JPH07267587A - Winch - Google Patents

Abstract

PURPOSE:To shorten the non-load takeup time of a wire. CONSTITUTION:A winch 1 is constituted so that its drum 5 is rotated by a motor 3 through reduction gears 9, 11. The reduction gear 9 comprises a sun gear 51 on the input side, pinion 53 on the output side meshing with the sun gear, engagement part 65 on the easing 27 side, engagement part 67 of a pinion carrier 57, an internal gear 61, and an operating member 47. The internal gear 61 can take three positions; i.e., the load takeup position 77 meshing both with the pinion 53 and the engagement part 65, the free position to mesh only with the pinion 53, and the non-load takeup position 81 to mesh with the pinion 53 and engagement part 67. The operating member 47 shifts the internal gear 61 to these three positions.

Description

Detailed Description of the Invention

[0001]

FIELD OF THE INVENTION This invention relates to winches.

[0002]

2. Description of the Related Art A winch 20 as shown in FIG. 6 is disclosed in JP-A-59-86595 and JP-A-60-232395.
1 is described. This is the drum 20 via a motor 203, a brake clutch 205, and a speed reducer 207.
9 is driven to rotate. Speed reducer 20
7 is a three-stage planetary gear mechanism 21 arranged in series
1, 213, 215. When the internal gear 217 of the planetary gear mechanism 213, 215 is moved to the free position in the direction of the arrow 221 by the operation lever 219, the meshing portion between the internal gear 217 and the casing 223 is formed. The meshing at 225 is released, the drum 209 is allowed to rotate freely, and the wire 227 can be lowered.

[0003]

However, since the wire 227 is wound on the drum 209 after the load hoisting work is completed, the wire 227 is decelerated in the same three stages as the load hoisting work. It takes a long time to wind up without load.

[0004] Therefore, an object of the present invention is to provide a winch capable of shortening the unloaded winding time of the wire.

[0005]

The winch of the first invention comprises:
A motor, a drum around which a wire is wound, and first and second reduction gears that are arranged in series to transmit the rotational force of the motor to the drum are provided. The first reduction gear is a sun gear to which the driving force of the motor is input. An output side pinion gear meshing with the sun gear, and a first meshing portion provided on the casing side,
A second meshing portion provided on the pinion carrier, a load winding position that meshes with the pinion gear and the first meshing portion, a free position that meshes only with the pinion gear, and a meshing portion with the pinion gear and the second meshing portion. It is provided with an internal gear that is movable to a matching unloaded winding position, and an operating member that moves and operates the internal gear to each of the above positions through a convex portion that engages with a circumferential groove of the internal gear. Is characterized by.

In the winch of the second invention, the free position is provided between the load winding position and the no-load winding position along the moving direction of the internal gear during the switching operation.
It is the described winch.

In the winch according to the third aspect of the present invention, the internal gear is moved along with the rotating operation of the operating member.
Or the winch described in 2.

A winch according to a fourth aspect of the present invention is the winch according to claim 1 or 2, wherein the internal gear is moved along with the sliding operation of the operating member.

A winch according to a fifth aspect of the present invention is a winch according to claim 1, 2 or 3 or 4, which comprises a plurality of stages of planetary gear mechanisms in which the second reduction gears are arranged in series.

[0010]

Operation: The deceleration of the motor is performed by the first and second reduction gears,
Since the pinion gear is fixed to the pinion carrier in the first speed reducer to provide the no-load winding position that reduces the number of reduction stages by one, the no-load winding operation of the wire can be performed quickly. (First to fifth inventions) Since a free position is provided between the load winding position and the no-load winding position, switching to any winding position is performed once via the free position.
It is possible to prevent the danger of the operator and the damage of the motor due to the erroneous operation. (2nd to 5th inventions)

[0011]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT An embodiment of the fifth invention will be described with reference to FIGS. The left and right directions are the left and right directions in FIG.

As shown in FIG. 1, the winch 1 of the embodiment has a motor 3, a drum 5, a brake clutch 7, a first and a second.
Speed reducers 9 and 11.

