JPH02117594A - Winch - Google Patents

Abstract

PURPOSE:To prevent the damage of a sheave and a rope by a method wherein the diameter of a sheaves which generate a traction force is reduced from the load side toward the drum side. CONSTITUTION:A drum and a traction device 10 are rotated forward, and a rope 8 is hauled by means of sheaves 20, 21, 25, and 26 of the traction device 10 to wind the rope around a drum 1. In this case, the diameter of the sheaves 20, 21, 25, and 26 which generate a traction force is reduced from the load side toward the drum side. As a result, the slip of the rope 8 is prevented from occurring on the sheave in the vicinity of the load side, and the rope 8 is prevented from damage.

Description

[Detailed description of the invention] [Industrial application field 1 The present invention relates to a winch using a sheave.

[Prior Art 1] In general, a winch winds a rope onto a single drum to carry out both rope towing and rope storage. However, there are devices that use a capstan to pull the rope and wind the rope pulled by the capstan onto a drum. A rope alignment device is placed between the capstan and the drum to move the rope along the grooves of the drum and prevent it from winding up randomly. Such a winch was developed in Japanese Patent Application Laid-Open No. 57-131694.
JP-A-56-75397.

[Problem to be solved by the invention 1 When a capstan or sheave is used as a winch.

The traction force of the rope is determined by the angle of winding of the rope, and the larger the angle of zero winding, the greater the traction force.

When the winch is constructed using a sheave.

The angle of winding around one sheave is approximately 180 degrees, so 3
In order to increase the traction force, it is necessary to increase the number of sheaves. This increases the size of the device.

To prevent this, it is possible to place rubber on the contact surface of the sheave to increase the frictional force with the rope.

However, in this case, the life of the rubber was shortened.

The object of the present invention is to provide a winch with a long life.

[Means to solve the problem]

The present invention provides a first shaft having a required number of first sheaves for generating a traction force, and a second shaft having a required number of second sheaves, which are provided in parallel, and the first sheave, After the rope is sequentially passed through the second sheave, it is connected to the drum to form a winch, and when comparing the sheave on the side near the drum and the sheave on the far side in the rope path, The sheave is characterized in that the diameter of the sheave is smaller than the diameter of the sheave on the far side.

[Effect l The tension of the rope connected to the load decreases each time it passes a sheave that generates a traction force. In other words, the tension and elongation of the rope closer to the load is greater. For this reason, if the diameter of the sheave is the same, the slip between the sheave on the side closer to the load and the rope hooked thereon will be greater, causing premature damage to the rope and damage to the rubber placed on the sheave. I do things.

However, in the present invention, since the sheave diameter is set taking into consideration the elongation of the rope, slipping of the rope can be prevented and the service life can be extended.

At least one of the sheaves is provided so as to be drivable by a drive device, and after a rope is sequentially passed through the first sheave and the second sheave, the ropes are connected to the drum to form a sifting device.

[Embodiments of the Invention] The present invention will be described below with reference to an embodiment shown in the drawings. 1st
The figure is a longitudinal cross-sectional view of the sieving device, and the left half of the sheave 28, such as the right half of the rotation shaft 22 and the left half of the sheave 28, is not cut. FIG. 2 shows only the left half of the rotating shaft 22 in cross section. FIG. 3 is a cross-sectional view of the sheave 28,
Only the right half of the sheave 28 is shown.

In FIG. 5, 1 is a drum capable of multi-layer winding;
It is driven by a constant torque type motor 21, for example, a star type hydraulic motor. A brake 3 is installed at the narrow end of the drum l. The speed reducer is not shown in Figure 1 because a planetary speed reducer is installed inside the drum 1. Reference numeral 5 denotes a rope alignment device, which has a known configuration. Reference numeral 10 designates a rope separating device of the present invention, which includes a constant speed rotating motor 11. For example, it is driven by a hydraulic motor. 12 is a planetary reduction gear;
A brake (not shown) is provided. The rope 8 enters the separating device 10 from the left side of the separating device 10 and exits from the aligning device 5 (J!I+, passing through the aligning device 5 and being wound onto the drum 1.

The configuration of the separation device 10 will be explained with reference to FIGS. 1 to 4.

In FIG. 1, a rotating shaft 22 with two sheaves 20 and 21 on the left is vertically provided, and two sheaves 25 are on the right.
．． A rotating shaft 27 having a diameter 26 is provided vertically. One sheave 28 is provided between the two. Separation device 10
Rope 8 entered from the left side of sheave 20. Sheave 25.
Sheave 21° Sheave 26. It passes sequentially through the sieve 28 and reaches the alignment device 5. Sheaves 25 and 26 are respectively Sheaves 20
．． The six sheaves 28, which are installed slightly above the sheaves 21, are installed slightly above the sheaves 26. A gear 30 is provided at the upper part of each of the rotating shafts 22 and 27, and meshes with a pinion 32 at the lower end of the output shaft 31 of the reduction gear 12. The sheave 28 is rotatably attached to the lower end of the output shaft 31.

