JPS624927B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a metal wheel used in wire drawing work, and particularly to an eccentric metal wheel that can prevent an increase in wire drawing tension when a protector, joint, etc. pass.

Conventionally, when wires are sent from one metal wheel to another during wire extension work, the tension of the wire is stable and smooth wire transfer is performed, but when the protector, joint, etc. pass through the metal wheel, the tension increases. The tension increases abnormally, and the tension can sometimes increase by about 50% compared to normal operation, depending on the angle of the feed line, the shape of the wire guide groove on the wire wheel, etc. This time will be explained in detail with reference to FIGS. 1 and 2. In FIG. 1, 1 is the supporting part of the steel tower, 2 is the metal wheel suspended from the supporting part 1, 3 is the electric wire, 4 is the protector, and T ₀ , T ₁ , and T ₂ are the tensions of each part.
As shown in FIG. 1, when the protector 4 is applied to the metal wheel 2, the tensions T ₀ and T ₁ increase. Figure 2 shows this rise in tension T ₁ confirmed using an oscilloscope, and shows that when tension T ₁ was stable it was 4050 kg.
When protector 4 crosses over gold wheel 2, it increases to a maximum of 5930 kg in ₁ hour. Naturally, the tension associated with this
T ₀ also increases. When the protector 4 climbs over the metal wheel 2, the tension _T1 decreases once due to reaction and then returns to a stable state.

In this way, during wire transmission work using conventional wire wheels, the tension on the wire increases abnormally when the wire wheel passes through the protector, etc., which may affect the strength of the steel tower, and the wire rope used to pull the wires. Problems have also arisen in the selection of overhead line cars. This also causes wire knicking to increase. Furthermore, if there is a large difference between the upper and lower limits of the tension T ₁ as described above, there is a problem that the electric wire swings greatly due to this tension variation.

Therefore, it has become an important issue to take appropriate measures to prevent the increase in tension in the wires.

The present invention is intended to achieve the above-mentioned problems,
It is an object of the present invention to provide an eccentric metal wheel that can prevent an increase in wire tension when a protector or the like passes through the wire.

Embodiments of the present invention will be described below with reference to FIGS. 3 to 6.

FIG. 3 is a front view of the eccentric metal wheel 10 according to the present invention;
FIG. 4 is a partially cutaway side view of the same. In the figure, 11 is a groove wheel, 12 is an eccentric sheave, 13 is a frame, and 14 is a clutch plate 40 which is a guide member.

The groove wheel 11 has a bearing 15 on an eccentric sheave 12.
It is rotatably supported through the eccentric sheave 12 and rotates around the center line 0-0 of the eccentric sheave 12. Reference numeral 11a is a winding portion for electric wires and the like.

The eccentric sheave 12 is rotatably supported by an eccentric shaft 16 fixed to a frame 13 via a bearing 17. A hook pin 18 is rotatably supported on the eccentric sheave 12, and a lever 20 having a roller 19 at its tip is integrally connected to the hook pin 18, and a gear 21 is fixed thereto. A clutch pin 22 is rotatably supported on the eccentric sheave 12, and a gear 23 that meshes with the gear 21 is fixed to the clutch pin 22. Details of how to support each of these pins 18, 22 are shown in the perspective view of FIG.

A bracket 24 for hanging a gold wheel is attached to the frame 13.
is attached, and the detection roller (detection member) 2
An arm 26 that rotatably supports 5 is rotatably supported. A link 42 is provided between the arm 26 and a clutch lever 27 rotatably supported by the frame 13.

The clutch plate 14 is attached to the side surface of the groove wheel 11, and a plurality of grooves 28 are formed at equal intervals in the circumferential direction on its inner periphery, as shown in FIG.

