JP5674538B2 - Horizontal roll device with variable trunk width - Google Patents

Description

[Technical Field] The present invention relates to a body width variable type horizontal roll apparatus capable of arbitrarily adjusting a body width of a horizontal roll used in a finish rolling mill for H-section steels offline.

Conventionally, in a universal rolling mill for H-section steel, means for rolling H-section steel with different dimensions by changing the horizontal roll barrel width of the universal mill online is described in, for example, Patent Document 1 and Patent Document 2. ing.
Patent Documents 1 and 2 disclose a variable body width type horizontal roll apparatus having a pair of horizontal rolls for rolling H-shaped steel flanges and a web connecting the flanges, and one of the horizontal rolls is driven by a mill motor. The other horizontal roll is fixed to the non-drive side (work side) hollow shaft connected to the drive side (drive side) roll shaft by a spline. Yes.

Inside the hollow shaft, there is provided a screw shaft in which the roll shaft and the shaft center coincide with each other and a male screw is formed in part, and the male screw of this screw shaft is screwed with the female screw formed inside the hollow shaft. doing. A clutch mechanism is provided at the end of the hollow shaft for switching between a lock side for locking the rotation of the screw shaft and a side for connecting the screw shaft to the hollow shaft.

Then, when the roll shaft is driven by the mill motor while the screw shaft is fastened by operating the clutch mechanism, the female screw moves relative to the fixed male screw, and as a result, the left and right horizontal rolls provided on the hollow shaft The interval of changes. As the horizontal roll moves, the center position on the left and right is also shifted from the rolling line. I have to.

Furthermore, as a conventional example, the details of the trunk width variable horizontal roll apparatus provided on the non-driving side (work side) will be described with reference to FIG. 5A shows a state during rolling operation (roll cylinder width W is min (minimum)), and FIG. 5B shows a condition when the roll cylinder width is changed (roll cylinder width is changed from min (minimum) to max (maximum). ))).
In FIG. 5, 60 is a hollow shaft, 61 is a screw shaft, 62 is a female screw provided on the hollow shaft 60, 63 is a male screw attached to the hollow screw piece 70, 64 is a horizontal roll on one side, 65 Denotes a bearing box, 66 denotes a screw shaft bearing, 67 denotes a roll shaft connected to a rotational drive source, and 68 denotes a spline connecting the roll shaft 67 and the hollow shaft 60.

The roll shaft 67 and the screw shaft 61 are separated from each other, and the clutch mechanism is omitted in FIG. A flange 71 is provided on the outer peripheral portion of the hollow screw piece 70 on which the male screw 63 is formed, and a thrust load receiving nut 73 that is screwed into the male screw 72 formed on the screw shaft 61 is provided.

The hollow screw piece 70 meshes with a hollow shaft 60 having a female screw 62 that is screwed into a male screw 63 on the outer periphery of the hollow screw piece 70. A screw shaft 61 is rotatably inserted into the hollow screw piece 70, and a thrust load receiving nut 73 connected to the hollow screw piece 70 is screwed to the screw shaft 61 via a male screw 72. The horizontal reaction force applied to the horizontal roll 64 is supported by the screw shaft bearing 66 via the thrust load receiving nut 73.
Thus, since there is no screw mechanism on the inner periphery of the hollow screw piece 70, a mechanism for the thrust load receiving nut 73 is required.

The distance L ′ between the axial center of the bearing housing 65 and the axial center of the screw shaft bearing 66 is expressed by the following equation (1).
L ′ = La + Lb + Lc + Ld + S (1)
La: Distance from the center of the bearing box to the end of the hollow shaft at the body width Wmin Lb: Flange width dimension of the hollow screw piece Lc: Distance from the end of the thrust load receiving nut to the center of the screw shaft bearing Ld: Width dimension S of the thrust load receiving nut The distance L ′ between the center of the roll moving amount bearing box 65 and the center of the screw shaft bearing 66 includes the width dimension of the thrust load receiving nut 73.

Furthermore, the screw length P ′ of the hollow screw piece 70 is expressed by the following equation (2).
P ′ = m + S (2)
m: Load Fv support dimension S: Roll movement amount Thus, the screw length P ′ is the movement amount S of the horizontal roll 64 adjusted by the male screw 62 of the hollow screw piece 70 and the length of the load Fv support dimension. Is required.

