JPH0123202B2 - - Google Patents

Description

[Detailed description of the invention] Industrial applications The present invention relates to a drive device for an inclined rolling mill.

More particularly, the present invention relates to a drive for an inclined rolling mill having a plurality of universal joints, the drive being adjustable such that speed fluctuations due to the universal joints are minimized.

BACKGROUND OF THE INVENTION A tilt rolling mill is used as a tilt roll perforator or a tube polishing machine for manufacturing seamless steel pipes. In these inclined rolling mills, a plurality of rolls are connected to a drive source via a universal joint, and the inclination angles of the rolls are changed according to rolling conditions.

For this reason, when power is transmitted using a so-called cross-pin type universal joint, even if the drive side rotates at a constant speed, speed fluctuations will appear in the rolls, and this tendency tends to occur especially in the case of cross-type inclined rolling, which has been adopted in recent years. is strong.

This problem will be explained with reference to the attached drawings.

A typical structure of a cross pin type universal joint is schematically shown in Fig. 1. As can be seen in the figure, approximately Y is provided at both ends of the drive shaft 1 and the driven shaft 2.
The letter-shaped yokes 3 and 4 are installed, and after rotating 90 degrees to face each other so that the tips of the yokes 3 and 4 occupy complementary positions, the bearings located at the tips of each of the yokes 3 and 4 are A universal joint is formed by connecting a cross-shaped connecting member (cross pin) 6 consisting of shafts 5 and 5' that are engaged with each other and are perpendicular to each other. It is well known that in this cross-pin type universal joint, the transmission of speed and torque from the drive shaft 1 to the driven shaft 2 is not constant.

If the rotation angle and angular velocity of the drive shaft 1 and the driven shaft 2 are respectively θ ₁ , θ ₂ , ω ₁ , ω ₂ , and the angle formed by the rotation axes of the drive shaft 1 and the driven shaft 2 is α (operating angle), The following formula holds.

tanθ ₂ = tanθ ₁・cosα ω ₂ /ω ₁ = cosα/1−sin ² θ ₁・sin ² α As is clear from the above equation, even if the rotation of the drive shaft 1 is constant, the rotation of the driven shaft 2 The rotation angle and angular velocity of the drive shaft 1 change in accordance with the rotation of the drive shaft 1.
Incidentally, the actual changes are as shown by curves a and b in FIG.

In other words, such fluctuations in the rotation angle and angular velocity also appear as fluctuations in the torque transmitted to the driven shaft 2, as shown by curve c in FIG. 2.

Furthermore, as shown in FIG. As shown in FIG. 4, the speed fluctuation that occurs in the shaft 12 is a combination of the fluctuation that occurs in the first driven shaft 2, shown by the curve p, and the fluctuation in the second driven shaft, shown by the curve q. .
At this time, if the first fluctuation and the second fluctuation are out of phase, the overall fluctuation resulting from the combination of curves p and q will cancel each other out, but if they are in phase, the overall fluctuation will be multiplied and become a large value. .

As described above, in a power transmission device equipped with two sets of universal joints, the phases of speed fluctuations of the first universal joint and the second universal joint are adjusted so that the fluctuation is minimized as a whole. This is very important in the design or installation of such devices.

Here, the operating angles of the universal joints are the same (α = β in Figure 3), and the center lines of the drive shaft, first driven shaft, and second driven shaft are in the same plane (Figure 3 ψ
= 0) and the yoke of the first driven shaft (Fig. 14,
7) are in the same phase, the fluctuations are completely canceled out and the second driven shaft rotates the same as the drive shaft. In many cases, these three conditions are satisfied before use.

However, in inclined drilling machines or polishing machines for manufacturing seamless steel pipes, the operating angles of the joints may not be the same (α≠β) due to various rolling conditions, and the plane formed by the drive shaft and the first driven shaft may The phase angle ψ between the plane formed by the first and second driven shafts often becomes non-zero. Especially when performing cross-type inclined rolling,
The degree of variation is so large that the speed fluctuation in this case cannot be ignored.

Here, the tilt type rolling mill refers to a rolling mill in which the rolling rolls rotate at an inclination angle γ (variable) from the pass line when viewed from the front, as shown in the front view and plan view in Figure 8 A and B, respectively. The cross-type inclined rolling mill further refers to a rolling mill in which the rolling rolls are rotated by a crossing angle δ (variable if necessary) from the pass line when viewed from a plane.

