolling mill for H-section steel on-line.

2. Description of the Related Art Conventionally, in a universal rolling mill for H-section steel, a variable-roller-width horizontal roll apparatus that rolls H-section steel of different dimensions by changing the horizontal roll barrel width of the universal mill online has been disclosed (for example, (See Patent Documents 1 and 2).
For example, as shown in FIGS. 7A and 7B, this body width variable horizontal roll apparatus has a pair of horizontal rolls for rolling a flange of H-shaped steel and a web connecting the flanges. The horizontal roll (not shown) is fixed to the drive side (drive side) of a roll shaft 88 driven by a mill motor, and the other horizontal roll 85 is moved to the work side side (reverse drive side) of the roll shaft 88 by a spline 89. It is fixed to the hollow shaft 80 to be connected. 7A shows a state during rolling operation (roll body width W is min (minimum)), and FIG. 7B shows a state when the roll body width is changed (roll body width is changed from min (minimum) to max (max). ))).

Inside the hollow shaft 80, there is provided a screw shaft 81 having a shaft center aligned with the roll shaft 88 and partially formed with a male screw 91, and a hollow screw piece 82 having a male screw 83 provided on the screw shaft 81. Are screwed, and the male screw 83 of the hollow screw piece 82 is screwed with a female screw 84 formed inside the hollow shaft 80. A clutch mechanism is provided at the end of the hollow shaft 80 for switching between a lock side for locking the rotation of the screw shaft 81 and a side for connecting the screw shaft 81 to the hollow shaft 80. When the roll shaft 88 is driven by a mill motor while the screw shaft 81 is stopped by operating the clutch mechanism, the female screw 84 of the hollow shaft 80 moves with respect to the male screw 91 of the fixed screw shaft 81, and as a result. The space between the left and right horizontal rolls provided on the hollow shaft 80 changes. Since the center position of the left and right horizontal rolls also shifts with respect to the rolling line due to the movement of the horizontal roll, a centering device for moving the entire hollow shaft 80 and the roll shaft 88 to the left and right is provided, The center is adjusted to coincide with the center of the rolling line. Further, a flange 90 is provided on the outer peripheral side of the base portion of the hollow screw piece 82 where the male screw 83 is formed, and a thrust load receiving nut 92 is screwed into the male screw 91 formed on the screw shaft 87.

By adopting such a configuration, the hollow screw piece 82 is attached to the hollow shaft 80 by screwing the male screw 83 formed outside the hollow screw piece 82 and the female screw 84 formed inside the hollow shaft 80, and The screw shaft 81 can be rotatably inserted into the hollow screw piece 82. Then, the thrust load receiving nut 92 is screwed onto the male screw 91 of the screw shaft 81 and brought into contact with the flange 90 of the hollow screw piece 82, whereby the horizontal load Fv (roll horizontal reaction force) acting on the side surface of the horizontal roll 85 is obtained. Can be supported by the screw shaft bearing 87 via the thrust load receiving nut 92.

A distance L ′ between the axial center of the bearing housing 86 and the axial center of the screw shaft bearing 87 is expressed by equation (1).
L ′ = La + Lb + Lc + Ld + S (1)
La: Distance from the center of the bearing box 86 to the end surface of the hollow shaft 80 when the body width Wmin is Lb: Width dimension Lc of the flange 90 of the hollow screw piece 82: Screw shaft bearing from the end surface of the thrust load receiving nut 92 on the flange 90 side The distance Ld to the center of 87: the width dimension of the thrust load receiving nut 87 S: the amount of movement of the roll Note that the distance L ′ between the center of the bearing housing 86 and the center of the screw shaft bearing 87 is the width of the thrust load receiving nut 92 Dimensions are included.

Furthermore, the screw length P ′ of the hollow screw piece 82 is expressed by the equation (2).
P ′ = m + S (2)
m: Length of the internal thread 84 provided on the hollow shaft 80 (size of the portion that supports the horizontal load Fv)
S: Roll movement amount of the horizontal roll 85 As described above, the screw length P ′ of the hollow screw piece 82 is equal to the roll movement amount S of the horizontal roll 85 adjusted by the male screw 83 of the hollow screw piece 82 and the hollow shaft 80. The total length of the female screw 84 is obtained.

