JPH01238766A - Roller table - Google Patents

Abstract

PURPOSE:To obtain a preferable backlash value between teeth composed of plural gear group by providing the title roller table composed of fixed gears with divided teeth fixed on a rotating shaft and mobile gears slidable in the axial direction and also providing a pressing means for restricting a minimum value of a gap between both gears. CONSTITUTION:The gear device of a roller table is composed of plural divided gears alternatively meshed with an integral gear. The divided gears 2 are composed of a fixed gear 2a rigidly mounted on a rotating shaft 7 and a movable gear 2b which is movable in the axial direction and not movable to the shaft 7. The gap S between both gears 2a, 2b is pushed in the approaching direction by a connecting bolt 4 and conical spring 5. The teeth of respective gears are spiral gears so that it is possible to obtain a preferable backlash between an integral gear and divided gears 2 and the rattling between rollers of the roller table is prevented, thus obtaining the synchronous rotation with high accuracy.

Description

Detailed Description of the Invention [Field of Industrial Application] The present invention relates to a roller table installed as a material conveying device in a rolling mill or the like. This invention relates to a gear train type gear device that is assembled to a table body and drives each table roller to rotate uniformly.

[Conventional technology]

As shown in FIGS. 5 and 6, a roller table installed as a material conveying device in a rolling mill, etc., has a large number of table rollers 16 arranged between a pair of frames 17 with their rotating axes parallel to each other and the same. It is constructed by combining a roller table main body 15 that is assembled in parallel while being positioned on a plane, and a large number of gears, and transmits rotational force from a motor 13 that is a driving source to each table roller 16. Gear device 1
It is composed of.

The gear device 1° constituting this roller table can be broadly classified into a gear train type and a bevel gear type, depending on the type of gear used and the method of transmitting rotational force.

Of these two gear devices 1', the gear train type one is constructed by arranging a large number of helical gears in a casing 11, and the output shaft, which is the rotation axis, is connected to each of the roller table main bodies 15. A drive gear 20 connected to the rotation shaft of the table roller 16 and an intermediate gear 21 that transmits rotational force between the drive gear 20 are arranged such that the rotation shafts of the gears 20 and 21 are located parallel to each other, and they are adjacent to each other. drive gear 20
It has a configuration in which an intermediate gear 21 is positioned between them.

That is, in the case of the gear device 1° shown in FIGS. 5 and 6, the intermediate gear 21 located at the right end in the figure is rotationally driven by the motor 13, and the intermediate gear 21 at the right end is meshed in series by rotationally driving. By simultaneously rotating the drive gear 20 and the intermediate gear 21, and thereby rotating each drive gear 20 in the same direction, each table roller 16 of the roller table main body 15 is rotated in the same direction, and the material is removed. It is transported in a fixed direction.

[Problem to be solved by the invention]

In the gear device 1 in this roller table, which is constructed by combining a large number of helical gears, there is always backlash at the meshing part between each intermediate gear 21 that transmits the rotational force of the motor 13 and the drive gear 20. There is a looseness called. According to actual measurements, the backlash (hereinafter simply referred to as B) of one meshing portion between the intermediate gear 21 and the driving gear 20 is usually 0.7 to 1.5.

Now, if the rotation direction of the motor 13 is reversed in order to reverse the direction in which the material is conveyed by the roller table, the n-th gear from the motor 13 will accumulate a play of BXn, and this accumulated play will cause n The rotational movement of the table roller 16 coupled to the drive gear 20, which is the th gear, is caused by the rotation of the table roller 1
This results in a delay corresponding to the accumulated backlash relative to the rotational movement of step 6. Table roller 1 farthest from this motor 13
According to actual measurements, the delay in rotation of the table roller 16 closest to the motor 13 of No. 6 reaches as much as 4 to 9 degrees of play in terms of the roller outer circumference.

For this reason, when trying to convey a stationary material on the roller table main body 15, variations in the timing of rotational drive between the table rollers 16 due to this accumulated backlash may cause the material to move between the outer periphery of the table roller 16 and the material. This slip causes problems such as scratches on the back side of the material and noise and damage caused by collisions between gears when starting and stopping.

