JPS5941136B2 - Gear wear amount detection method in gear coupling - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a method for detecting the amount of gear wear in a gear coupling, which is intended to detect the amount of gear wear with simple steps and a simple configuration.

Gear couplings are used in almost all rolling lines as couplings for transmitting torque, and their sizes vary from about 200 to 1000.

A breakage accident of the gear of this gear coupling will immediately lead to a line stoppage, and preventing this accident is an extremely important issue. Conventionally, the amount of wear on the gears of a gear coupling has been detected mainly visually by disassembling the gear coupling when the line is stopped, such as during daily maintenance.

However, with this conventional method, it is necessary to disassemble all gear couplings, regardless of whether the gears are worn or healthy, especially when the gears are in good condition, which is extremely cumbersome. It was hot. The present invention
In view of the problems of the conventional gear coupling, it was created with great effort, and its characteristics are as follows. The amount of wear on both gears is detected by measuring the backlash between the drive side and load side gears based on the difference between the time interval between the drive side pulse and the load side pulse during forward rotation and the same time interval during reverse rotation. At the point.

Embodiments of the present invention will be described below with reference to the drawings.

1 to 3, the figures show a gear coupling 1 used, for example, in a rolling line, and inner gears 6, 6 are attached to each shaft 4, 5 on the drive side 2 and load side 3, respectively. ,
Outer gears 7, 7 are provided which mesh with these inner gears 6, 6, respectively, and these outer gears 7, 7 are connected via bolts 8. The upper front inner and outer gears 6 and 7 are slidable relative to each other in the axial direction in order to absorb axial fluctuations between the two gears. Both ends of gear coupling 1, that is, drive side 2
Further, photoelectric or magnetic pulse detectors 9, 9, which detect one pulse every rotation of each shaft 4, 5 on the load side 3, are fixedly provided.

9a is a pulse detection target (reflective tape) fixed to the shaft 4 on the drive side, and 9b is a pulse detection target (reflective tape) fixed to the load side shaft 5.

By rotating these pulse detection targets 9a and 9b together with the shafts 4 and 5, the fixed side pulse detectors 9 and 9 are rotated together with the shafts 4 and 5.
One pulse is detected every one rotation of the Further, arrow X indicates the direction of rotation. FIG. 4 is a simplified diagram of the meshing state of each gear when the gear coupling 1 rotates in the normal direction.
The front tooth surface of the gear 6 on the first drive side 2 in the normal rotation direction contacts the rear tooth surface of the gear 7 on the load side 3, and the rear tooth surface of the gear 6 on the first drive side 2 and the load 11113 A backlash l occurs between the gear 7 and the front side tooth surface.

In the above meshing state during forward rotation, the pulse detection object 9a fixed to the drive side shaft 4 and the pulse detection object 9b fixed to the load side shaft 5 have a positional deviation of 11 in the circumferential direction. are doing.

During normal rotation, the pulse detectors 9 detect pulses as shown in FIG.

That is, since the pulse detection object 9a on the drive side and the pulse detection object 9b on the load side have a relative positional deviation in the circumferential direction when the gears 6 and 7 are in the normal rotation meshing state, This positional shift 11 in the circumferential direction causes a generation time difference t1 between the 5th drive side pulse A and the load side pulse B.

That is, as shown in FIG. 6, during normal rotation, pulse A is first generated for each rotation, and then pulse B is generated after a time delay of T. Conversely, by multiplying the time difference t1 by the circumferential speed, the circumferential positional deviation distance of both pulse detection targets 9a and 9b can be calculated. That is, when the rotational speed is F and the on-axis mounting radius of the pulse detection objects 9a and 9b is R, the circumferential positional deviation distance 1 is 2πRf,tl. Fifth
The figure is a simplified diagram of the meshing state of each gear when the gear coupling 1 is reversed, and a backlash l occurs at the abutting portion of the tooth surface shown in FIG. 4 above. In the meshing state during the above-mentioned reverse rotation, the circumferential positional deviation of both pulse detection objects 9a and 9b is 2, and the relationship with the above 1 is 12=1, +l, as is clear from FIGS. 4 and 5.