JP 62-156007 A Japanese Patent Laid-Open No. 3-210907

However, the conventional trunk width variable horizontal roll apparatus has the following problems.
(1) When a large horizontal load is applied to the horizontal roll fixed to the hollow shaft side, the load is applied to the screw shaft through the female screw of the hollow shaft. However, in general, the screw shaft has a small diameter and cannot receive a large load.
(2) A clutch mechanism with a complicated structure is required to switch between the side that locks the rotation of the screw shaft and the side that connects (unlocks) the screw shaft to the hollow shaft.
(3) Further, when the barrel width of the left and right horizontal rolls is adjusted, the center position of the left and right horizontal rolls is shifted with respect to the center of the rolling line, so a centering device for moving the entire apparatus is required. There was a problem of increasing complexity.
(4) When the size range of the H-shaped steel to be rolled is wide, the distance from the center of the bearing box to the center of the screw shaft bearing is the distance between the hollow shaft and the hollow screw piece required for changing the roll drum width. There is a problem that an extra length corresponding to the screw meshing length between them and the width corresponding to the width of the thrust load receiving nut are required, and it cannot be made compact.

The present invention has been made in view of such circumstances, is small, withstands the action of a large roll horizontal reaction force, while maintaining the center of the roll cylinder width of the horizontal roll on the drive side and the work side on the center line of the rolling line. An object of the present invention is to provide a variable width horizontal roll apparatus capable of adjusting the roll width by a simple operation.

The variable body width horizontal roll device according to the present invention that meets the above-mentioned object includes an arbor shaft (roll shaft, main shaft) that is connected to a rotational drive source on one side and supported on both sides by a bearing box, and a center of the arbor shaft. One side of the sleeve that is spline-coupled to the other side of the part, a drive side horizontal roll that is fixed to one side from the central part of the arbor shaft and presses one side of the material to be rolled during rolling, and one of the sleeves A work side horizontal roll that is fixed to the side and presses the other side of the material to be rolled during rolling, and a roll positioning mechanism that adjusts the position of the drive side horizontal roll and the work side horizontal roll with respect to the arbor shaft In the body width variable horizontal roll device having
The roll positioning mechanism includes: 1) a first male screw formed on a part of the other side of the arbor shaft; 2) a first female screw formed on the other side of the sleeve; A second female screw that is screwed to one male screw, a second male screw that is screwed to the first female screw is formed on the outside, and a screw cylinder that is screwed to the arbor shaft and the sleeve, 4) A screw cylinder switching means for stopping rotation of the screw cylinder at the time of adjusting the interval between the drive side and work side horizontal rolls, and integrating the rotation of the screw cylinder and the arbor shaft at the time of rolling;
The second female screw and the second male screw formed on the screw cylinder have different spiral directions at the same feed pitch.

In the body width variable horizontal roll device according to the present invention, the screw cylinder switching means includes: 1) a clutch seat fixed to the other side of the screw cylinder; and 2) the arbor shaft via a second spline connection. A clutch sleeve that is mounted on the other side so as to be movable in the axial direction, and that unifies the screw cylinder via the arbor shaft and the clutch receiving seat by coupling the clutch receiving seat and a third spline when moving on the other side And 3) a clutch base having a clutch operating seat attached to a predetermined position of the clutch sleeve via a bearing and abutting against the clutch receiving seat when the clutch sleeve moves to one side, and 4) a shaft of the clutch base And an actuator that moves the clutch base to one side by the actuator to move the clutch side and the drive side. To allow the distance adjustment of Kusaido side horizontal rolls, the clutch base is moved to the other side by the actuator, by the third spline coupling is preferably carried out the integration of the screw cylinder and the arbor shaft.

In the body width variable horizontal roll device according to the present invention, an annular protrusion is provided on the inner side of the other side of the sleeve, and the tip of the screw cylinder screwed into the arbor shaft and the sleeve is between the protrusion. Preferably, a compression spring is disposed to reduce backlash of the arbor shaft, the screw cylinder, and the sleeve that are screwed together.

In the body width variable horizontal roll apparatus according to the present invention, the roll positioning mechanism includes 1) a first male screw formed on a part of the other side of the arbor shaft, and 2) a first male screw formed on the other side of the sleeve. 1) a female screw, 3) a second female screw that is screwed to the first male screw on the inside, and a second male screw that is screwed to the first female screw on the outside, and are respectively screwed to the arbor shaft and the sleeve 4) Since there is a screw cylinder switching means for stopping rotation of the screw cylinder at the time of adjusting the interval between the drive side and work side horizontal rolls, and integrating the rotation of the screw cylinder and the arbor shaft at the time of rolling, The diameter of the arbor shaft can be increased to a size that can be screwed with the screw cylinder, and the horizontal reaction force (horizontal load) acting on the side portion of the horizontal roll can be increased.