This backlash occurs even if the gear cutting and polishing accuracy of the gears is maximized, and the machining accuracy of the casing 11 that holds the gears when assembled and the bearings increases due to gaps, etc., so for each pair of gears. An adjustment mechanism is required to minimize backlash. Furthermore, since banklash increases due to wear of gear teeth, a mechanism is required to adjust backlash to a minimum in response to wear of teeth. Furthermore, if the bank crash is minimized too much, there is a risk that the teeth between the gears will jam, causing excessive force to be applied to the gears and causing damage to the teeth. A tooth escape function such as a torque limiter is required.

The present invention was devised to solve the problems in the conventional technology described above, and it reduces or eliminates the backlash that tends to occur between the gears that transmit rotational force to each table roller, and The purpose is to prevent excessive force from acting on the

[Means to solve the problem]

Means for the roller table according to the present invention to achieve the above object is to move the roller table main body, which is composed of a large number of table rollers arranged in parallel, through a gear device using a large number of beveled gears of a gear train type. It is a driven roller table, the gear device is composed of a large number of split gears and integral gears arranged in mesh with each other alternately, and the split gears are immovably fixed to the split gear rotation shaft, which is a rotating shaft. a fixed gear, and a movable gear attached to the rotating shaft of the split gear so that it cannot idle but is slidable in the axial direction; There is provided a pressing means for regulating and setting the minimum value of the gap formed between the fixed gear and the movable gear.

Further, the pressing means is attached to a coupling bolt assembled between the fixed gear and the movable gear, and is fitted and assembled to the coupling bolt to apply elasticity in a direction that urges the movable gear toward the fixed gear. It is preferable that the gear is composed of a disc spring and an adjustment bolt that regulates and sets the minimum value of the gap between the fixed gear and the movable gear.

[Effect]

(See Fig. 4 below) The split gear 2 is connected to the split gear rotation shaft 7.
The fixed gear 2a is assembled into a fixed gear 2a immovably attached to the split gear rotating shaft 7, and the movable gear 2b is attached to the split gear rotating shaft 7 so that it cannot idle but is slidable in the axial direction. Since both the moving gear 2b and the moving gear 2b are helical gears,
Tooth line a of fixed gear 2a and tooth line b of movable gear 2b
Both are inclined with respect to the axial direction of the split gear rotating shaft 7. Similarly, since the integral gear 3 with which this divided gear 2 meshes is also a helical gear, the tooth line C of this integral gear 3 is also inclined with respect to the axial direction of the divided gear rotating shaft 7.

Therefore, the movable gear 2b is moved in a direction that reduces the gap S along the axial direction of the split gear rotating shaft 7, that is, the fixed gear 2
When moved in the direction approaching a, the tooth thickness of the segmented gear 2 that meshes with the negative body gear 3 increases, thereby reducing or eliminating the backlash B between the segmented gear 2 and the integral gear 3. Can be done.

Furthermore, if an overtorque exceeding the torque set by the urging force of the pressing means acts on the split gear 2, the fixed gear 2
The divided gear 2, which had achieved torque transfer between the integral gear 3 and either the moving gear 2b or the moving gear 2b, is fixed as the moving gear 2b overcomes the biasing force of the pressing means due to this overtorque. It moves in the direction away from the gear 2a, and as a result of this movement, the load from one integral gear 3 is stopped being received by both the fixed gear 2a and the moving gear 2b, so that it is applied only to either the fixed gear 2a or the moving gear 2b. This prevents tooth breakage accidents due to overload.

Furthermore, since the minimum value of the gap S between the fixed gear 2a and the movable gear 2b is regulated to a constant value by the pressing means provided on the split gear 2, the urging force of the pressing means against the movable gear 2b is reduced. The lower limit of the reduction in backlash B due to the action can be regulated, thereby making it possible to prevent the occurrence of an accident in which the teeth of the split gear 2 and the integral gear 3 are damaged. In other words, the smaller the gap S, the smaller the backlash B. Therefore, if the urging force from the pressing means remains applied to the moving gear 2b, the backlash B can be completely reduced. However, as described above, if the backlash B is made too small, tooth meshing will occur between the segmented gear 2 and the integral gear 3, resulting in tooth breakage. Therefore, by appropriately regulating the minimum value of the gap S using the pressing means, the backlash B can be set to a value that does not cause tooth jamming, thereby preventing tooth breakage accidents.