Support Structure for Rotating Shafts 22 and 27 1 A structure for attaching gears and sheaves to the rotating shaft will be explained with reference to FIG. Since these are substantially the same for the rotating shaft 22 and the rotating shaft 27,
The rotating shaft 22 will be explained.

The rotating shaft 22 is supported by a bearing 35 on a base 34 and a bearing 38 on an upper cover 37. Bearings 35 and 38 are sleeves.

The rotating shaft 22 has two flanges 22 between the bearings 35 and 38.
a, 22b, each having a flange 40.41.
are welded. Attach the gear 30 to the flange 41 with the bolt 4
It is fixed at 2.

A cylinder 43 is coaxially welded between the two flanges 40 and 41. A flange 44 is provided at the upper end of the cylinder 43.
Bolt holes are provided on the circumference.

A spline 43a is provided on the outer periphery of the lower part of the cylinder 43. The sheaves 20, 21, 25, and 26 are provided with splines that match this spline 43a to obtain nine rotational forces. 44 is a flange for fixing the sheave, 0 cylinder 4
6 Sheep 20.21.25.26 welded to 3 has a wear-resistant material with a high friction coefficient (for example,
High manganese steel. Hereinafter, it will be referred to as lining. )4
5 is set. The contact surface of the lining 45 with the lobe 8 is concave. The lining 45 is ring-shaped and is held by sheave frames 46, 47, 48. The lining 45 and the sheave frames 46 to 48 have a lining 45 attached to the rubber holding part.
A step 45a is provided to prevent movement in the radial direction.

The sheave frames 46 to 48 are provided so as to cover the upper and lower surfaces and the circumferential surface of the lining 45. The inner surfaces of the sheave frames 46 to 48 are provided with splines that match the splines 43a. Further, bolt holes are provided in the lining 45 and the sheave frames 46 to 48.

To explain how to assemble the sheave, 1. For example, pass the bolt 50 through the bolt hole of the flange 44, and insert the spacer 51. Sheave frame 48. Lining 45. Sheave frame 47. Lining 45. Sheave frame 47. The liner 52 is sequentially passed through and the nut 53 is tightened.

A partition plate 60 is installed at the height of the flange 44 to separate the gear 30, 32 chamber and the sheave chamber from the traction device 10.
It is removably attached to a ring-shaped seat 62 of a side cover 61 with bolts 63. The partition plate 60 has a flange 44
An oil seal 65 is provided in contact with the end of the cylinder.

The difference between the rotating shaft 22 and the rotating shaft 27 is that the flange 22a of the rotating shaft 22 is located slightly higher than that of the rotating shaft 27, and the length of the spacer 50 and bolt 51 is slightly larger on the rotating shaft 22 side. short.

Rotation axes 22 and 27 are parallel.

Note that the diameters of the rubber 45 of the sheaves 20, 21, 25, and 26 are slightly different. This will be discussed later.

As shown in FIG. 3, the sheave 28 is attached to the output shaft 31 below the partition plate 60. The sheave 28 is rotatable relative to the output shaft 31 by a bearing 70. 71 is an oil seal.

In FIG. 1, the base 34 below the sheave 28 is provided with an opening for attaching and detaching the sheave 28. 75 is a mounting seat, and 76 is a reinforcing member.

In FIG. 4, reference numeral 80 is a passage port for the rope 8 on the load side, and guide rollers are provided on the left and right sides thereof, but not shown, and 81 is a passage port for the rope 8 to the rope alignment device 5. . In addition, the side cover 6 of the sheaves 20 to 28
1 is provided with appropriate openings for hanging ropes 8 over sheaves 20-28.

To explain the entire assembly, first, the sheaves 20, 21, 25, 26 are attached to the 1-rotation shaft 22, 27, and then the bearing 35
．． 35 from above. Next, the partition plate 60 is inserted from above and fixed to the seat 62. Seal to prevent oil (e.g. grease) from leaking. Next, the gear 30 is attached to the flange 41.
Fix each. Next, attach the upper cover 37 and fix it with bolts 83. Next, attach the pinion 32 to the output shaft 31.
Insert the reducer 12 with attached from above and remove the upper cover 37.
Fixed to. Next, the sheave 28 is inserted through the lower opening 34a, and the flange 85. Attach to the output shaft 31 with bolts 86. The upper cover 37 is fixed to the side cover 61 with bolts 78.

The reason why the grooves of the sheaves 20.21, 25.26.28 are wide is that they allow the joints connecting the ropes to pass through.

In FIG. 5, reference numeral 89 is a rotational speed meter that measures the number of rotations of the rotating shaft 27, and measures the length of the rope 8.

A load cell 90 is installed between the shaft 22 and its bearing, and measures the tension of the rope 8. The load cell 90 is connected to the sheave 2 through which the rope 8 is drawn into the traction device 10 from the outside.
It is provided on the shaft 22 side on the 0.21 side. The upper end of the shaft 22 is movable around a bearing 35. A concave guide 92 is provided on the upper cover 38, and the inner wall of this guide and a boss 93
A load cell 90 is provided between the two. The boss 93 moves along the inner wall of the guide 92.

