JPH02276B2 - - Google Patents

Description

[Detailed description of the invention] Industrial applications The present invention relates to a winch device.

Conventional structure and its problems In general, in winch equipment, when winding wire rope around the winch drum, if the fleet angle exceeds ±2°, or at most ±3°, the wire rope will be wound in an orderly manner or in multiple layers. This becomes difficult. Therefore, in the conventional winch device, as shown in FIG. 5, a feed screw 2 is rotated in synchronization with the winch drum 1, and a guide sheave 5 that guides the wire rope 4 to a feed base 3 that is screwed onto the feed screw 2 is used. By providing this, the wire rope 4 can be accurately and orderly wound in multiple layers and let out. However, in such a conventional configuration, the wire rope 4
When the feed screw 2 reaches the end of the winch drum 1, the feed screw 2 must be reversed in the direction of movement of the feed base 3, and there is a problem in that the reversing mechanism for this purpose becomes large-scale.

OBJECT OF THE INVENTION Therefore, an object of the present invention is to enable a wire rope to be wound evenly with a simple structure that does not require a reversing mechanism or the like.

Structure of the Invention In order to achieve the above object, the present invention provides a winch drum that rotates half a revolution when the winch drum rotates by the amount necessary to wind the wire rope from one end to the other end in the axial direction. a rotating arm linked to the rotating arm; a roller configured to be movable in the rotating radial direction with respect to the rotating arm; and a roller that engages with the roller and detects a velocity component of the roller in the drum axis direction based on the rotating of the rotating arm. a constant velocity cam groove that makes the winch drum constant; a fork that engages with the roller and moves reciprocally in the direction of the drum axis; a fork that moves back and forth in the drum axis direction in conjunction with the fork; A wire guide that engages with the wire rope in the vicinity and guides the wire rope.

Therefore, the wire guide is reciprocated in the direction of the drum axis in synchronization with the rotation of the winch drum due to the action of the swing arm and constant velocity cam groove.
The wire rope can be wound accurately, and the constant-velocity cam groove allows the wire guide to reciprocate by simply rotating the swing arm in one direction, making it possible to reciprocate the wire guide without using a conventional reversing mechanism. This makes it possible to make the apparatus smaller and simpler.

DESCRIPTION OF THE EMBODIMENTS FIG. 1 shows an embodiment of the present invention, in which reference numeral 11 is a winch drum supported by a pair of brackets 12, and is capable of winding up and letting out a wire rope 13. 14 is a hydraulic motor for driving the winch drum 11;
4, an idling gear 16 that meshes with the gear 15, another idling gear 17 that rotates integrally with the idling gear 16, and a gear 18 that meshes with the idling gear 17. The structure is such that power is transmitted to a winch drum 11 to which a winch drum 11 is fixed. Further, the hydraulic motor 14 can be rotated in both forward and reverse directions, thereby winding and letting out the wire rope 13.

Another gear 19 is meshed with the free rotating gear 16, and a worm 21 is fixed to a shaft 20 to which the gear 19 is fixed and extends between both brackets 12. Reference numeral 22 denotes a worm wheel that meshes with the worm 21. The worm wheel 22 is fixed to a shaft 23 by a bearing bracket 60, and as the worm wheel 22 rotates, the worm wheel 22 is rotated in a plane parallel to the axial direction of the winch drum 11. A pivot arm 24 is attached which pivots. Therefore, the hydraulic motor 14 is connected to the winch drum 11 and the swing arm 24.
The idling gears 16,
Winch drum 11 by 17 and worm 21 etc.
An interlocking device 25 between the rotary arm 24 and the rotating arm 24 is constructed.

The interlocking device 25 rotates the swing arm 24 from one drum axial position when the winch drum 11 rotates by the amount necessary to wind the wire rope 13 from one end to the other end in the axial direction. The interlocking mechanism is configured to rotate half a rotation to the other drum axis direction position. That is, when the width of the winch drum 11 in the axial direction is W and the wire diameter of the wire rope 13 is d, the required rotational speed N of the winch drum 11 to finish winding the wire rope 13 over the entire width W of the winch drum 11 is becomes N=W/d. Since it is sufficient for the swing arm 24 to rotate 1/2 while the winch drum 11 rotates N, the total reduction ratio n in the interlocking device 25 is n=d/2W. Therefore, the number of teeth of the gear 18 on the winch drum 11 side is Z ₁ , and the number of teeth of the gear 19 on the shaft 20 side is Z 1 .
When Z ₂ is assumed, the worm reduction ratio N _w is n _w = d/2W×Z ₁ /Z ₂ .

The rotating arm 24 is fitted with a sleeve 26 in a state in which rotation is inhibited and only slidable, for example by key fitting, and a roller 27 is fitted onto the sleeve 26.
is installed. Reference numeral 28 denotes a constant velocity cam groove that engages with the roller 27, and is provided along a bottom plate 29 extending between both brackets 12. The shape of the constant velocity cam groove 28 is determined so that the speed component of the drum axis direction of the roller 27 based on the rotation of the rotation arm 24 is constant. That is, for example, as shown in FIG.
The shape of the constant velocity cam groove 28 can be determined by drawing assuming that when the roller 27 rotates around the shaft 23 at a constant angular velocity due to the rotation of 4, the roller 27 moves at a constant velocity in the drum axis direction X. It is. 30 is an auxiliary line indicating constant angular velocity displacement, and 31 is an auxiliary line indicating uniform velocity displacement.