〔Example〕

FIG. 1 is a plan view showing one embodiment of a roller table according to the present invention, FIG. 2 is a front view of a gear device used in the embodiment illustrated in FIG. FIG. 2 is a vertical cross-sectional view of a main part showing a specific configuration of the gear device shown in the figure.

In the embodiment shown in FIGS. 1 to 3, the roller table main body 15 is constructed by rotatably assembling a large number of table rollers 16 between a pair of frames 17 so as to be positioned in parallel and on a single horizontal plane. and each table roller 16
A roller shaft 18, which is a rotating shaft of the gear device 1, is made to protrude from the frame 17 on the side where the gear device 1 is disposed.

The tooth type device 1 placed near the roller table main body 15 is mounted in a steel plate casing 11 that is immovably installed on a base 12, and includes a number of split gears 2 and an integral gear corresponding to the number of table rollers 16. 3 are engaged with each other alternately and rotatably assembled via a bearing 10, and the tip of the split gear rotating shaft 7 of each split gear 2 protruding from inside the casing 11 is connected to the end of the split gear rotating shaft 7 via a gear camp ring 14. Frame 1
The output shaft of a motor 13 as a drive source is connected to the split gear rotation shaft 7 at the end. That is, each divided gear 2 serves as a driving gear for each table roller 16, and the integral gear 3 serves as an intermediate gear.

The pressing means provided on the split gear 2 is installed between the fixed gear 2a and the movable gear 2b, passing through both gears 2a and 2b, and with its axis parallel to the axis of the split gear rotating shaft 7. A plurality of coupling bolts 4 (preferably around 6 bolts) are assembled in a shape, and a plurality of coupling bolts 4 are fitted and assembled to the coupling bolts 4 to exert elasticity in the direction of pressing the movable gear 2b toward the fixed gear 2a. The disc spring 5 is screwed and fixed to the fixed gear 2a, and its tip, which has been hardened to prevent wear, protrudes from the end surface of the fixed gear 2a facing the movable gear 2b, and this protruding tip is moved. An adjustment bolt 6 that regulates and sets the minimum value of the gap S by coming into contact with the end surface of the gear 2a.
It is composed of.

The coupling bolt 4 can function to prevent the movable gear 2b from rotating relative to the fixed gear 2a due to its assembly structure with the gears 2a and 2b.
In the embodiment shown in FIG. 3, the assembly of the movable gear 2b to the split gear rotation shaft 7, which cannot idle but is slidable in the axial direction, is formed between the split gear rotation shaft 7 and the movable gear 2b. This is achieved by the spline 8.

In FIG. 1, when the motor 13 is driven in the forward rotation direction,
This rotational force is transmitted to each gear along the solid line arrows in FIG. That is, the rotational force from the motor 13 is transmitted from the fixed gear 2a of the first split gear 2 to the first integral gear 3, and the rotational force transmitted to the first integral gear 3 is transmitted to the second integral gear 3.
It is transmitted from the movable gear 2b of the divided gear 2 to the second integral gear 3 via the fixed gear 2a, and thereafter transmitted to the final (sixth in the illustrated embodiment) divided gear 2 in this order. Conversely, when the motor 13 is driven in the reverse direction, this rotational force is transmitted to each gear along the broken line arrows in FIG.

That is, the rotational force from the motor 13 is transmitted as follows: moving gear 2b of the first split gear 2→first integral gear 3→fixed gear 2a of the second split gear 2→moving gear 2b of the second split gear 2→
The signal is transmitted through the path of the second integral gear 3, and thereafter is transmitted in this order to the final divided gear 2.

When torque exceeding the specified value is applied to the split gear 2, each disc spring 5
The gear 2b moves in the direction of elastically deforming and increasing the gap S.
, thereby moving both gears 2 to the single integral gear 3.
The torque applied by meshing a and 2b at the same time is divided and borne. Moreover, the setting of the gap S is achieved arbitrarily by adjusting the screwing position of the adjustment bolt 6 with respect to the fixed gear 2a.

It should be noted that the gear force/puncture force of the coupling 14 also affects the synchronous drive of each table roller 16, so it is regulated to a minimum value.