When the eccentric wheel 10 is in the state shown in FIG. 3, the lever 20 is biased clockwise in FIGS. 3 and 6 by a spring 29 (see FIG. 6) whose one end is fixed to the eccentric sheave 12. The roller 19 at the tip of the clutch lever 27 is locked by a bent portion (locking portion) 30 at the tip of the clutch lever 27 . In this state, if you try to rotate the eccentric wheel 10 clockwise in FIG. 3, the lever 20 will rotate counterclockwise in FIG. 3 because the roller 19 is locked by the bent portion 30. As a result, the clutch pin 22 attempts to rotate clockwise. However, clutch pin 2
The right side of the lever 38 that is integrally fixed to the sixth
As shown in the figure, the clutch pin 22 does not rotate because it is locked to the eccentric sheave 12. That is,
In the state shown in FIG. 3, the eccentric sheave 12 does not rotate clockwise. On the other hand, the portion of the clutch pin 22 facing the clutch plate 14 is formed with a semicircular portion 31 as shown in FIGS.
1 is in contact with the inner peripheral surface of the clutch plate 14 when the lever 20 is in the position shown in FIG. Therefore, in this state, the groove wheel 11 can rotate without being stopped by the eccentric sheave 12 (clutch-off). Further, the eccentric sheave 12 is provided with a stopper pin 34, and although not shown in detail, the stopper pin 34 is biased by a spring to move the eccentric sheave 12.
protrudes from the side of the This stopper pin 34
In the state shown in FIG. 3, the protruding portion is engaged with the right side of the frame 13 to prevent the eccentric sheave 12 from rotating in the counterclockwise direction. In this way, in the state shown in FIG. 3, the eccentric sheave 12 is stably held by the frame 13, only the groove wheel 11 is rotatable, and the center O of the groove wheel 11 is relative to the center P of the eccentric shaft 16. It is located slightly past the top dead center of eccentricity.

The stopper pin 34, the lever 38, and the portion of the eccentric sheave 12 that locks the right side of the lever 38 constitute means for stably holding the eccentric sheave 12.

The extension of electric wires and wire ropes is started in this state. In this case, the wire is extended while the groove wheel 11 rotates clockwise in FIG. 3.

When the wire feed progresses and a large-diameter obstacle such as a protector or joint is encountered, the arm 26 is rotated clockwise in FIG. 3 due to the engagement of this obstacle with the detection roller 25, and this movement causes the clutch to The lever 27 is driven via the link 42 and rotates counterclockwise in FIG. 3 to release the lock of the roller 19. Therefore,
The lever 20 is biased by a spring 29 and rotates clockwise from the solid line position to the chain line position in FIG. 6, and this movement causes the clutch pin 22 to shift into gear 2.
1 and 23 and rotates counterclockwise from the position shown by the solid line to the position shown by the chain line in FIG. In this state, the groove wheel 11 and the eccentric sheave 12 are integrated via the clutch plate 14 and the clutch pin 22. As a result, the rotation center of the groove wheel 11 moves from the center line O to the center line P of the eccentric shaft 16, and after this, the groove wheel 11 starts eccentric movement.
Therefore, the torque of the grooved sheave 11 increases, and this eccentric effect allows the grooved sheave 11 to move more easily and send out obstacles. In this case, by appropriately setting the amount of eccentricity (distance between O and P), it is possible to minimize the increase in wire tension.

Before the center O reaches the bottom dead center, the obstacle is groove wheel 1.
1, but the clutch-on state remains as it is, and the eccentric sheave 12 is rotated clockwise in FIG. 3 together with the groove wheel 11 due to the frictional force between the electric wire and the winding portion 11a. In this case, the stopper pin 34 provided on the eccentric sheave 12 engages with the frame 13, but a tapered surface is formed at the tip of the stopper pin 34, and this tapered surface engages with the frame 13 at the time of the engagement. The stopper pin 34 then retreats against the urging force of the spring, so that the stopper pin 34 can rotate to pass through the frame 13. Even after the center O reaches the bottom dead center, the concave groove 2 of the clutch plate 14
8 and the arcuate surface 32 of the clutch pin 22, the eccentric sheave 12 continues to rotate clockwise in FIG. 3. When the slope 37 and the arc surface 32 engage, a force is applied to rotate the clutch pin 22 clockwise in FIG.
As shown in FIGS. 5 and 6, a lever 38 is fixed to the lever 38, and a roller 39 is supported at the tip of the lever 38.
Since the clutch pin 22 is locked to a ring-shaped guide member 40 with an L-shaped cross section attached to the frame 13, the clutch pin 22 does not rotate and the center O continues to rotate toward the top dead center.