As shown in FIGS. 5 and 7, the circumferential positional deviation distance 12 of both pulse detection targets 9a and 9b during reverse rotation can be calculated as 2πRf2t2, as described above, where the pulse generation time difference is T2 and the rotation speed is F2. .

The circumferential positional deviation distance 1 during the reverse rotation is changed by 2 times the backlash of the gears 6 and 7 compared to the normal rotation.
Therefore, by finding the difference from the positional deviation distance 11 during forward and reverse rotation, the backlash l can be calculated. Therefore, in order to measure the wear amount of the gears 6 and 7, it is sufficient to measure the backlash 2, so first, the rotation speed f1 during normal rotation and the pulse detection time difference t1 at that time are measured.

Next, the coupling is rotated in the reverse direction, and the rotational speed F2 during the reverse rotation and the pulse detection time difference T2 at that time are measured.

However, from the above data, the backlash is calculated, but for convenience of calculation, if the initial backlash is set to O, then
The backlash, that is, the amount of wear Δx is calculated by the following equation.

Δx=2πr・1f,・T,−F2・T2l However, r
: Gear diameter (pitch circle radius).

In order to obtain more accurate results, firstly, we need to acquire a large amount of data and reduce the effects of uneven rotation of the rotating shaft, electrical noise, and vibration of the pulse detector through statistical processing. It is preferable to do so.

Also, if the pulse width changes due to a change in the distance between the pulse detector and the axis, even if the backlash is O,
The time interval between the rising points of both the drive-side pulse A and the load-side pulse B causes a difference between the time interval Tm during forward rotation and the time interval Tn during reverse rotation, resulting in an error in the measurement of backlash. becomes. In order to eliminate this error, the positive
In any case of reverse rotation, it is preferable to measure the time interval Tc between the centers of the drive-side pulse A and the load-side pulse B, and measure the pulse time interval unrelated to changes in pulse width. In Fig. 9, the figure shows the signal processing circuit of this detection method, and considering statistical processing etc., a 1-chip microcomputer is introduced, and further versatility is sought, and the pulse detector 9→
Amplifier circuit 10 → waveform shaping circuit 11 → counter circuit 12 →
Processing is performed as follows: 1-chip microcomputer 13 in which gear diameter, number of data to be taken, etc. are set → display device 14.

In Fig. 10, the figure shows an example of detection by this detection method, where the horizontal axis is the detected displacement and the vertical axis is the bump. Approximately the same value is taken.

According to the present invention, the backlash of the gear, that is, the amount of wear can be easily detected without disassembling the gear coupling, and therefore, the gear coupling can be inspected easily and accurately. As a result, the damage can be prevented, which is beneficial.

Furthermore, this inspection is accomplished with a simple configuration using a pulse detector or the like, which makes this invention an excellent invention.

[BRIEF DESCRIPTION OF THE DRAWINGS] The drawings show an embodiment of the present invention, in which FIG. 1 is a side partial sectional view of a gear coupling, FIG. 2 is a partial sectional view taken along the line - in FIG. 1, and FIG. An assembly diagram of the gear coupling ring, Fig. 4 is a simplified cross-sectional view of the gear mesh during forward rotation, Fig. 5 is a simplified cross-sectional view of the gear mesh during reverse rotation, Fig. 6 is a pulse diagram during normal rotation, and Fig. 7 is the reverse rotation. FIG. 8 is a pulse diagram showing another preferred embodiment of time interval measurement, FIG. 9 is a circuit diagram, and FIG.
Figure 0 is a diagram of a detection example. 1...Gear coupling spring, 2...Drive side, 3...
・Load side, 6...Inner gear, 7...Outer gear, 9.
...Pulse detector, A...Drive side pulse, B...Load side pulse, tpi...Time interval between both pulses during forward rotation, T
2... Time interval between both pulses during reverse rotation, l... Backlash.

Claims (1)

[Claims] 1 A pulse detector that detects one pulse per rotation is installed on each of the drive side and load side of the gear coupling, and the detection time interval of the drive side pulse and load side pulse during forward rotation and the same time interval during reverse rotation are determined. A gear wear amount detection method in a gear coupling that measures the backlash between the drive side and load side gears based on the difference in the amount of gear wear.