OBJECT OF THE INVENTION An object of the present invention is to provide a driving device for an inclined rolling mill equipped with two sets of universal joints, in order to solve the problems of the prior art described above. To provide a drive device that enables operation with minimizing speed fluctuations occurring in a driven shaft by adjusting angles such that speed fluctuations occurring in both universal joints cancel each other out. .

Structure of the Invention In order to achieve the above object, the present invention provides a first driven shaft connected to a drive shaft via a cross-pin type universal joint, and a first driven shaft and another cross-pin type universal joint. A drive device for an inclined rolling mill, comprising a second driven shaft that is connected to the roll via the shaft and supports a roll, the first driven shaft being separable into two parts, and the end face of the separated part being a face gear. Provided is a drive device for an incline rolling mill, comprising: a drive device for an inclined rolling mill, characterized in that speed fluctuations occurring in the second driven shaft can be minimized by changing the rotational phase of the second driven shaft with respect to the drive shaft; be done.

The present invention will be explained below with reference to Examples, but it goes without saying that these Examples do not limit the scope of the present invention in any way.

Embodiment FIG. 5 is a diagram schematically showing a drive device according to the present invention.

The output shaft 32 of the power source 30 transmits rotation to the driven shaft 36 via the universal joint 34 .
The driven shaft 36 is provided with a telescoping mechanism 38 on its upstream side, and at the same time, this telescoping mechanism 38 of the driven shaft 36
A holder 42 that supports the following telescopic portion 40 is provided near the midpoint. Further, this holder 42 is configured to extend and contract the telescopic portion 40 of the driven shaft in the axial direction by means of a hydraulic device 46 via an arm 44 . The holder 42 allows the driven shaft 36 to expand and contract, and also supports the weight of the driven shaft 36 as a whole.

The telescoping mechanism 38 has teeth cut on the inner periphery of the lower end of the upstream side of the driven shaft 36 parallel to the rotating shaft, and teeth cut on the outer periphery of the upstream end of the telescoping portion 40 of the driven shaft 36. It is movable and enables power transmission by meshing teeth parallel to the rotation axis (spline connection).

Further, the downstream end of the telescoping portion 40 of the driven shaft 36 is divided into a portion integral with the telescoping portion 40 and a second portion.
and a portion 50 constituting the yoke portion of the universal joint. A face gear 48 is provided on the end surface of the portion that is integral with the telescopic portion 40, and a face gear 49 that meshes with the face gear 48 is provided on the end surface of the short portion 50 that connects with the second universal joint. The rotation transmitted via the driven shaft 36 is transmitted to the second universal joint 52. Thus,
The second universal joint 52 transmits power to driven equipment (not shown) while changing the direction of the rotating shaft.

FIG. 6 is an enlarged view of the configuration near the second universal joint 52 of the device according to the present invention.

54 in the figure is a rolling roll, and the output from a power source not shown in this figure is the first driven shaft 3.
6 and the second universal joint 52 to the rolling roll 54.

Below the universal joint 52 are the universal joint 52 and face gears 48, 4.
A support device 62 is provided with a platform 60 having sufficient dimensions to support 9.
This support device 62 raises and lowers the platform 60 as required by means of hydraulic cylinders 64. This support device 62 supports the platform 60
The universal joint 52 and the face gear 4 are connected to the universal joint 52 and the face gear 4 through liners 70 and 71 having protrusions 68 and 69 that fit into grooves 66 and 67 provided all around the outer circumference of the face gears 48 and 49, respectively.
I support 8,49. The liners 70 and 71 are separate bodies.

In the power transmission device as described above, the procedure for exchanging the rolls and aligning the phases of the two universal joints, which is the object of the present invention, will be explained with reference to FIGS. 6 and 7.

First, after turning off the power and stopping the power, the hydraulic means 64 is activated to raise the platform 60 of the support device 62, and the second universal joint 52 and the engaged face gears 48, 49 are raised.
support. At this time, liners 70 and 71 are sandwiched between the face gears 48 and 49, the universal joint 52, and the platform 60, so that these members will not be damaged by contact with the platform 60. In this state,
Face gear 48, 4 freed from any load
9 on its central axis.