According to the embodiment shown in FIGS. 1 to 3, the amount of play (runout amount) of the outer periphery of the sixth and final table roller 16 was actually measured with the first table roller 16 fixed. As a result, the amount of play was 0.5 (au
nl or less, and it was confirmed that highly accurate synchronous rotation of each table roller 16 could be obtained.

〔Effect of the invention〕

Since the present invention is configured as described above, it exhibits the effects described below.

Since the backlash between the gears that transmit rotational force can be minimized, it is possible to achieve high-precision synchronous rotational drive of a large number of table rollers, which are rotationally driven bodies. The steel material to be transported can be transported satisfactorily without any scratches on the back surface thereof, and the direction of transport can be reversed extremely smoothly.

The backlash that occurs in a gear device made up of a large number of gears is also increased by the wear of each gear, and although the wear of each gear is never uniform, backlash occurs independently for each split gear. -14= Since the backlash can be adjusted, by adjusting the backlash according to the degree of gear wear,
Conventionally, gears had to be replaced due to wear every year, but in the case of the present invention, bank lash adjustment for each segmented gear allows the roller table main body to be driven smoothly for more than three years without replacing gears. can be achieved.

When overtorque acts on one gear of a split gear,
The action of the pressing means prevents this overtorque from being received by both gears, and the backlash value between the individual gears can be arbitrarily set to the best value. It is possible to reliably prevent the occurrence of damage to the vehicle, thereby achieving extremely safe operation.

The pressing means provided on the split gear is composed of a plurality of coupling bolts, a plurality of disc springs fitted into the coupling bolts, and an adjustment bolt threadedly coupled to one of the gears. The structure is extremely simple, and the adjustment of the backluff value using the adjustment bolt is achieved by simply adjusting the screwing position of the adjustment bolt with respect to one gear, so the adjustment operation is extremely simple. This can be achieved with high precision.

[Brief explanation of the drawing]

FIG. 1 is an overall plan view showing an embodiment of a roller table according to the present invention. 2 is a front view showing the arrangement of gears in the gear device shown in the embodiment of FIG. 1. FIG. FIG. 3 is a longitudinal cross-sectional view showing a specific configuration of essential parts of the gear device shown in FIG. 2. FIG. FIG. 4 is an explanatory diagram for explaining the operating principle of the gear device according to the present invention. FIG. 5 is a plan view showing a schematic configuration of a conventional roller table. 6 is a front view showing the arrangement of gears of the gear device on the roller table shown in FIG. 5. FIG. Explanation of symbols 1: Gear device, 2; Split gear, 2a; Fixed gear, 2b;
Moving gear, 3; integral gear, 4; coupling bolt, 5; flat spring, 6: adjustment bolt, 7; split gear rotation shaft, 9; integral gear rotation shaft, 10; bearing, 11; casing, 12; mounting on base , 13; motor, 14; gear coupling,
15; roller table body, 16; table roller,
17; Frame, 18; Roller shaft, 1"; Gear device, 20;
Drive gear, 21; intermediate gear, S; gap, B; backlash, a; tooth line of fixed gear, b; tooth line of moving gear,
C: Teeth line of integral gear. Applicant: Kawasaki Steel Co., Ltd.=16=

Claims (2)

[Claims] (1) A roller table in which a roller table main body composed of a large number of table rollers arranged in parallel is driven via a gear device using helical gears of a gear train type, the gear device being driven by a large number of table rollers arranged in parallel. Consisting of segmented gears and integral gears arranged in mesh with each other alternately, the segmented gears are assembled to a fixed gear immovably fixed to a rotating shaft and a rotating shaft so that they cannot idle but are slidable in the axial direction. a movable gear, and includes a pressing means for applying a force toward the fixed gear to the movable gear, and regulating and setting a minimum value of the gap formed between the fixed gear and the movable gear. A roller table made of (2) The pressing means is attached to a coupling bolt assembled between the fixed gear and the movable gear, and is fitted and assembled to the coupling bolt to apply elasticity in a direction that urges the movable gear toward the fixed gear. 2. The roller table according to claim 1, comprising: a disc spring to act on; and an adjustment bolt for regulating and setting a minimum value of the gap between the fixed gear and the movable gear.