The drum 5 is rotatably supported on the left and right side walls 13 and 15 through bearings 17 and 17, and each side wall 1
The stays 3 and 15 are integrated with the stay 19 and the bolts 21 and 21. A wire 23 is wound around the drum 5. Each casing 2 of the motor 3 and the speed reducers 9 and 11
Reference numerals 5 and 27 are fixed to the side walls 13 and 15, respectively.

The output shaft 29 of the motor 3 is connected to the input shaft 37 of the speed reducer 9 through the joint 33, the connecting shaft 35, and the brake clutch 7 inside the cylindrical portion 31 of the drum 5, and thus the input The shaft 37 is rotationally driven by the motor 3. The left end side of the input shaft 37 is supported by the hub portion 41 of the drum 5 via the bearing 39, and the right end side thereof is the bearing 4
It is supported by the casing 27 via 3.

The speed reducer 9 is a planetary gear type speed reducer 45, an operating lever 47 (operating member), and a check mechanism 4.
9 and 9. The sun gear 51 of the reduction mechanism 45 is formed integrally with the input shaft 37, and the pinion gear 53 is provided with the left and right pinion carriers 57, 5 via the pinion shaft 55.
9 is supported. Further, the sleeve 63 having the internal gear 61 formed therein is arranged so as to be axially movable and rotatable. The casing 27 and the left pinion carrier 57 are provided with splines 65 and 67 (first and second meshing portions) that can be engaged with and disengaged from the internal gear 61, respectively.

The operating lever 47 includes a disk-shaped base portion 69 rotatably attached to the casing 27, a lever 71 which is angled with respect to the center axis of rotation of the base portion 69 as shown in FIG. 2, and a base portion. It is formed by the convex portion 73 formed on the reference numeral 69. The recess 73 is shown in FIG. 3 (A-A sectional view of FIG. 1).
As described above, it is slidably engaged with the peripheral groove 75 provided on the outer periphery of the sleeve 63, and the convex portion 73 rotates as shown in FIG. 3 by the rotation operation of the operation lever 47 as shown in FIG. Accordingly, the sleeve 63 (internal gear) has a load take-up position 77 that meshes with the pinion gear 53 and the spline 65 of the casing 27, a free position 79 that meshes only with the pinion gear 53, and a spline of the pinion gear 53 and the pinion carrier 57. 67 to the unloaded winding position 81 that meshes with 67. The check mechanism 49 acts on the base portion 69 of the operating lever 47 at each position 77, 79, 81.

The speed reducer 11 is composed of planetary gear type speed reducers 83 and 85. These are composed of hollow sun gears 87 and 89, pinion gears 91 and 93, a common internal gear 95, and the like. The sun gears 87, 89 are supported on the outer periphery of the input shaft 37, and the sun gear 8
The above-mentioned pinion carrier 57 is engaged with 7. Further, the pinion gear 93 is supported by the left and right pinion carriers 105 and 107 via the pinion shaft 103,
The left pinion carrier 105 is spline-connected to the hub portion 41 of the drum 5. The internal gear 95 is formed on the casing 27.

When the sleeve 63 of the reduction gear transmission 9 moves to the load winding position 77, the internal gear 61 is locked to the casing 27. Therefore, the driving force of the motor 3 for rotating the sun gear 51 is reduced by the reduction mechanism 45 (first stage), transmitted to the reduction mechanism 83 via the pinion carrier 57 to be reduced (two stages), and reduced via the pinion carrier 99. It is transmitted to the mechanism 85, decelerated (three stages) and transmitted from the pinion carrier 105 to the drum 5, and the drum 5 is rotated with a large torque to wind the wire 23 under load.

When the sleeve 63 moves to the free position 79, the internal gear 6 receives the driving resistance on the motor 3 side.
1 idles, the drum 5 is in a free rotation state, and the wire 23 can be paid out.

When the sleeve 63 moves to the unloaded winding position 81, the pinion gear 53 and the pinion carrier 57 are locked, so that the rotation of the motor 5 bypasses the speed reducer 9 in the first stage and is input to the speed reducer 11. Therefore, the unloaded wire 23 can be wound up as quickly as that.