In such a configuration, rotating the pinion 32 causes the gear 30.30 to rotate in the same direction, causing the sheaves 20.21,
25 and 26 rotate in the same direction. The sheave 28 rotates relative to the output shaft 31.

To wind up the rope 8, the motor 2.11 is rotated in the normal direction, and the drum 1 and the traction device IO are rotated in the normal direction.

The rope 8 is pulled by the sheaves 20 to 26 of the traction device 10 and wound around the drum 1. The pulling force on the rope 8 by the drum l is smaller than that by the traction device lO. Since the drive motor 2 for the drum 1 is of a constant torque type, the drum 1 is rotated at a low speed when the substantial diameter of the drum increases by winding the rope 8. Therefore, the rope can be wound in multiple layers.

To pay out the rope 8, the motor 1.11 is reversed and the drum 1.1. Reverse the traction device 10.

The force of the load coupled to the rope 8 causes the rope to be paid out.

In this case, since the lining 45 is provided on the contact surface of the rope 8 in the sheave, the coefficient of friction can be increased.
The number of stages of the driving sheaves 20 to 26 can be reduced, and the lining 45 may be embedded in recesses provided at predetermined intervals on the circumference of the sheave.

Now, the diameter of the sheave 20, 21, 25, 26 (that is, the diameter of the rubber 45 which is the surface in contact with the rope 8) is determined as follows.

Here, the diameters of the sheaves 20, 21, 25, and 26 are respectively Da, Di, and D4. The tension of the rope 8 between the sheave 20 and the load is T1, and the sheave 20 and the sheave 25
The tension of the rope 8 between the sheave 25 and the sheave 21 is T2, the tension of the rope 8 between the sheave 25 and the sheave 21 is T, and the tension of the rope 8 between the sheave 25 and the sheave 21 is T2.
Let T4 be the bow length force of the rope 8 between the sheave 26 and the sheave 26, and T be the tension of the rope 8 between the sheave 26 and the sheave 28.

As a representative example, the relationship between the rope tension T and T2 is as follows.

T1=T2e, na −−−−−−−−−−−−−−
----- (1) where μ: coefficient of friction θ: angle of winding of the rope around the sheave. Therefore, the relationship between the tensions of each rope is as follows.

TI>T2>T3>T,>TS --------(2)
The elongation δ of the unit length of the rope 8 due to the load T is as follows.

δ=ε・T −−−−−−−−−−−−−−−−−−−
----(3) Here, ε is the elongation of the rope 8 in unit length due to unit load.

Rope 8 (TI) hung on sheave 20 as a representative.

The difference in elongation of T2) is as follows.

Δδ=ε(T, -T2) Therefore, the radius of the sheave 20.25, D2, in order to prevent slippage between the sheave 20.25 and the rope 8 hooked thereon, has the following relationship.

D2=″″°−△' −−−−−−−−−−−−−−−
-(4)π The diameters (D,,D,) of other seas 121.26 are calculated in the same way.

As mentioned above, considering the elongation of the rope, the sheave 20.2
Since the diameter is set at 1.25.26, slippage of the rope 8 is eliminated and damage to the rubber 45 can be reduced.

[Effect of the invention 1 As described above (according to the present invention, the flow from the load side to the drum side (
Accordingly, the diameter of the sheave that generates the traction force is reduced, so damage to the sheave and rope can be prevented.

[Brief explanation of drawings]

Fig. 1 is a longitudinal sectional view of a towing device according to an embodiment of the present invention, Fig. 2 is an enlarged sectional view of section A in Fig. 1, and Fig. 3 is an enlarged sectional view of section A in Fig. 1.
FIG. 4 is a horizontal plan view of the sheave portion of FIG. 1, and FIG. 5 is a plan view of a winch according to an embodiment of the present invention. 1 ------- Drum, 2 ---- Constant torque type motor, 5 - - One rope alignment device, 8 - One - Rope, 1o ---- One traction device. , 1
1------Motor, 12---One reduction gear,
20.21.25.26.28-Sieve, 22.27
--------Rotating shaft, 30-------gear. 31----- Output shaft of one speed reducer, 32--------
Binion, 60-----One partition plate, 65.71-
---One oil sea Jζ 〃 Spear 3 figure Sai 4 figure

Claims (1)

[Claims] 1. A drum capable of winding a rope, a first drive device capable of changing the rotational speed of the drum, a first shaft equipped with a required number of first sheaves, and a required number of first sheaves. a second sheave, a required number of second sheaves located at different positions in the axial direction of the first sheave, and a second shaft provided parallel to the first axis; a second axis that rotates at least one of the first axis and the second axis;
a drive device, and a rope that is passed sequentially between the first sheave and the second sheave and then fixed to the drum, and the diameter of each of the first sheave and the second sheave is equal to the diameter of the rope. Comparing the sheave on the side closer to the drum and the sheave on the side farther from the drum in the path, the former is smaller.