The guide member 40 is rotated by the reaction force applied to the clutch in the process of the clutch pin moving from the bottom dead center to the top dead center, and has the role of restraining the lever 38 to prevent the clutch from disengaging.

When the roller 19 comes to the original position shown in FIG. 3, the obstacle has passed the detection roller 25 and the clutch lever 27 has returned to the position shown in FIG. 27, and the lever 20 is rotated from the position indicated by the chain line in FIG. 6 to the position indicated by the solid line. At the same time, the lever 38, which is engaged through the gears 21 and 23, also returns from the position indicated by the chain line in FIG. 6 to the position indicated by the solid line. Note that the flange 41 of the guide member 40
Since the upper part of the lever 38 is cut out over a predetermined range, the restraint of the lever 38 is released, and therefore the lever 3
Return operation No. 8 is possible. In this state, the clutch is turned off and the groove sheave 11 and clutch plate 14 are separated from the eccentric sheave 12, and thereafter only the groove sheave 11 is transported together with the clutch plate 14 to continue the wire extension.

The above configuration will be explained in more detail as follows.

The relationship between the guide member 40, the lever 38, and other parts such as the sheave 12 will become clear from FIGS. 7 and 8. FIG. 7 shows an enlarged cross-section of main parts along section A in FIG. 3, in which 27 is a clutch lever, 20 is a lever, 30 is a bent part,
The relative positions of the clutch lever 27 and the lever 20 are as shown in the figure. FIG. 8 is a partially enlarged cross-sectional view taken along section B in FIG. 3, and shows the relative position of the lever 38 and the sheave 12.
In the figure, 23 is a gear when not engaged, 40 is a guide member, and 31 is a semicircular portion.

The above-mentioned effects will be understood based on these positional relationships.

As described above, according to the present invention, when an obstacle such as a protector comes during wire extension work, the groove wheel is integrated with the eccentric sheave and its rotation center is located from O to P, causing the eccentric This eccentric effect makes it easier for the groove wheel to move and send out obstacles, making it possible to prevent an increase in tension on electric wires, etc. when passing obstacles.

[Brief explanation of the drawing]

Figure 1 is an explanatory diagram of wire transmission work using a metal wheel, Figure 2
Figures 3 to 6 are explanatory diagrams showing wire tension fluctuations when passing obstacles when using a conventional metal wheel.
The figures show an embodiment of the eccentric metal wheel according to the present invention, FIG. 3 is a front view showing the overall outline, FIG. 4 is a partially cutaway side view of the same, and FIG. 5 is a part of the main part of the metal wheel. The cutaway perspective view and FIG. 6 are explanatory views of the same operation. 7 shows a partially enlarged sectional view taken along section A in FIG. 3, and FIG. 8 shows a partially enlarged sectional view taken along section B in FIG. In the figure, 10 is an eccentric metal wheel, 11 is a groove wheel, 12 is an eccentric sheave, 13 is a frame, 14 is a clutch plate, 16 is an eccentric shaft, 18 is a hook pin, 19, 39 are rollers, 20, 38 is a lever, 21 and 23 are gears, 2
2 is a clutch pin, 25 is a detection roller (detection member), 26 is an arm, 27 is a clutch lever, 2
8 is a concave groove, 29 is a spring, 30 is a bent part (locking part), 31 is a semicircular part, 32 is an arc surface, 33 is an inner peripheral surface, 34 is a stopper pin, 35 and 36 are arc surfaces, 37 is a 40 is a guide member, and 41 is a flange.

Claims (1)

[Claims] 1. An eccentric sheave that can eccentrically rotate around an eccentric shaft, a groove sheave that is supported by the eccentric sheave so as to be rotatable around the center of the eccentric sheave, and a wire that is fed through the groove sheave. a detection means for detecting a large diameter part in the middle of the line; a stable holding means for stably holding the eccentric sheave in a state where its center has passed the top dead center with respect to the center of the eccentric shaft; and the groove wheel. It is characterized by comprising a one-turn clutch mechanism provided between the eccentric sheave and activated when the detecting means detects the large diameter portion to rotate the eccentric sheave once together with the groove wheel. An eccentric metal wheel.