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

However, the trunk width variable type horizontal roll apparatus described above 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, since the center positions of the left and right horizontal rolls are deviated from the rolling line, a centering device for shifting the entire apparatus is necessary, and the entire apparatus is complicated.
(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 a long screw with a hollow shaft and a hollow screw piece for changing the roll drum width. Engagement and the extra length of the width of the thrust load receiving nut are necessary, and there is a problem that it cannot be made compact.

The present invention has been made in view of such circumstances, and can be used even with a large roll load. Further, the clutch mechanism and the centering device are unnecessary, the size can be reduced, and the trunk width can be changed by a simple operation. An object of the present invention is to provide a horizontal roll device with variable trunk width.

A horizontal roll apparatus with variable trunk width according to the present invention that meets the above-mentioned object is provided with a drive shaft connected to one side and a roll shaft supported on both sides by a bearing box, and left and right hollows mounted on the roll shaft by spline coupling. A body roll variable type horizontal roll apparatus having a shaft, a pair of left and right horizontal rolls fixed to the left and right hollow shafts, and positioning means for respectively determining the mounting positions of the left and right hollow shafts with respect to the roll shaft In
The positioning means includes 1) a first male screw formed on a part of the roll shaft, 2) a first female screw formed on the inner side of the hollow shaft, and 3) an inner side of the first male screw. A hollow screw piece formed with a second female screw to be screwed and formed with a second male screw screwed to the first female screw on the outside; and 4) the movable in the axial direction of the roll shaft. Rotation prevention means for preventing rotation of the hollow screw piece is provided, and the second female screw and the second male screw of the hollow screw piece are different in spiral direction.

Therefore, in the body roll variable horizontal roll device according to the present invention, when the roll shaft is rotated by the drive source while the rotation of the hollow screw piece is stopped by the rotation preventing means, the roll shaft is engaged by the spline connection. The hollow shaft rotates, and the first female screw and the first male screw formed on a part of the roll shaft rotate in the same direction. On the other hand, the second female screw of the hollow screw piece and the second male screw have different spiral directions, and the first female screw and the first male screw are connected to the second male screw and the second female screw of the hollow screw piece, respectively. Since they are screwed together, the hollow screw piece moves in the axial direction, and the hollow shaft also moves in the same direction as the movement direction of the hollow screw piece with respect to the hollow screw piece.

In the body width variable horizontal roll device according to the present invention, the rotation preventing means passes through a groove-shaped latching portion provided on an outer peripheral portion of the hollow screw piece and a part of the bearing box, and the latching It is preferable to have the detachable latching member into which the tip portion is fitted. Thus, the hollow screw piece can be reliably prevented from rotating, and the hollow screw piece can be moved only in the axial direction.

In the body width variable horizontal roll device according to claims 1 and 2, the clutch mechanism is unnecessary, and as a result, the roll shaft can be increased in diameter, so that the load load of the horizontal roll is increased. Can do. In addition, since the left and right positioning means are provided to adjust the position of the horizontal roll, respectively, a centering device is not required. Since the positioning means can be reduced in size, the positioning means can be easily remodeled to a barrel width variable horizontal roll apparatus by adding to the existing horizontal roll apparatus.

In particular, in the body width variable horizontal roll device according to claim 2, the rotation preventing means passes through a groove-shaped latching portion provided on the outer peripheral portion of the hollow screw piece and a part of the bearing box, and the latching portion Therefore, the rotation preventing means has a simple structure and can be easily removed, and the roll barrel width changing operation performed off-line can be performed quickly.

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 detail drawing which shows the positioning means of the same trunk width variable type horizontal roll apparatus. (A), (B) is explanatory drawing at the time of rolling operation of the same cylinder width variable type horizontal roll apparatus, respectively, and explanatory drawing at the time of roll cylinder width change. (A), (B) is the longitudinal cross-sectional view of the screwing means provided in a positioning means, respectively, and a cross-sectional view. (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.