Further, in this way, the free position 79 is arranged between the load winding position 77 and the unloaded winding position 81,
Since switching to any of the winding positions is performed via the free position 79, it is safe for the worker, and, for example, the wire 23 is erroneously unloaded while the wire 23 is loaded. By doing so, an accident that damages the motor 3 with an excessive load can be avoided.

Although the operation of the brake clutch 7 (see FIG. 1) arranged in the drum 5 has not been mentioned in the above description of the operation at each position of the sleeve 63, the operation of the brake clutch 7 at this time is described. The operation will be described with reference to FIGS.

FIG. 4 is an enlarged cross-sectional view of the brake clutch 7, and FIG. 5 is an exploded view showing a part of the brake clutch. The brake clutch 7 is arranged in the middle of the connecting shaft 35 on the side of the motor 3 and the input shaft 37 on the side of the speed reducer 9, and the hexagonal holes provided in the shaft center are fitted and connected to the shafts 35, 37, respectively. ing. The driving force from the motor 3 is input to the cam 111 via the connecting shaft 35, and then is output to the input shaft 37 on the speed reducer 9 side from the cam 113 arranged opposite to this. That is, the opposite ends of the cams 111 and 113 are formed in a saw-tooth shape (see FIG. 5) that is biased by the coil springs 115 and 115 and meshes with each other. When the load is dropped due to, the sawtooth inclined surfaces 111a and 113a press each other. Further, when the motor 23 feeds the wire 23, the saw-tooth flat portions 111b and 113b press each other. Furthermore, the male taper surface 1 is provided on the other end side of both cams 111 and 113.
11c and 113c are formed.

On the other hand, as shown in FIG. 4, a ring-shaped block 11 is provided on the inner circumference of the drum 5 with a predetermined axial interval.
7, 117 are fixed, and cones 121, 121 are arranged on the inner circumferences of the blocks 117, 117 via one-way clutches 119, 119, respectively. And cone 1
The cam holes 11c and 121c of the cams 21 and 121
1, 113 are opposed to each other so as to fit with the male tapered surfaces 111c and 113c, and the cones 121 and 121 and the cams 111 and 11 are opposed to each other.
The coil springs 115, 115 between 3 urge the two in a direction to separate them from their fitting. Also cone 1
Thrust bearings 123, 123 are arranged between the blocks 21, 121 and the blocks 117, 117.

With the construction of the brake clutch 7 as described above, when the sleeve 63 of the reduction gear transmission 9 moves to the load winding position 77 and the winch 1 winds the load, the cams 111, 113 are driven by the driving force of the motor 3. Inclined surface 111a,
113a press each other. Although the cams 111 and 113 tend to be separated from each other by the axial thrust force generated by this, the male taper surfaces 111c and 113c are separated from each other by the cone 12.
Since it closely fits in the tapered hole 121c of No. 1, the axial movement stops and the rotational force is transmitted from the cam 111 to the cam 113. In this way, the driving force of the motor 3 is transmitted to the input shaft 37 of the reduction gear transmission 9 via the brake clutch 7, and the load is wound up. At this time, the cams 111 and 113 and the cone 121 rotate integrally, but the one-way clutch 119 is arranged so as to be in a free rotation state at this time. Therefore, the brake clutch 7 and the block 117 (drum) in this part are arranged. There is no direct connection with 5) and load winding takes place as described above.

Further, when the sleeve 63 of the reduction gear transmission 9 moves to the unloaded winding position 81 and the winch 1 carries out unloaded winding, the state where the brake clutch 7 and the drum 5 are not directly connected is as described above. Since it is the same as the case of the load winding, the non-load winding is performed as described above.