As shown in FIG. 1, a fork 32 is engaged with the roller 27. This fork 32 is provided between sleeves 34 that are slidably fitted onto a pair of guide bars 33 that extend between the brackets 12 in the direction of the drum axis. By moving along 28, it is possible to reciprocate in the direction of the drum axis. One sleeve 34 has a stand 35
is fixed, and a wire guide 36 that engages with the wire rope 13 is attached to the stand 35 at a position opposite to the winch drum 11. This wire guide 36 is composed of a pair of traversal rollers 37 that sandwich the wire rope 13 therebetween.

In such a configuration, when the hydraulic motor 14 is rotated, the winch drum 11 is thereby rotated and the wire rope 13 is wound up. At this time, the swing arm 2 is linked to the winch drum 11.
4 rotates, the roller 27 is guided by the constant velocity cam groove 28, and the speed component in the direction of the drum axis becomes constant, so the fork 32 that engages with this roller 27
The wire guide 36 is reciprocated at a constant speed in the direction of the drum axis, and as a result, the wire rope 13 is wound around the winch drum 11 one by one. As a result, the wire rope 13 is prevented from winding randomly or in a rounded manner, and winch troubles are prevented.
Moreover, by winding the wire rope 13 in a compact manner, the space required around the winch drum 11 can be reduced. Moreover, it is also possible to reduce fluctuations in the winding torque. In addition, in the above, "uniform speed" means winch drum 1
The wire guide 36 is rotated at an equal pitch in synchronization with the rotation of step 1.
This means that a large load is applied to the wire rope 13 and the winch drum 11
When the rotation speed of the wire guide 36 decreases, the feed speed of the wire guide 36 naturally changes accordingly.

3 to 4 show other embodiments of the present invention,
In this example, the wire guide 36 is moved by a swing arm 38 instead of the stand 35 in FIG. That is, the swing arm 38 is attached to a bracket 40 erected on the frame 39 of the device.
The center portion of the drum is supported by the drum, and is capable of swinging in a plane parallel to the axial direction of the drum. 41 is a support shaft. Further, like the sleeve 34, the wire guide 36 is also slidable along a guide bar 42 in the direction of the drum axis. 43 is a sleeve fitted onto the guide bar 42; 44 is a traverser roller 3;
7 is a support plate fixed to the sleeve 34. In this example, the wire rope 13 runs in a direction different from that shown in FIG. 1. A roller 46 sandwiched between a pair of guide members 45 fixed to the sleeve 34 is provided at one end of the swing arm 38, and a roller 46 is provided at the other end.
Another roller 48 is provided which is sandwiched between a guide member 47 fixed to the sleeve 43 and an end surface of the support plate 44, and the linear movement of the sleeve 34 is transferred to the wire guide 36 through the swinging movement of the swinging arm 38. It is said that it can be converted to linear motion without play.

According to this configuration, the wire guide 36 is moved along the guide bar 42, and the swing arm 38 is supported by the bracket 40, so that the cantilevered stand 35 and wire guide shown in FIG. 36, it is possible to improve the rigidity, that is, the stability, and the slideability of the guide bar 42 and the sleeve 43.

As shown in FIG. 4, the shaft 23 to which the worm wheel 22 is fixed is supported by a bearing 50 within a housing 49 provided within the apparatus. Further, the constant velocity cam groove 28 has the following configuration. That is, as shown in FIGS. 4 and 2, a support member 53 having an outer cylindrical projection 51 and an inner cylindrical projection 52 is fixed on the bottom plate 29. A constant velocity cam groove 28 is formed by an inner edge 55 of the outer plate 54 which is fitted and fixed, and an outer edge 57 of the inner plate 56 which is fitted and fixed to the cylindrical projection 52. Furthermore, in FIGS. 2 and 4, the fork 32 has a hole 59 in the center of the plate 58 in which the roller 27 engages, instead of the pair of rod-shaped bodies shown in FIG. By using the formed material, we aim to improve the rigidity.

Effects of the Invention As described above, according to the present invention, the wire guide is reciprocated in the direction of the drum axis in synchronization with the rotation of the winch drum due to the action of the swivel arm, constant velocity cam groove, etc. Accurate winding is possible, and the constant-velocity cam groove allows the wire guide to reciprocate by simply rotating the swing arm in one direction.
It is possible to eliminate the need for a conventional reversing mechanism, etc., and the device can be made smaller and simpler.

[Brief explanation of drawings]

Fig. 1 is a perspective view of one embodiment of the present invention, Fig. 2 is a diagram showing a constant velocity cam groove, Fig. 3 is a front view of another embodiment of the invention, and Fig. 4 is the left side of Fig. 3. cross-sectional view of the surface,
FIG. 5 is a plan view of a conventional example. 11...Winch drum, 13...Wire rope,
24... Swivel arm, 25... Interlocking device, 27... Roller, 28... Constant velocity cam groove, 32... Fork, 33...
Guide bar, 34... Sleeve, 36... Wire guide, 37... Traverser roller, 38... Swing arm.

Claims (1)

[Scope of Claims] 1. A swing arm that is interlocked with the winch drum so as to rotate half a revolution when the winch drum rotates by the amount necessary to neatly wind the wire rope from one end to the other end in the axial direction of the winch drum. a roller configured to be movable in the radial direction of rotation with respect to the rotation arm; and a constant velocity that engages with the roller and makes the velocity component of the roller in the direction of the drum axis constant based on the rotation of the rotation arm. a cam groove; a fork that is engaged with the roller and reciprocated in the drum axis direction; A winch device comprising: a wire guide that engages with the wire guide and guides the wire rope.