When the rotation of the screw cylinder is stopped and the arbor shaft is rotated by the rotational drive source, the sleeve splined to the arbor shaft performs the same rotation operation as the arbor shaft. Here, since the second female screw and the second male screw of the screw cylinder have different spiral directions at the same feed pitch, the arbor shaft and the sleeve that are respectively screwed into the screw cylinder have the same distance in the opposite direction. Just move. For this reason, since the roll drum width can be adjusted while maintaining the roll drum width centers of the drive-side and work-side horizontal rolls on the center line of the rolling line, online roll drum width adjustment is facilitated.

Since the arbor shaft and the sleeve move in the opposite direction by the same distance, the screw engagement length between the sleeve and the screw cylinder can be halved compared to the conventional one, and the roll positioning mechanism can be made compact. can do. Furthermore, since the position of the screw cylinder is always a fixed position when adjusting the distance between the drive side and work side horizontal rolls and rolling, the position of the support member necessary for the screw cylinder can also be fixed at a fixed position. For this reason, a roll positioning mechanism can be easily remodeled by adding it to an existing horizontal roll device to a variable trunk width type horizontal roll device.

In the body width variable horizontal roll device according to the present invention, the screw cylinder switching means includes 1) a clutch seat fixed to the other side of the screw cylinder, and 2) the other side of the arbor shaft via the second spline connection. And a clutch sleeve that integrates the screw cylinder through the arbor shaft and the clutch receiving seat by connecting the clutch receiving seat and the third spline when moving to the other side, and 3) the clutch sleeve In the case of including a clutch base having a clutch operating seat attached to a predetermined position via a bearing and abutting on the clutch receiving seat when the clutch sleeve moves to one side, and 4) an actuator for moving the clutch base in the axial direction, a screw Stops the rotation of the cylinder (ie, releases the connection between the arbor shaft and the screw cylinder), and unifies the arbor shaft and the screw cylinder (connects the arbor axis and the screw cylinder) Can be performed, the roll body width adjustment online becomes easier.

In the horizontal roll device with variable trunk width according to the present invention, an annular protrusion is provided on the inner side of the other side of the sleeve, and a compression spring is provided between the arbor shaft and the tip of the screw cylinder screwed into the sleeve and the protrusion. Are arranged to reduce backlash of the arbor shaft, the screw cylinder, and the sleeve that are screwed together, and the sleeve can be moved with high responsiveness when the arbor shaft is rotated.

It is sectional drawing of the universal rolling mill containing the trunk width variable type horizontal roll apparatus which concerns on one embodiment of this invention. It is sectional drawing of the body width variable type horizontal roll apparatus. (A) is a partially omitted arrow view seen from the M direction of FIG. 2, (B) is a partially cutaway view seen from the NN arrow direction of (A). It is explanatory drawing of the roll body width change operation | movement of the same body width variable type horizontal roll apparatus. It is explanatory drawing of the roll positioning mechanism at the time of roll body width change. It is explanatory drawing of the roll positioning mechanism in the next rolling preparatory operation after roll body width change. (A), (B) is explanatory drawing at the time of rolling operation of the trunk width variable type horizontal roll apparatus which concerns on a prior art example, respectively, and explanatory drawing at the time of roll trunk width change.

Next, embodiments of the present invention will be described with reference to the accompanying drawings for understanding of the present invention.
As shown in FIG. 1, the variable barrel width type horizontal roll device 10, 10 a according to an embodiment of the present invention is, for example, a universal rolling mill 12 that manufactures an H-section steel 11 (an example of a material to be rolled). Arbor shafts 15 and 15a, which are used as upper and lower pairs, are connected to a rotational drive source (not shown) via a coupling on one side, and are supported by bearing housings 13, 14, 13a and 14a on both sides; It has sleeves 16 and 16a mounted on the other side of the arbor shafts 15 and 15a by spline coupling. Here, the bearing boxes 13, 14, 13a, and 14a are fixed to mounting bases 17 and 17a provided in a housing (not shown) of the variable barrel width type horizontal roll device 10 and 10a.