Embodiments of the present invention will be described below with reference to the drawings.
As shown in FIG. 1, variable waist width horizontal roll devices 21, 21 a according to an embodiment of the present invention are used in an H-section steel rolling mill, for example, a universal rolling mill, and are offline, variable width horizontal horizontal apparatus. The roll body width of the roll devices 21 and 21a is changed. The body width variable horizontal roll devices 21 and 21a are respectively left and right horizontal rolls 10 and 10a (in the case of the body width variable horizontal roll device 21a, horizontal rolls 10b and 10c) and left and right hollow shafts 11 and 11a. Positioning means 20 and 20a are provided.

FIG. 1 shows a universal rolling mill that includes variable roll width horizontal roll devices 21 and 21a.
Further, the universal rolling mill rolls the H-section steel 30 by rotating a pair of the upper body width variable horizontal roll device 21 and the lower body width variable horizontal roll device 21a in the vertical direction. Furthermore, in the left-right direction, the hard rolls 22, 22a push and roll the H-section steel 30 from the left-right direction on the counter drive side and the drive side.
And according to the dimension (web length) of the H-section steel 30, the trunk width of the trunk width variable horizontal roll apparatus 21 (that is, the interval between the left and right horizontal rolls 10, 10a), the trunk width variable horizontal roll apparatus 21a The body width (that is, the distance between the left and right horizontal rolls 10b and 10c) is set by the positioning means 20 and 20a, respectively, and corresponds to various sizes of H-section steel rolling.

Here, since the upper and lower trunk width variable horizontal roll apparatuses 21 and 21a have the same structure, the upper trunk width variable horizontal roll apparatus 21 will be described below.
A roll driving motor (not shown) serving as a drive source is connected to the roll drive coupling 17 at one end of the roll shaft 12 of the variable body width type horizontal roll device 21 to drive the horizontal rolls 10 and 10a. The other end is a roll shaft fixed bearing 16, and the roll shaft 12 is rotatably fixed.

The body width variable horizontal roll device 21 is divided into a drive side driven by a roll drive motor (not shown) and a non-drive side having no driving force, and has a left-right symmetrical structure. The explanation will focus on the side structure.
On the non-driving side, the roll shaft 12 and the hollow shaft 11 are splined by a spline 15 (in the case of the driving-side horizontal roll 10a, coupled by the hollow shaft 11a and the spline 15a). Thereby, the driving force of the roll shaft 12 driven by the motor is transmitted to the hollow shaft 11. As a result, the roll shaft 12 and the hollow shaft 11 rotate together and are splined so that the hollow shaft 11 can move in the axial direction of the roll shaft 12. A horizontal roll 10 is fixed to the hollow shaft 11.

Further, the hollow screw piece 13 constituting the positioning means 20 is screwed with the roll shaft 12 and the hollow shaft 11. Furthermore, the roll shaft 12 is supported and fixed by a bearing box 14 formed of a rotatable bearing.
The drive side will be described briefly. The hollow screw piece 13a constituting the positioning means 20a is similarly screwed with the roll shaft 12 and the hollow shaft 11a. The bearing box 14a similarly supports and fixes the roll shaft 12.
The positioning means 20 adjusts the mounting position of the hollow shaft 11, that is, the position of the horizontal roll 10, and the positioning means 20 a adjusts the mounting position of the hollow shaft 11 a, that is, the position of the horizontal roll 10 a, so that they are independent of each other. Since the position adjustment is performed, a centering device that aligns the center of the trunk width determined by the horizontal roll 10 and the horizontal roll 10 a with the center of the H-shaped steel 30 becomes unnecessary.

Next, the rolling reaction force applied to the body width variable horizontal roll device 21 will be described. For example, when Fv2> Fv1, the horizontal roll 10 supports the rolling reaction force (horizontal force), and the differential action force (Fv2-Fv1) between the action force Fv1 of the hard roll 22 and the action force Fv2 of the hard roll 22a. It is transmitted to the roll shaft 12 through the hollow shaft 11 and the hollow screw piece 13. The roll shaft 12 is held in position by the roll shaft fixed bearing 16 and receives the acting force Fv2. In this case, the rolling reaction force (horizontal force) can be transmitted to the roll shaft fixed bearing 16 only by the hollow shaft 11 and the hollow screw piece 13 without requiring a separate new mechanism, and the load load of the horizontal roll 10 is increased. Can do. This is because a small-diameter screw shaft provided separately for loading the horizontal roll 10 is not required.
The rolling reaction force (vertical force) Fh1 is also held in position by the bearing box 14 to which a difference in force (not shown) acting in the opposite direction is applied. Since this is not related to the present invention, a detailed description thereof will be omitted.

