JPS6216918B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION Technical Field The present invention relates to a power winch for transporting cargo such as felled wood.

Conventional technology When using a conveyor that moves on overhead cables to collect thinned trees that are scattered over a wide area, such as in an afforestation area, the number of felled trees within a unit area is small, so it is necessary to replace the overhead cables. It must be repeated many times.

Particularly in recent years, in intensive forestry, which requires environmental conservation and an increase in the growth of timber, the amount of felling per given area has decreased significantly, and the number of times cables have to be replaced has increased. This has increased to the point where the work of relining cables now occupies a greater weight than the work directly involved in collecting cargo.

Therefore, there has been a demand for simplification and simplification of cable laying. In other words, the endless tyler system that has been widely used in the past has one span of overhead cable, one span of pulling cable, two spans of endless cable for running the conveyor, and two spans of pulling cable that intercepts timber on the side. This method involves stringing a minimum of six spans of cable, and this type of method is gradually being avoided.
A four-span cable system consisting of an aerial cable, a pull cable, and a pull cable, or a three-span cable system in which the aerial cable is omitted is increasingly being adopted.

However, in all of these methods, when transporting cargo, the cargo is transported in a suspended state by pulling the cargo with power using a pull cable and applying a brake on the return cable. Therefore, if the tension between the two cables becomes unbalanced, the cables may be severed or the cargo may be dragged along the ground. Then, as the cargo is dragged along the ground, the ground surface becomes rough and may cause landslides. Therefore, conveyance operation requires uniform movement of both cables, which not only requires advanced technology but also does not allow for high work efficiency. Since it must be used for braking force,
Economical driving could not be expected.

In order to solve this problem, a power winch disclosed in Japanese Patent Publication No. 56-27436 by the same applicant was developed. This winch has a torque converter interposed between the winding side drum and the unwinding side drum so that the rotational torque of both drums is the same, which increases the tension of the rope on the winding side and the unwinding side. This is to adjust the balance. However, this power winch uses an expensive torque converter, resulting in large efficiency losses, large size, and overall high cost.

OBJECT OF THE INVENTION It is an object of the present invention to provide a power winch in which the above-mentioned problems are universally resolved.

Embodiment Hereinafter, an embodiment embodying the present invention will be described based on the drawings. First, the configuration of the power winch 1 will be described. At the rear of the machine base 2 of the winch 1, an engine room 3 containing an engine (not shown) as a drive source is provided.
Further, first, second, and third drums 5, 6, and 7 are rotatably supported between the left and right frames 4 at the front of the machine base 2, and on both sides of these drums 5, 6, and 7, , as shown in FIGS. 3 to 5, the first to sixth clutches 8 to 13 are connected to the first to sixth clutches, respectively.
Large diameter gears 14 to 19 are provided. When the first to sixth clutches 8 to 13 are closed, the first to sixth large diameter gears 14 to 13 are closed.
19 and the first, second, and third drums 5, 6, and 7 are coupled to each other, and the drums 5, 6, and 7
and the large diameter gears 14 to 19 rotate integrally, and
By opening the first to sixth clutches 8 to 13, the coupling between the first, second, and third drums 5, 6, and 7 and the first to sixth large diameter gears 14 to 19 is released. Ru. Further, a brake device (not shown) acts on each drum 5, 6, 7, and by releasing the action of the brake device, each drum 5, 6, 7 becomes rotatable.

Below the winding drums 5, 6, and 7, there are support shafts 20, 20 and 20, respectively, between the frames 4.
21 are fixed, and on both ends thereof, the marks shown in FIGS.
As shown in FIG. 5, the first to fourth small diameter gears 22
- 25 are rotatably supported, and the first to fourth small diameter gears 22 to 25 are connected to the first to sixth large diameter gears 14 located on both front and rear sides thereof, respectively.
It meshes with ~19.

A forward/reverse switching mechanism 26 is disposed below the support shaft 20 on the rear side, and its input shaft 27 is connected to the fluid transmission 2.
8 to the output shaft of the engine, and as shown in FIGS. 1 and 4, a drive gear 30 on the output shaft 29 is connected to the first small diameter gear 2.
It meshes with 2.

As shown in FIGS. 3 to 5, first and second intermediate gears 32 and 33 are mounted on a support shaft 31 rotatably supported between the frames 4 below the second drum 6. The first intermediate gear 32 is fixed, and the first intermediate gear 32 meshes with the third large-diameter gear 16, as shown in FIG.