Further, the body width variable horizontal roll device 10, 10a is fixed to one side from the central part of the arbor shafts 15, 15a, and one side of the web 18 of the H-section steel 11, that is, the drive side (DS in FIG. 1) during rolling. And the other side of the web 18 of the H-section steel 11, that is, the workpiece side (denoted as WS in FIG. 1), is fixed to one side of the drive side horizontal rolls 19 and 19a and the sleeves 16 and 16a. Work side horizontal rolls 20 and 20a to be pressed and roll positioning mechanisms 21 and 21a for adjusting the positions of the drive side horizontal rolls 19 and 19a and the work side horizontal rolls 20 and 20a with respect to the arbor shafts 15 and 15a are provided. doing.
In addition, the code | symbol 22 is a saddle roll which pinches and rolls the flange 23 of one side of the H-section steel 11 with the side part of the horizontal rolls 19 and 19a, and the code | symbol 24 is the horizontal roll of the flange 25 of the other side of the H-section steel 11. The rolls 26 and 26a are splines for spline coupling, which are rolled between the side portions 20 and 20a.

Then, the body width variable horizontal roll device 10, 10a is an on-line drive-side horizontal roll so that when the size of the H-section steel 11 to be rolled is changed, it corresponds to the changed H-section steel rolling. The roll body width W1 between 19, 19a and the work side horizontal rolls 20, 20a is changed. Here, since the upper and lower trunk width variable horizontal roll apparatuses 10 and 10a have the same structure, the upper trunk width variable horizontal roll apparatus 10 will be described below.

As shown in FIG. 2, the roll positioning mechanism 21 includes a first male screw 27 formed on a part of the other side of the arbor shaft 15, a first female screw 28 formed on the other side of the sleeve 16, and an inner side. A second female screw 29 that engages with the first male screw 27 is formed on the outside, and a second male screw 30 that engages with the first female screw 28 is formed on the outside, and the screws that respectively engage with the arbor shaft 15 and the sleeve 16. Screw cylinder switching means 32 that stops the rotation of the screw cylinder 31 when adjusting the distance between the cylinder 31, the drive-side horizontal roll 19 and the work-side horizontal roll 20, and integrates the rotation of the screw cylinder 31 and the arbor shaft 15 during rolling. And have. Here, the second female screw 29 and the second male screw 30 of the screw cylinder 31 have different spiral directions at the same feed pitch.

As shown in FIGS. 2, 3 (A), and (B), the screw cylinder switching means 32 has an arbor via a clutch receiving seat 40 fixed to the other side of the screw cylinder 31 and a second spline coupling 36. It is mounted on the other side of the shaft 15 so as to be movable in the axial direction, and when moving to the other side, the screw cylinder 31 is integrated through the arbor shaft 15 and the clutch receiving seat 40 by the clutch receiving seat 40 and the third spline coupling 41. The clutch sleeve 37 is attached to a predetermined position of the clutch sleeve 37 (the other side of the clutch sleeve 37 in FIG. 2) via a bearing 35, and the clutch sleeve 37 contacts the clutch receiving seat 40 when moving to one side. An annular clutch base 34 having a seat 33 and a cylinder 50 (see FIG. 3) which is an example of an actuator for moving the clutch base 34 in the axial direction are provided. And a movement driving unit 39. Here, the movement drive part 39 is attached to the side part of the cylindrical connection member 38 supported by the attachment base 17 that fixes the bearing box 14 that supports the other side of the arbor shaft 15.

The third spline coupling 41 is connected to the spline 43 formed on the inner peripheral side of the clutch receiving seat 40 and one side of the outer peripheral portion of the clutch sleeve 37, that is, when the clutch operating seat 33 and the clutch receiving seat 40 are connected. And a spline 44 formed on the front side of the region protruding from the spline 43 of the clutch receiving seat 40 into the screw cylinder 31. Reference numeral 42 denotes a pressing member that fixes the bearing 35.

Here, the movement drive unit 39 is connected to the cylinder 50 held via the cylinder base 49 fixed to the connecting member 38, the base side is connected to the piston rod 51 of the cylinder 50, and the intermediate part slides on the cylinder base 49. When the clutch sleeve 37 is mounted on the other side of the arbor shaft 15, the pair of latching portions 52 are arranged so as to face each other outward in the radial direction of the annular clutch base 34. Each has a connecting pin 54 fixed via a mounting ring 53. The stroke of the piston rod 51 is such that when the amount of protrusion of the piston rod 51 from the cylinder 50 is minimized, the clutch operating seat 33 is connected to the clutch receiving seat 40 and the amount of protrusion of the piston rod 51 from the cylinder 50 is reduced. When maximum, the clutch operating seat 33 is disengaged from the clutch receiving seat 40 and the third spline coupling 41 is formed between the spline 43 of the clutch receiving seat 40 and the spline 44 of the clutch sleeve 37. .
As a result, the clutch base 34 is moved to one side by the cylinder 50, and the distance between the drive side horizontal roll 19 and the work side horizontal roll 20 can be adjusted, and the clutch base 34 is moved to the other side by the cylinder 50, The arbor shaft 15 and the screw cylinder 31 are integrated by the third spline coupling 41.