Next, the hydraulic device 46 is operated, and the driven shaft 36
The retractable portion 40 of is moved along the axial direction toward the power source (to the position shown by the chain line in FIG. 7), and the meshing of the face gears 48 and 49 is completely disengaged. At this time, since the liners 70 and 71 are separate bodies as described above, the liner 70 also slides on the platform 60 as the telescopic portion 40 moves, and can still perform the protective function of the face gear 48.

In this separated state, the roll 54,
Its appurtenances (not shown), second universal joint 52 and face gear 49 are completely released.

According to the present invention, in this state, phase adjustment is performed to reduce speed fluctuations during power transmission caused by the second universal joint 52 and the first universal joint 34.

The phase adjustment can be easily performed by starting the power source and rotating the driven shaft 36 at a slow speed.

The accuracy of phase adjustment improves in proportion to the number of teeth of the face gear, but is naturally within the range of mechanical constraints.

As described above, according to the present invention, the phase adjustment between the first universal joint and the second universal joint can be arbitrarily set.

Therefore, it is possible to easily adjust the phase even in a cross-type inclined rolling mill.

After setting in this way, by performing the operation in reverse to the above-mentioned operation and connecting the driven shaft 36 and the second universal joint 52, it is possible to operate the power transmission device in the mode with the least fluctuation. It is.

Further, since the device according to the present invention can be used not only as a phase adjustment means but also as a roll exchange device, equipment costs can be saved.

In case of roll replacement, face gear parts 48, 4
9 is not separated, but the universal joint side and the roll side are separated at the mating surface 73. At this time, other than the fact that the second universal joint portion 52 moves together with the driven shaft 36 and the liners 70 and 71 also move together, the movement and operation method of the platform 60 and hydraulic device 46 are completely different from those in the case of phase adjustment. The same is true.

Effects of the Invention As detailed above, by adjusting the phase of the speed fluctuation of the driven shaft caused by the universal joint before operation using the device of the present invention, the rotation transmission device equipped with two sets of universal joints can be adjusted. It becomes possible to minimize speed fluctuations occurring in the second driven shaft.

Incidentally, for adjusting the phase of the speed fluctuation of the driven shaft, existing equipment can be used except for dividing the driven shaft through meshing face gears, and the equipment cost is small.

[Brief explanation of drawings]

FIG. 1 is a schematic diagram of a cross-pin type universal joint. Figure 2 shows the rotation angle, angular velocity, and torque fluctuation of the driven shaft of the cross pin type universal joint. FIG. 3 is a schematic diagram of a transmission mechanism equipped with two cross-pin type universal joints. Figure 4 shows the first transmission mechanism with two cross-pin type universal joints.
3 is a graph showing fluctuations in the angular velocity of the driven shaft and the second driven shaft, and fluctuations in the angular velocity of their combined output side. FIG. 5 is a diagram schematically showing an apparatus according to the present invention. FIG. 6 is an enlarged view of the structure near the second universal joint of the device according to the present invention. FIG. 7 is a detailed view of the face gear portion of FIG. 6. FIG. 8 is a model diagram of a cross-type inclined rolling mill, where A shows a front view and B shows a plan view. (Main reference numbers), 1... Drive shaft, 2... Driven shaft, 3 and 4... Yoke, 11... Universal joint, 12... Second driven shaft, 30... Power source, 32... ... Output shaft, 34 ... Universal joint, 36 ... Driven shaft, 38 ... Telescopic mechanism,
42...Holder, 46...Hydraulic system, 48, 49
... face gear, 52 ... second universal joint, 54 ... rolling roll, 60 ... platform, 62 ... support device, 64 ... hydraulic cylinder, 66 and 67 ... groove, 68, 69 ...
...Protrusion, 70, 71...Liner, 72...Mounting bolt.

Claims (1)

[Claims] 1 A first driven shaft connected to the drive shaft via a cross pin type universal joint, and a second driven shaft connected to the first driven shaft via another cross pin type universal joint and supporting the roll.
A drive device for an inclined rolling mill comprising a driven shaft, wherein the first driven shaft is separable into two parts, an end face of the separated part is constituted by a face gear, and the second driven shaft is separated from the driving shaft. A drive device for an inclined rolling mill, characterized in that the rotation phase of a driven shaft can be changed.