As shown in FIGS. 1 and 2, the frame 4 on one side includes a differential gear mechanism 34 and a hydraulic pump 3.
5 is provided. As shown in FIGS. 3 and 5, the differential gear mechanism 34 includes a sun gear 36,
It has a pair of planetary gears 37, an output gear 38 made of an internal gear that meshes with the planetary gears 37, and a return gear 39 that supports both the planetary gears 37 on the side.
0, an input gear 41 that meshes with the sixth large-diameter gear 19 is supported, and a return gear 39 meshes with the second intermediate gear 33. Further, a rotating shaft 42 of the hydraulic pump 35 is connected to the center of the sun gear 36.

Next, the circuit of the hydraulic pump 35 will be explained with reference to FIG. A first relief valve 53 is connected to a pipe line 52 between the discharge side of the hydraulic pump 35 and the oil tank 51.
A solenoid switching valve 55 that can be switched between two positions is connected to the pipe line 54 between the vent side of the valve 3 and the pipe line 52. Further, a second relief valve 57 having a lower set pressure than the first relief valve 53 is connected to a conduit 56 between one port of the switching valve 55 and the conduit 52.

Next, the power winch 1 configured as above
Describe a tethering system that uses As shown in FIGS. 7a to 10a, FIGS. 11 and 12, the traveling overhead cable 61, which is wound around the first drum 5 at one end, is connected to the guide pulley attached to the base column 62. 63 and a guide pulley 65 attached to a front post 64, respectively, so as to be movable and supported, and the other end is connected to a carriage 66, which will be described later. Then, as the first drum 5 rotates in the clockwise direction in the drawing, the traveling overhead cable 61 is wound up.

A hoisting carriage 66 (hereinafter simply referred to as a carriage) is suspended from the running overhead cable 61 between the guide pulleys 63 and 65, and the carriage 66 rotates clockwise when the first drum 5 rotates. By traveling in the direction of arrow P, the traveling overhead cable 61 is moved to the front post 64 side, and the first drum 5 rotates counterclockwise, causing the traveling overhead cable 61 to travel in the direction of reverse arrow P. As a result, it is moved to the base pillar 62 side. The carriage 66 has an hourglass-shaped pulley 67 as a driving pulley and two sets of guide pulleys 6.
8,69 are provided. Also, the carriage 66
A winding shaft (not shown) is supported coaxially with the hourglass-shaped pulley 67, and a hanging rope 7 is attached to the outer periphery of the winding shaft (not shown).
0 is wrapped around it. The hanging rope 70 is suspended downward via a fleet angle pulley (not shown) and a guide pulley 71, and a load hook 72 is provided at its tip. The winding shaft is rotated integrally with the hourglass-shaped pulley 67, and as the hourglass-shaped pulley 67 is rotated in the clockwise direction in the drawing, the winding shaft is connected to the hanging rope 70. The loading hook 72 is rotated in a direction in which the loading hook 72 is pulled out.

Both ends of a load guide rope 73 are wound around the second and third drums 6, 7 in the same winding direction, and as both drums 6, 7 rotate clockwise, the load guide rope 73 is wound around the second and third drums 6, 7. is wound up. This load guide cable 73 is supported by a guide pulley 74 on the base pillar 62, and is wound around the hourglass-shaped pulley 67 at least once and a half at the intermediate portion. Also, the load guide rope 73 is removed from the hourglass-shaped pulley 67, and as shown in FIGS. 11 and 12.
As shown in the figure, the guide pulley 6 of the carriage 66
8 and 69, and orbits on a guide pulley 75 located on the side of the traveling overhead cable 61.

An auxiliary carriage 76 is suspended from the load guide rope 73 between guide pulleys 68 and 69 on one side of the carriage 66 and a guide pulley 75 on the side of the overhead cable 61. The carriage 76 is provided with a clamp 77 and a load hook 78 which are fixed to the load guiding cable 73 between the guide pulley 68 and the guide pulley 75.

Next, the power winch 1 configured as above
Explain the effect of First, when collecting felled timber immediately below or in the vicinity of the traveling overhead cable 61, as shown in Fig. 7a
As shown in FIG. 3, the middle portion of the load guiding rope 73 is wrapped around the hourglass-shaped pulley 67 of the carriage 66. In this state, the switching valve 55 shown in FIG. 6 is switched to the position shown in FIG.
Close the sixth clutch 8, 11, 13 and release the brake. In this way, the load guiding rope 7
Based on the tension of 3, rotational torque is applied to the sun gear 36 via the large diameter gears 17 and 19, the small diameter gear 25, the input gear 41, the output gear 38, and the planetary gear 37, and the rotational torque is applied to the rotation shaft 42 of the hydraulic pump 35. Although the torque is applied, in this case, the rotation shaft does not rotate because it is lower than the set pressure of the second relief valve 57. Then, as shown in FIG. 7c, the rotation of the engine changes from the forward/reverse switching mechanism 26 to
The rotation is transmitted in the clockwise direction to the first drum 5 via the small diameter gear 22 and the first large diameter gear 14, and the traveling overhead cable 61 is wound up. Therefore, the carriage 66 is moved toward the front post 64 side.