The roll positioning mechanism 21 is further provided with a screw cylinder moving means 55 that moves the screw cylinder 31 in the axial direction. The screw cylinder moving means 55 is located on the side of the connecting member 38 and is gear-coupled to the gear driving section 56 attached to the region where the cylinder base 49 is not fixed. A bearing box 58 that is rotatably attached to the other side of the outer peripheral portion of the bearing housing 57 via a bearing 57, and a male screw 59 and a male screw 59 that are formed on the outer peripheral portion of the bearing box 58, and are provided inside the connecting member 38. And a screw feed portion 61 composed of the female screw 60 formed. Here, the gear drive unit 56 meshes with the rotation drive source 62 (for example, a hydraulic motor), a small gear 63 attached to the rotation shaft of the rotation drive source 62, and the small gear 63, and a part of the connection member 38. A large gear 64 penetrating the side portion, and a holding member 65 for attaching the large and small gears 64 and 63 and the rotation drive source 62 to the side portion of the connecting member 38 are provided. Further, on one side of the outer peripheral portion of the bearing housing 58, a driving gear 66 that is screwed into the large gear 64 and rotates the bearing housing 58 is provided. Reference numeral 45 denotes a fixing member for the bearing housing 58.

With the above configuration, when the rotational drive source 62 is stopped, the clutch operating seat 33 is inserted into the clutch receiving seat 40 by operating the cylinder 50 (the clutch operating seat 33 and the clutch receiving seat 40 are connected). While connecting the screw cylinder 31 to the connecting member 38, the third spline coupling 41 between the spline 43 of the clutch receiving seat 40 and the spline 44 of the clutch sleeve 37 is released. As a result, the screw cylinder 31 is released from the connection state with the arbor shaft 15 via the clutch sleeve 37 and is fixed to the mounting base 17 so that the screw cylinder 31 can be prevented from rotating.

Here, since the arbor shaft 15 and the sleeve 16 are spline-coupled, when the arbor shaft 15 is rotated at a very low speed by a rotational drive source, the arbor shaft 15 and the sleeve 16 perform the same rotational operation (at the same rotational speed in the same direction). Rotate). Since the second female screw 29 and the second male screw 30 of the screw cylinder 31 are different in spiral direction at the same feed pitch, when the arbor shaft 15 and the sleeve 16 perform the same rotation operation, the screw cylinder 31 On the other hand, the arbor shaft 15 and the sleeve 16 are moved by the same distance in opposite directions along the axial direction.

Further, when the clutch operating seat 33 is detached from the clutch receiving seat 40 by the operation of the cylinder 50, the connection between the screw cylinder 31 and the connecting member 38 is released, and the spline 43 of the clutch receiving seat 40 and the clutch sleeve 37 are disconnected. A third spline coupling 41 is formed between the spline 44. As a result, the screw cylinder 31 is released from the mounting base 17 and can rotate, and is connected to the arbor shaft 15 via the clutch sleeve 37. For this reason, when the arbor shaft 15 is rotated, the screw cylinder 31 can be rotated integrally with the arbor shaft 15. Further, since the arbor shaft 15 and the sleeve 16 are spline-coupled, the arbor shaft 15 and the sleeve 16 perform the same rotation operation. Thereby, the screw cylinder 31 and the sleeve 16 are also rotated in the same manner, and the horizontal rolls 19 and 20 can be rotated in the same rotational motion by the rotation of the arbor shaft 15.

Further, when the rotation drive source 62 is rotated, the drive gear 66 can be rotated via the small gear 63 and the large and small gear 64, and the bearing housing 58 can be rotated along with the drive gear 66. Here, since the bearing box 58 rotates while the male screw 59 formed on the outer peripheral portion of the bearing box 58 is screwed into the female screw 60 of the connecting member 38, the bearing box 58 is connected to the connecting member 38 (the other side of the arbor shaft 15). Is moved along the axial direction of the bearing housing 58 with respect to the mounting base 17) for fixing the bearing housing 14 supporting the bearing housing 14). Therefore, when the clutch actuating seat 33 is put in the clutch receiving seat 40 and the screw cylinder 31 is not rotated, and the rotation drive source 62 is rotated and the bearing box 58 is rotated, the screw cylinder 31 is moved along with the movement of the bearing box 58. Moves in the axial direction.