As shown in FIG. 2, the positioning means 20 includes a first male screw 26 formed on a part of the roll shaft 12, a first female screw 27 formed on the inner side of the hollow shaft 11, and a first inner side. A hollow screw piece 13 formed with a second female screw 29 screwed to the male screw 26 and formed with a second male screw 28 screwed to the first female screw 27 on the outside, and movable in the axial direction A rotation prevention means 25 for preventing the rotation of the hollow screw piece 13 is provided, and the second female screw 29 and the second male screw 28 of the hollow screw piece 13 have different spiral directions.

That is, the hollow shaft 11 is provided with a through hole, and the first female screw 27 is provided on the inner peripheral surface of the end portion. And the roll axis | shaft 12 has penetrated the said through-hole. A hollow screw piece 13 having a second male screw 28 on the outer peripheral surface and a second female screw 29 on the inner peripheral surface is inserted into the through hole. The second male screw 28 of the hollow screw piece 13 is screwed with the first female screw 27 of the hollow shaft 11. Further, the second female screw 29 of the hollow screw piece 13 is also screwed with the first male screw 26 provided at the end of the roll shaft 12.
Therefore, the hollow shaft 11 to which the horizontal roll 10 is fixed and the roll shaft 12 are screwed to the hollow screw piece 13. In addition, the feed pitch of the 2nd external thread 28 and the 2nd internal thread 29 may be the same, and may differ.

The rotation preventing means 25 includes the latch member 18, the notch hole 31, and the latch portion 19.
The bearing housing 14 is provided with a notch hole 31. The latching member 18 passes through the notch 31, and the tip of the latching member 18 is provided on the outer periphery of the flange 33 that is built at the end of the hollow screw piece 13 and has a larger outer diameter than the second male screw 28. The hollow screw piece 13 can be moved in the axial direction, but cannot be rotated. Here, the latching portion 19 is constituted by a groove provided in the axial direction of the hollow screw piece 13. Thus, the rotation preventing means 25 is composed of a simple pin-shaped latching member 18, a notch hole 31, and a groove-shaped latching portion 19. Variable operation can be performed quickly.

In this way, the hollow screw piece 13 can be reliably prevented from rotating because the circumferential position is fixed to the bearing housing 14. Moreover, since the latching part 19 is provided in the flange 33 with a large diameter, a small load can be given and the rotation of the hollow screw piece 13 can be stopped, and the latching part 19 uses a small and small thing. It is also possible.

Next, the operation of the trunk width variable horizontal roll device according to the present embodiment will be described.
When the roll barrel width variable operation is performed offline, the rotation prevention means 25 prevents the hollow screw piece 13 from rotating. That is, the latch member 18 is inserted into the notch hole 31 of the bearing housing 14 and inserted into the latch portion 19 provided on a part of the outer periphery of the flange 33 of the hollow screw piece 13. Rotation is prevented and movement is possible only in the axial direction.
Since the roll shaft 12 and the hollow shaft 11 rotate in the same direction, the second male screw 28 provided in the hollow screw piece 13 and the action of the second female screw 29 having a different spiral direction with respect to the second male screw 28 are provided. Thus, the moving direction of the hollow screw piece 13 with respect to the roll shaft 12 and the moving direction of the hollow shaft 11 with respect to the hollow screw piece 13 are the same in the axial direction.

FIG. 3A shows an explanatory diagram during rolling operation (the roll body width W is min (minimum)).
The rolling reaction force applied to the variable width horizontal roll device 21 on the counter drive side during rolling operation will be described.
Since the H-section steel 30 is pushed in by the hard rolls 22 and 22a, a horizontal force Fv is applied to the horizontal roll 10. Here, the horizontal force Fv acting on the side surface of the horizontal roll 10 during rolling operation is transmitted to the roll shaft fixed bearing 16 via the hollow screw piece 13 and the roll shaft 12 which are screwed with the hollow shaft 11, and the compression reaction. Supported by force.
Here, when specifically described (when Fv2> Fv1), there is a difference between Fv2 and Fv1 applied to the horizontal rolls 10, 10a, so the horizontal force Fv becomes the difference Fv2-Fv1 and the axial center. Is supported from the roll shaft fixed bearing 16 toward the roll shaft fixed bearing 16.