As the carriage 66 moves toward the front column 64, the load guiding cable 73 is pulled, and the second and third drums 6 and 7 are rotated in the rewinding direction. In this case, the fourth and sixth large diameter gears 17, 19
are meshed and connected by the fourth small-diameter gear 25, so the rotational speeds of the second and third drums 6 and 7 are the same. As shown in FIG. 7d, the rotation of the fourth and sixth large-diameter gears 17 and 19 as the second and third drums 6 and 7 rotate in the rewinding direction is controlled via the input gear 41. and is transmitted to the output gear 38. Therefore, the planetary gear 37 rotates around the sun gear 36 and the return gear 39 is rotated, and the rotational power is transmitted to the second intermediate gear 33 and the first intermediate gear 3.
2, third large diameter gear 16, first small diameter gear 22,
It is recovered to the first drum 5 via the first large-diameter gear 14 as rotational power in the winding direction. In addition,
In the power winch 1 of this embodiment, the reduction ratio of rotation transmission from the unwinding side drum to the winding side drum is 0.7936, so that torque based on the unwinding tension is always applied to the input gear 41. ing.

As the first drum 5 is wound, the winding diameter of the first drum 5 increases, so the amount of winding per unit rotational speed increases, and as a result, the winding diameter of the load decreases. A gradually increasing tension is applied to the upper guide rope 73. Therefore, the torque of the unwinding rotation of the second and third drums 6 and 7 becomes large, and the rotational torque applied to the sun gear 36 of the differential gear mechanism 34 becomes large. When the rotation torque exceeds a certain level, the rotation of the hydraulic pump 35 is allowed by the action of the second relief valve 57, and based on this, the rotation of the second and third drums 6, 7 is allowed to increase speed. , both cables 61 and 73 move at the same speed, and excessive tension on the load guiding cable 73 is prevented. In this manner, the carriage 66 is moved toward the front column 64 while the tension of both the cables 61 and 73 is maintained at a predetermined level, and the carriage 66 can be placed at the load-loading work position.

After the carriage 66 has been placed in the working position in this way, as shown in FIG. Close. In this way, the drive gear 30, the first small gear 2
2, the third drum 7 via the third large-diameter gear 16, the third small-diameter gear 24, and the fifth large-diameter gear 18.
is rotated in the winding direction, and along with the winding, the second drum 6 is rotated in the unwinding direction, and the loading hook 72 is lowered. The rotation of the second drum 6 is transmitted to the differential gear mechanism 34 through the fourth large-diameter gear 17 and the input gear 41 in the same manner as described above.
from there to the second and first intermediate gears 3
3, 32, the third large diameter gear 16, the third small diameter gear 24, and the fifth large diameter gear 18.

After the wood is hung on the loading hook 72 at the loading point in this way, the third
Then, the sixth clutch 10, 13 is closed and the switching valve 55 shown in FIG. 6 is held in position. Therefore, as shown in FIG. 8c, the second drum 6 is rotated in the winding direction via the drive gear 30, the first small diameter gear 22, and the third large diameter gear 16, and the load guiding rope is rotated. At the same time, one side of the load guide rope 73 is wound up, and the other side of the load guide rope 73 is unwound, and the third drum 7 is unwound and rotated.
The signal is transmitted to the input gear 41 via the large diameter gear 19 , the fourth small diameter gear 25 , and the fourth large diameter gear 17 .

In the above case, if the rotational torque on the unwinding side becomes large, it is adjusted in the differential gear mechanism 34 by the action of the hydraulic pump 35 and the relief valve in the same manner as described above, and the difference in the winding diameter is reduced. It is absorbed.

The wood W lifted in the above manner is the original pillar 6.
To convey to the second side, as shown in Figure 10b,
The switching valve 55 is switched to the position to close the second, third and fifth clutches 9, 10, 12.
In this way, the second drum 6 is rotated in the winding direction via the drive gear 30, the first small diameter gear 22, and the third large diameter gear 16, and the third small diameter gear 24 and the fifth The third drum 7 is also rotated in the winding direction via the large-diameter gear 18 . As a result, the load guiding rope 73 is wound around the second and third drums 6 and 7 at the same time, and the carriage 66 is moved toward the base pillar 62 while lifting the wood. Then, as the carriage 66 travels, the traveling overhead cable 61 on the first drum 5 is rewound, and its rotation is controlled by the second large-diameter gear 15, the second small-diameter gear 23, the fourth
is transmitted to the input gear 41 via the large-diameter gear 17 .