As a result, the arbor shaft 15 and the sleeve 16 are also moved in the axial direction (same as the moving direction of the screw cylinder 31), so that the body width variable horizontal roll device 10 is moved along the axial direction of the arbor shaft 15. be able to. For this reason, when the center position between the horizontal rolls 19 and 20 of the trunk width variable horizontal roll apparatus 10 and the center position between the horizontal rolls 19a and 20a of the trunk width variable horizontal roll apparatus 10a do not coincide, Either one or both of the variable horizontal roll device 10 and the variable barrel width type horizontal roll device 10a are moved along the axial direction of the arbor shafts 15 and 15a, so that the center position between the horizontal rolls 19 and 20 is horizontal. The center position between the rolls 19a and 20a can be matched.

As shown in FIG. 2, an annular projection 46 is provided on the inner side of the other side of the sleeve 16, and a compression spring is provided between the tip of the screw cylinder 31 screwed into the arbor shaft 15 and the sleeve 16 and the projection 46. 47 is arranged. As a result, backlash of the arbor shaft 15, the screw cylinder 31, and the sleeve 16 that are screwed together can be reduced.

Subsequently, the roll body width between the horizontal rolls 19 and 20 is increased from W1 to W2 online as shown in FIG. 4 using the body width variable horizontal roll apparatus 10 according to the embodiment of the present invention. The case will be described.
First, as shown in FIG. 5, with the rotational drive source 62 stopped, the cylinder 50 of the screw cylinder switching means 32 is operated to move the clutch sleeve 37 toward the screw cylinder 31 so that the clutch operating seat 33 is moved to the clutch receiving seat. Connect to 40. As a result, the connection between the screw cylinder 31 and the arbor shaft 15 is released by releasing the third spline coupling 41 between the clutch sleeve 37 and the screw cylinder 31, and the screw cylinder 31 is attached to the mounting base via the connecting member 38. 17 and the screw cylinder 31 is in a rotation-stopped state.

Next, the arbor shaft 15 is rotated at a slow speed. When the arbor shaft 15 rotates, the arbor shaft 15 and the sleeve 16 are spline-coupled, so that the arbor shaft 15 and the sleeve 16 perform the same rotation operation. Here, since the second female screw 29 and the second male screw 30 of the screw cylinder 31 have different spiral directions at the same feed pitch, the arbor shaft 15 extends along the axial direction with respect to the screw cylinder 31. The sleeve 16 moves toward one side and moves along the axial direction toward the other side by the same distance as the arbor shaft 15. For this reason, since the roll cylinder width can be adjusted while maintaining the roll cylinder width center of the drive side horizontal roll 19 and the work side horizontal roll 20 on the center line of the rolling line, it is easy to adjust the roll cylinder width online. .

And since the roll drum width can be adjusted while maintaining the roll drum width center of the drive side horizontal roll 19 and the work side horizontal roll 20 on the center line of the rolling line, the drive side horizontal roll 19 after adjusting the roll drum width and A centering device that has been conventionally required to make the center of the roll body width of the work-side horizontal roll 20 coincide with the center of the rolling line becomes unnecessary.
Further, since the position of the screw cylinder 31 is always a fixed position when adjusting the roll barrel width, the position of the support member necessary for the screw cylinder 31 can also be fixed at a fixed position. For this reason, it is possible to easily modify the roll positioning mechanism 21 to an existing horizontal roll device to modify the trunk width variable horizontal roll device 10.

Further, as shown in FIG. 4, the slide margin ΔS between the drive side horizontal roll 19 and the work side horizontal roll 20 when the roll body width is increased from W1 to W2 is the drive side horizontal roll 19 and the work side horizontal roll. Since 20 moves the same distance in the opposite direction, ΔS = (W2−W1) / 2, which is ½ of the roll cylinder width change allowance (W2−W1). For this reason, even if the size range of the H-shaped steel 11 to be rolled is large, the change margin of the roll body width of the drive side horizontal roll 19 and the work side horizontal roll 20 can be reduced, and the roll positioning mechanism 21 becomes compact. .
In order to reduce the roll barrel width between the drive side horizontal roll 19 and the work side horizontal roll 20, the arbor shaft 15 that rotates at a low speed may be rotated in reverse.