That is, the second male screw 28 on the outer periphery of the hollow screw piece 13 and the second female screw 29 on the inner periphery with different spiral directions are engaged with the hollow shaft 11 and the roll shaft 12, respectively. It is possible to directly support acting forces in both directions and outwards. As a result, the screw shaft 61 and the thrust load receiving nut 73, which are separately required in the conventional example to receive the difference between the left and right horizontal forces Fv (Fv2-Fv1), become unnecessary (see FIG. 5).

Further, it is not necessary to provide the screw shaft separately from the roll shaft. As a result, the roll neck diameter of the roll shaft 12 is larger than that of the conventional screw shaft, so that the load load of the horizontal roll can be increased. .
As a result, since the conventional screw shaft was provided separately, the roll neck diameter of the roll shaft, which was previously only about 40% of the effective diameter of the roll shaft, can be integrated to be 85% or more. It was. As a result, it was possible to increase the hard roll allowable reaction force value of the horizontal roll for rolling from 100 tons to 250 tons.

FIG. 3B is an explanatory diagram when the roll drum width is changed (the roll drum width W is changed from min (minimum) to max (max)).
Basically, when the roll barrel width is changed, the latching member 18 is inserted into the notch hole 31 of the bearing housing 14 and is different from the latching portion 19 provided on a part of the outer periphery of the flange 33 of the hollow screw piece 13. Is included. Thereby, the position of the circumferential direction of the hollow screw piece 13 is fixed to the bearing box 14 by the latching member 18, and rotation of the hollow screw piece 13 is prevented. In this state, the roll driving motor is driven to rotate the roll shaft 12 and the spline-coupled hollow shaft 11.

For example, as described with reference to FIG. 2, the roll shaft 12 has a right-hand thread, and the hollow screw piece 13 that is screwed in when the roll shaft 12 rotates to the right is the center (center) of the roll shaft 12. Move in the direction. Further, since the hollow screw piece 13 has a different spiral direction (left-hand thread) on the outer periphery, when the hollow shaft 11 that is screwed with this rotates in the same direction (right) as the roll shaft 12, the hollow screw piece 13 is similarly hollow. The screw piece 13 also moves in the axial direction (center).

As shown in FIG. 3B, the distance L between the center of the bearing housing 14 and the center of the roll shaft fixed bearing 16 is expressed by the following equation (3).
L = La + Lb + Lc + S (3)
La: Distance from the bearing box center to the end of the hollow shaft at the case width Wmin Lb: Flange width dimension of the hollow screw piece Lc: Distance from the hollow screw piece to the roll shaft fixed bearing center S: Amount of roll movement As a result, the bearing box 14 The distance L between the center in the axial direction and the center in the axial direction of the roll shaft fixed bearing 16 eliminates the need for the thrust load receiving nut 73 which is the conventional example shown in FIG. As a result, it can be designed compactly in the roll axis direction.

Furthermore, the screw length P of the hollow screw piece 13 is expressed by the following equation (4).
P = m + S / 2 (4)
m: Load Fv supported dimension S: Roll movement amount, that is, screw length P is a synergistic screwing of a male screw provided in the hollow screw piece 13 and a female screw having a different spiral direction compared to the hollow screw piece 70 of the conventional example. As a result, the roll moving amount S can be shortened by ½, which is advantageous when the required moving amount S of the horizontal roll 10 is large. As a result, the positioning means 20 can be miniaturized. It becomes easy to add the positioning means 20 and remodel it into the body width variable horizontal roll device 21.

As a result of designing an actual actual machine, the distance L was reduced from 5245 mm to 3920 mm. As a result, since the positioning means 20 has become compact, it can be applied to an existing horizontal roll apparatus.
As a result, the positioning means 20 can be installed on the non-driving side and the positioning means 20a on the driving side, and the positions of the horizontal rolls 10 and 10a can be determined independently on the left and right sides. No longer needed.