In this case as well, the tension of the aerial cable 61 to be rewound that exceeds a predetermined value is absorbed in the differential gear mechanism 34 by the action of the hydraulic pump 35 and the first relief valve 53 having a high set pressure.

Next, in order to collect wood from a position away from the traveling overhead cable 61, as shown in FIGS. 11 and 12, a guide pulley 75 is provided near the logging point.
The load guide rope 73 is removed from the hourglass-shaped pulley 67, and the load guide rope 73 is attached to the guide pulley 68 of the carriage 66.
69 and around the guide pulley 75.
Further, an auxiliary carriage 76 having a load hook 78 is attached to the load guide cable 73 between the guide pulleys 68, 69 and the guide pulley 75 using a clamp 77.

Naturally, in this case each clutch 8
The operations of steps 1 to 13 are brought to the states shown in FIGS. 8b and 9b. That is, as shown in FIG.
8, set the clutch to the state shown in Fig. 8b, and set the switching valve 55 to the position.
Adjust the set pressure of the second relief valve 57 to be slightly higher, and set the clutch to the state shown in Fig. 9b when pulling the loading hook 72 along with the wood as shown in Fig. 12. .

As described above, in this power winch 1, unwinding torque can be recovered as winding force, so efficient operation can be performed, and a torque converter is installed between the winding side and the unwinding side. Efficient operation can be achieved compared to an interposed power winch. In other words, in systems that use a torque converter, all of the unwinding power passes through the torque converter, but efficiency is poor due to power loss occurring in the turbine pump and turbine, and in reality only about 60% is recovered.
In contrast, this power winch 1 is efficient because it absorbs only the torque caused by excess tension and directly recovers the rest through the gears. Furthermore, as mentioned above, since the torque converter receives all the power of unwinding, it cannot be made smaller, and inevitably requires a large space and is expensive. A small hydraulic pump operated by extra torque is sufficient for this power winch 1.

Effects of the Invention As exemplified in the embodiments above, the present invention provides a power winch that recovers the unwinding rotational force of the unwinding side drum as the winding rotational power of the winding side drum. A differential gear mechanism is interposed between the drum and the drum on the rewinding side so that the recovered power is transmitted through the differential gear mechanism, and a hydraulic pressure is provided on the differential output side of the differential gear mechanism. By connecting the rotating shaft of the pump and connecting a relief valve to the absorption side or the discharge side of the hydraulic pump that allows the rotating shaft to rotate when a torque of a predetermined amount or more is applied to the rotating shaft, The tension of the cable can be automatically adjusted for efficient and safe operation, and a torque converter for tension adjustment is no longer required, which has the excellent effect of reducing the overall cost of the winch.

[Brief explanation of the drawing]

The drawings show a power winch that embodies the present invention; FIGS. 1 and 2 are a side view and a plan view showing the entire power winch, and FIG. 3 is a schematic diagram showing the operating part of the power winch. Figures 4 and 5 are schematic diagrams showing the gear mechanism of the power winch, Figure 6 is a circuit diagram of the hydraulic pump, and Figures 7a--
d, Figure 8 a-d, Figure 9 a-d, Figure 10 a-
d, Figures 11 and 12 respectively show different operating modes of the power winch, Figures a, 11 and 12 are overall views showing the cable tensioning, and Figures b are schematic diagrams showing the open and closed states of the clutch. Figures c and d are schematic diagrams showing the state of power transmission. Power winch...1, first, second, third drum...5,6,7, differential gear mechanism...34, hydraulic pump...35, relief valve...53,5
7.

Claims (1)

[Scope of Claims] 1. In a power winch configured to recover the unwinding rotational force of the unwinding drum as the winding rotational power of the winding side drum, the winding side drum and the unwinding side drum are connected to each other. A differential gear mechanism is interposed between the two, so that the recovered power is transmitted through the differential gear mechanism, and a rotating shaft of a hydraulic pump is connected to the differential output side of the differential gear mechanism. A power winch, characterized in that a relief valve is connected to the discharge side of the hydraulic pump to allow rotation of the rotating shaft when a torque exceeding a predetermined value is applied to the rotating shaft.