An annular protrusion 46 is provided on the inner side of the other side of the sleeve 16, and a compression spring 47 is disposed between the protrusion 46 and the tip of the screw cylinder 31 screwed into the arbor shaft 15 and the sleeve 16. Backlash of the arbor shaft 15, the screw cylinder 31, and the sleeve 16 that are screwed together can be reduced, and the sleeve 16 can be moved with high responsiveness when the arbor shaft 15 is rotated.

When the roll body widths of the drive-side horizontal roll 19 and the work-side horizontal roll 20 reach W2, the slow rotation of the arbor shaft 15 is stopped. Then, as shown in FIG. 6, the cylinder 50 of the screw cylinder switching means 32 is operated to move the clutch sleeve 37 to the other end side of the arbor shaft 15, and the clutch operating seat 33 is detached from the clutch receiving seat 40. As a result, the connection between the screw cylinder 31 and the connecting member 38 is released, and a third spline coupling 41 is formed between the spline 43 of the clutch receiving seat 40 and the spline 44 of the clutch sleeve 37. As a result, the screw cylinder 31 is released from the mounting base 17 and is in a rotatable state, and is connected to the arbor shaft 15 via the clutch sleeve 37 (the next rolling, that is, the H-shaped steel having a different size). Ready for rolling).

As shown in FIG. 1, when rolling the H-section steel 11, first, the arbor shafts 15 and 15 a of the variable barrel width type horizontal roll apparatuses 10 and 10 a are respectively rotated based on the rolling conditions. In addition, since the state of the trunk width variable horizontal roll apparatus 10 and 10a at the time of rolling is the same, the trunk width variable horizontal roll apparatus 10 is demonstrated.

When the arbor shaft 15 is rotated, the screw cylinder 31 and the arbor shaft 15 rotate integrally. Since the arbor shaft 15 and the sleeve 16 are spline-coupled, the arbor shaft 15 and the sleeve 16 perform the same rotation operation. As a result, the screw cylinder 31 and the sleeve 16 are rotated in the same direction, and the rotation of the arbor shaft 15 causes the drive-side horizontal roll 19 attached to the arbor shaft 15 and the work-side horizontal roll 20 attached to the sleeve 16 to It rotates with the same rotation. And it will be in a rolling standby state by rotating the rolls 22 and 24 based on rolling conditions, respectively.

As shown in FIG. 1, when the rolling of the H-section steel 11 is started, the H-section steel 11 is pushed by the scissors rolls 22 and 24, so that the drive-side horizontal roll 19 and the work-side horizontal roll 20 are moved to each other. The horizontal force Fv / 2 acts on each. Here, the horizontal force Fv / 2 acting on the side surface of the drive side horizontal roll 19 during rolling operation is transmitted to the arbor shaft 15 to which the drive side horizontal roll 19 is attached. Further, the horizontal force Fv / 2 acting on the side surface of the work side horizontal roll 20 is transmitted to the sleeve 16 to which the work side horizontal roll 20 is attached, and the screw cylinder via the screw cylinder 31 screwed to the sleeve 16. It is transmitted to the arbor shaft 15 that is screwed to 31. Here, one side of the arbor shaft 15 is rotatably fixed to the mounting base 17 by a pressing member 48 of the bearing housing 13 provided on the arbor shaft 15, and the other side of the arbor shaft 15 is a screw cylinder to be screwed. 31, a bearing box 58 attached to the screw cylinder 31, and a connecting member 38 screwed to the bearing box 58, and is fixed to the mounting base 17.

Therefore, the horizontal force Fv transmitted to the arbor shaft 15 is transmitted to the mounting base 17 and supported by the compression reaction force. When the horizontal forces Fv / 2 acting on the side surfaces of the drive side horizontal roll 19 and the work side horizontal roll 20 are different, the difference between the horizontal forces Fv / 2 is supported by the mounting base 17.
On the other hand, the vertical force Fh / 2 acting on the drive-side horizontal roll 19 in rolling the H-section steel 11 is supported by the mounting base 17 via the bearing box 13 that supports the arbor shaft 15, and is applied to the work-side horizontal roll 20. The acting vertical force Fh / 2 is supported by the mounting base 17 via the bearing box 14 that supports the sleeve 16.

As described above, the barrel width variable horizontal roll device 10 does not require the screw shaft, the thrust load receiving nut, and the screw bearing box, which are conventionally required, so the barrel width variable horizontal roll device 10 is made compact. be able to.
Further, the horizontal force Fv transmitted to the arbor shaft 15 is directly passed through the arbor shaft 15 on one side of the arbor shaft 15 and on the other side of the arbor shaft 15, a screw cylinder 31 and a screw cylinder 31 having a diameter larger than that of the arbor shaft 15. Since it is supported by the mounting base 17 via the connecting member 38 having a larger diameter, the load load on the drive side horizontal roll 19 and the work side horizontal roll 20 is increased as compared with the case where a conventional screw shaft is used. Can do.