Next, the screwing means 35 will be described with reference to FIGS. 4 (A) and 4 (B).
During the rolling operation, the hollow screw piece 13 and the roll shaft 12 are fixed by screw connection, and the latch member 18 is removed. Therefore, a screwing means 35 for fixing the hollow screw piece 13 and the roll shaft 12 is provided. The screwing means 35 includes a fixing screw 36 and a screwing hole 32. For example, a screwing hole 32 is further provided on the bottom surface of the latching part 19 of the hollow screw piece 13. A female screw is cut on the inner surface of the screwing hole 32, and a male screw of a fixing screw 36 is inserted into the screw screw hole 32 to fix the roll shaft 12 and the hollow screw piece 13. Thus, the hollow screw piece 13 and the roll shaft 12 can be reliably fixed by providing the screwing means 35. That is, during operation, the latching member 18 is removed, and the fixing screw 36 provided in the screwing hole 32 is turned to fix the hollow screw piece 13 to the roll shaft 12.

An example of manually changing the roll drum width is shown in FIG.
Here, the fixing screw 36 is removed and the roll shaft 12 and the hollow shaft 11 are stopped in an off-line operation. Since only the hollow screw piece 13 is manually rotated directly, the rotation prevention means 25 is not fixed to the bearing housing 14. For this purpose, an arm 23 is formed on the outer periphery of the hollow screw piece 13 and, for example, a protruding jig (not shown) is inserted into the arm hole formed in the arm 23, and the jig is manually rotated. The hollow screw piece 13 is rotated. In this way, by rotating the hollow screw piece 13, the hollow shaft 11 and the roll shaft 12 can move to opposite sides in the axial direction, and the operation of changing the roll body width of the horizontal roll 10 can be performed.

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 embodiment, and the matters described in the scope of claims. Other embodiments and modifications conceivable within the scope are also included.

10, 10a, 10b, 10c: horizontal roll, 11, 11a: hollow shaft, 12: roll shaft, 13, 13a: hollow screw piece, 14, 14a: bearing box, 15, 15a: spline, 16: roll shaft fixed bearing , 17: Roll drive coupling, 18: Latching member, 19: Latching part, 20, 20a: Positioning means, 21, 21a: Horizontal roll device with variable trunk width, 22, 22a: Hard roll, 23: Arm, 25: rotation prevention means, 26: first male screw, 27: first female screw, 28: second male screw, 29: second female screw, 30: H-shaped steel, 31: notch hole, 32: screw hole 33: flange, 35: screwing means, 36: fixing screw, 60: hollow shaft, 61: screw shaft, 62: female screw, 63: male screw, 64: roll, 65: bearing box, 66: screw shaft bearing, 67 :Low Axis 68: spline, 70: hollow screw piece, 71: flange, 72: external thread, 73: Thrust load receiving nut

Claims (2)

A drive source is connected to one side, and a roll shaft supported on both sides by a bearing box, left and right hollow shafts attached to the roll shaft by spline coupling, and left and right pairs fixed to the left and right hollow shafts, respectively. In a horizontal roll apparatus with variable trunk width having a horizontal roll and positioning means for determining the mounting positions of the left and right hollow shafts relative to the roll shaft,
The positioning means includes 1) a first male screw formed on a part of the roll shaft, 2) a first female screw formed on the inner side of the hollow shaft, and 3) an inner side of the first male screw. A hollow screw piece formed with a second female screw to be screwed and formed with a second male screw screwed to the first female screw on the outside; and 4) the movable in the axial direction of the roll shaft. A body roll variable type horizontal roll device having rotation prevention means for preventing rotation of the hollow screw piece, wherein the second female screw and the second male screw of the hollow screw piece have different spiral directions. 2. The body width variable horizontal roll device according to claim 1, wherein the rotation preventing means passes through a groove-shaped latching portion provided on an outer peripheral portion of the hollow screw piece and a part of the bearing box, and A trunk roll variable type horizontal roll apparatus characterized by having a detachable latch member in which a tip part fits into a stop part.

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