On the other hand, when the load is about to drop due to its own weight or the like, the drum 5 is rotated by the load in the direction opposite to that at the time of winding, and the rotational force thereof is in the route opposite to that at the time of winding.
1, 9 is transmitted to the input shaft 37, and the cam 11
An attempt is made to rotate the motor 3, which is stopped via the inclined surfaces 113a and 111a of the motors 1 and 113, in the direction opposite to that at the time of winding.
However, at this time, an axial thrust force acts between the cams 111 and 113, and the taper surfaces 111c and 11c closely fitted to each other are fitted.
At 3c, the cams 111 and 113 and the cone 121 rotate together, and the one-way clutch 119 is locked. In this way, when the drum 5 and the brake clutch 7 are directly connected, two paths, that is, a reverse path that follows the speed reducers 11 and 9 occur simultaneously, so that the drum 5 cannot rotate and the brake is activated. In this way, the load is prevented from falling.

When the wire 23 is paid out by the motor 3, the driving force of the motor 3 which rotates in the direction opposite to the winding direction is the plane portion 111b, between the cams 111, 113.
It is transmitted by pressing between 113b and further transmitted to the input shaft 37 of the reduction gear transmission 9. Thus, the cam 111,
The axial thrust force does not act on 113, so the cam 11
1, 113 and cone 121 are coil springs 115
Since the brake clutch 7 is not directly connected to the drum 5, the wire 23 is fed out.

The sleeve 63 of the speed reducer 9 is in the free position 7
When the wire 23 is moved to 9, and the wire 23 is pulled out by hand, since the one-way clutch 119 is in a free rotation state, there is no direct connection between the brake clutch 7 and the drum 5 in this portion, and the pulling out by hand is as described above. Done.

The second reduction gear 11 may be a reduction gear mechanism other than the planetary gear mechanism or a reduction gear mechanism using no gear. Further, the first reduction gear transmission 9 may be arranged at the subsequent stage of the second reduction gear transmission 11. In addition, the operating lever 4
7 may be configured to be automatically operated by a motor or hydraulic pressure.

[0031]

According to the winch of the present invention, since the first speed reducer is provided with the unloaded winding position for reducing the number of deceleration stages, the wire winding time under no load can be shortened. Further, in the configuration in which the load take-up position and the non-load take-up position are switched via the free position, it is possible to avoid the danger of the worker and the damage to the motor.

[Brief description of drawings]

FIG. 1 is a sectional view showing an embodiment of a fifth invention.

FIG. 2 is a view showing positions of operation levers in the embodiment of FIG.

3 is a cross-sectional view taken along the line AA of FIG.

FIG. 4 is an enlarged cross-sectional view of a brake clutch unit of the embodiment of FIG.

5 is a diagram showing a part of the brake clutch of the embodiment of FIG. 1 in an exploded arrangement.

FIG. 6 is a sectional view of a conventional example.

[Explanation of symbols]

 1 winch 3 motor 5 drum 7 brake clutch 9 first speed reducer 11 second speed reducer 23 wire 27 casing 47 operating lever (operation member) 51 sun gear 53 pinion gear 57 pinion carrier 61 internal gear 65 spline (first meshing) 67) Spline (second meshing portion) 73 Convex portion 75 Circumferential groove 77 Load winding position 79 Free position 81 No load winding position

Claims (5)

[Claims] 1. A motor and a drum around which a wire is wound,
1st which is arranged in series and which transmits the rotational force of the motor to the drum
And a second speed reducer, wherein the first speed reducer has a sun gear to which the driving force of the motor is input, an output side pinion gear meshing with the sun gear, and a first speed reducer provided on the casing side.
Meshing part, a second meshing part provided on the pinion carrier, a load winding position meshing with the pinion gear and the first meshing part, a free position meshing only with the pinion gear, a pinion gear and the second meshing part. Operation member for moving the internal gear to each of the positions through the internal gear that is movable to the unloaded winding position that meshes with the meshing part of the internal gear and the convex portion that engages with the circumferential groove of the internal gear. A winch characterized by having and. 2. The winch according to claim 1, wherein a free position is provided between the load winding position and the no-load winding position along the moving direction of the internal gear during the switching operation. 3. The winch according to claim 1, wherein the internal gear is moved in accordance with the rotation operation of the operation member. 4. The winch according to claim 1, wherein the internal gear is moved along with the sliding operation of the operation member. 5. The planetary gear mechanism having a plurality of stages in which the second speed reducer is arranged in series.
Or the winch according to 4.