As described above, the present invention has been described with reference to the embodiment. However, the present invention is not limited to the configuration described in the above-described embodiment, and the matters described in the scope of claims. Other embodiments and modifications conceivable within the scope are also included.
Further, the present invention also includes a combination of components included in the present embodiment and other embodiments and modifications.

10, 10a: Horizontal roll device with variable barrel width, 11: H-section steel, 12: Universal rolling mill, 13, 13a, 14, 14a: Bearing box, 15, 15a: Arbor shaft, 16, 16a: Sleeve, 17, 17a: Mounting base, 18: Web, 19, 19a: Drive side horizontal roll, 20, 20a: Work side horizontal roll, 21, 21a: Roll positioning mechanism, 22: Reed roll, 23: Flange, 24: Reed roll, 25: flange, 26, 26a: spline, 27: first male screw, 28: first female screw, 29: second female screw, 30: second male screw, 31: screw tube, 32: screw tube switching means, 33: Clutch operating seat, 34: Clutch base, 35: Bearing, 36: Second spline coupling, 37: Clutch sleeve, 38: Connecting member, 39: Moving drive source 40: clutch seat, 41: third spline coupling, 42: pressing member, 43, 44: spline, 45: fixing member, 46: protrusion, 47: compression spring, 48: pressing member, 49: cylinder base, 50 : Cylinder, 51: piston rod, 52: latching part, 53: attachment ring, 54: connecting pin, 55: screw cylinder moving means, 56: gear drive part, 57: bearing, 58: bearing box, 59: male screw, 60: Female screw, 61: Screw feed section, 62: Rotation drive source, 63: Small gear, 64: Large gear, 65: Holding member, 66: Drive gear

Claims (3)

Is connected rotation drive source on one side, and Arbor shaft supported on both sides by a bearing box, a sleeve on one side to the other side from the central portion of the arbor shaft is mounted is splined central portion of said arbor shaft A drive-side horizontal roll that is fixed to one side, and presses one side of the material to be rolled during rolling; and a work-side side horizontal roll that is fixed to one side of the sleeve and presses the other side of the material to be rolled during rolling In the trunk width variable type horizontal roll apparatus, the roll side positioning mechanism that adjusts the position of the drive side horizontal roll and the work side horizontal roll with respect to the arbor shaft,
The roll positioning mechanism includes: 1) a first male screw formed on a part of the other side of the arbor shaft; 2) a first female screw formed on the other side of the sleeve; A second female screw that is screwed to one male screw, a second male screw that is screwed to the first female screw is formed on the outside, and a screw cylinder that is screwed to the arbor shaft and the sleeve, 4) A screw cylinder switching means for stopping rotation of the screw cylinder at the time of adjusting the interval between the drive side and work side horizontal rolls, and integrating the rotation of the screw cylinder and the arbor shaft at the time of rolling;
2. The body width variable horizontal roll device according to claim 1, wherein the second female screw and the second male screw formed in the screw cylinder have different spiral directions at the same feed pitch. 2. The body width variable horizontal roll device according to claim 1, wherein the screw cylinder switching means includes: 1) a clutch seat fixed to the other side of the screw cylinder; and 2) the arbor via a second spline connection. A clutch that is mounted on the other side of the shaft so as to be movable in the axial direction, and that unifies the screw cylinder via the arbor shaft and the clutch receiving seat by coupling the clutch receiving seat and the third spline when moving on the other side. A clutch base having a sleeve, 3) a clutch operating seat attached to a predetermined position of the clutch sleeve via a bearing, and abutting the clutch receiving seat when the clutch sleeve moves to one side; and 4) the clutch base An actuator that moves in the axial direction,
The actuator can move the clutch base to one side to adjust the distance between the drive side and work side horizontal rolls, and the actuator can move the clutch base to the other side to connect the third spline. The arbor shaft and the screw cylinder are integrated with each other. 3. The body width variable horizontal roll device according to claim 1, wherein an annular protrusion is provided on the inner side of the other side of the sleeve, and the tip of the screw cylinder and the protrusion screwed to the arbor shaft and the sleeve. A compression spring is arranged between the two, and a back roll of the arbor shaft, the screw tube, and the sleeve, which are respectively screwed together, is reduced, and the body width variable horizontal roll device.

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