JP3238853B2 - Winch braking device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a winch braking device for braking a drum when a drum on which a wire is wound is rotated to wind and unwind the wire.

[0002]

2. Description of the Related Art Conventionally, as disclosed in Japanese Patent Publication No. 2-41509, a brake band having a lining attached to an inner peripheral surface thereof is provided, and the brake band is fastened to a brake drum in accordance with operation of a brake pedal. A winch braking device adapted to brake a brake drum is known.

[0003] However, in such a device, as in the case where a suspended hammer club or the like is dropped and a pile hole is excavated, the hammer club or the like is freely dropped and braking is performed by depressing a brake pedal. It gets quite hot. So, to solve this,
As disclosed in JP-A-6-64896, a brake drum is formed integrally with a winch drum, a brake band is wound around the brake drum, and heat dissipation is improved by using a winch drum having a large heat dissipation capacity. Have been.

[0004]

However, in such a conventional apparatus, when the hammer club or the like is dropped and excavated, if the drum is not braked immediately after the landing of the hammer club, the wire jumps out and the drum becomes turbulent. As a result, there has been a problem that the working efficiency is reduced and the wire is severely damaged. Further, if the drum is braked before landing, there is a problem that the bite of the hammer club or the like is reduced, and the work efficiency is reduced.

An object of the present invention is to provide a winch braking device that can prevent a wire from jumping out.

[0006]

In order to achieve the above object, the present invention takes the following means to solve the problem. That is, a brake mechanism that brakes the drum around which the wire is wound by the application of an external force, a brake spring that applies an external force to the brake mechanism, and a biasing force of the brake spring by the action of the introduced fluid pressure. A winch braking device having a release cylinder for releasing the application of the external force, wherein the brake mechanism is a wet-type multi-plate brake mechanism, and a semi-brake cylinder capable of adjusting a plate interval of the wet-type multi-plate brake mechanism by displacement.
Provided with a semi-braking mechanism provided with
The winch braking device is characterized in that the distance between the plates is reduced by a predetermined amount by the introduction of a brake.

The semi-braking mechanism further includes a nozzle communicating with a supply passage for supplying a fluid to the semi-braking cylinder and opening to the low pressure side, and the nozzle moves in accordance with the displacement of the semi-braking cylinder. A control valve provided with a valve body that is disposed so as to be capable of opposing the fluid pressure from the master cylinder and the fluid pressure discharged from the nozzle may be used. Further, the cooling oil of the wet multi-plate brake mechanism and the fluid of the release cylinder and the semi-braking cylinder may be supplied and discharged between the same tank.

[0008]

Embodiments of the present invention will be described below in detail with reference to the drawings. As shown in FIG. 1, reference numeral 1 denotes a drum, and a wire 2 can be wound around the drum 1. The drum 1 is rotationally driven by a hydraulic motor 6 via a planetary reduction gear 4, and the hydraulic motor 6 has a built-in brake 8.

In this embodiment, the planetary reduction gear 4 is
A first sun gear 10 attached to the hydraulic motor 6, a pair of first planetary gears 12 and 14 meshed with the first sun gear 10, and a first planetary gear set. A first internal gear 16 meshed with the first and second gears 12 and 14 and fixed to the inner periphery of the drum 1. First planetary gear 12,
14 is rotatably supported by the first carrier 18,
The first carrier 18 is rotatably supported around the rotation center of the hydraulic motor 6.

The planetary reduction gear 4 is further provided coaxially with the center of rotation of the hydraulic motor 6, and has a second sun gear 20 fixed to the first carrier 18 and a pair of second sun gears 20 meshed with the second sun gear 20. Second planetary gears 22 and 24 and second planetary gear 2
2 and 24 are meshed with each other and a second internal gear 26 fixed to the inner periphery of the drum 1.

The second planetary gears 22 and 24 are connected to the second carrier 2.
The second carrier 28 is provided with a carrier shaft 30 coaxially with the rotation center of the hydraulic motor 6. The drum 1 is rotatably supported on the carrier shaft 30 via a bearing 32, and the drum 1 is rotatably supported on a main body (not shown) via a bearing 34.

An end of the carrier shaft 30 is rotatably supported by a main body (not shown) via a bearing 36. The carrier shaft 30 penetrates an airtight case 38 and is rotatably supported via a pair of bearings 40 and 42. The case 38 is fixed to a main body (not shown).

A number of rotating plates 44 are mounted on the carrier shaft 30 so as to be movable in the axial direction but to rotate integrally with each other. The mounted fixed plate 46 can move in the axial direction, but is attached to the case 38 so that rotation about the axis is transmitted to the case 38. Thus, when an external force is applied and the fixing plate 46 is pressed in the axial direction, the fixing plate 46
The carrier shaft 30 is configured to be braked by a frictional force between the carrier shaft 30 and the rotating plate 44.

The case 38 has a supply hole 48 and a discharge hole 50.
After the cooling oil supplied from the supply hole 48 cools the rotating plate 44 and the fixed plate 46, the discharge hole 50 is formed.
The case 3
8, a rotary plate 44 and a fixed plate 46 constitute a wet-type multi-plate brake mechanism 52.

The wet multi-plate brake mechanism 52 includes a rotating plate 44.
When the cooling oil is present between the rotating plate 44 and the fixed plate 46, as shown in FIG. The braking force is small due to boundary friction, and the braking force is proportional to the plate interval.

The rotating plate 44 and the fixed plate 4 are provided in the case 38.
6, facing the cylinder rods 54,
Release cylinders 58 and 60 are provided so as to project 56. Brake springs 66, 68 are housed in the cylinder tubes 62, 64 of the release cylinders 58, 60 so as to urge the cylinder rods 54, 56 in the protruding direction. When the operating oil is supplied to the release cylinders 58, 60, the cylinder rods 54, 56
It is configured to pull against the biasing force of 6,68.

The cylinder rods 54, 56 have cylinder rods 74, 76 of the semi-braking cylinders 70, 72, respectively.
Are connected so that the cylinder tubes 78 and 80 of the semi-braking cylinders 70 and 72 can move within the case 38. A coil spring 8 inserted into cylinder rods 74 and 76 is provided in the cylinder tubes 78 and 80.
2,84 are stored.

When no hydraulic oil is supplied to the release cylinders 58, 60 and the semi-braking cylinders 70, 72, the urging forces of the braking springs 66, 68 are applied to the cylinder rods 54, 56, as shown in FIG. Cylinder rod 74,
76, it is configured to be applied as an external force to the wet-type multi-plate brake mechanism 52 via the cylinder tubes 78 and 80.

When the wire 2 is wound by the rotation of the drum 1 to be described later, the carrier shaft 30 needs to be held so as not to rotate, and a large reaction force due to the winding is applied to the wet multi-plate brake mechanism 52. At this time, the wet multi-plate brake mechanism 52 requires a large braking force, and the applied external force also needs to be large. Therefore, the urging force of the braking springs 66, 68 is very large, and therefore, the release cylinders 58, 60 have a large cylinder diameter so that a large thrust can be obtained.

When hydraulic oil is supplied to the release cylinders 58, 60 and the semi-brake cylinders 70, 72, the release cylinders 58, 60 resist the urging forces of the brake springs 66, 68, as shown in FIG. And cylinder rods 54 and 56
Is pulled, and the semi-brake cylinders 70 and 72
Cylinder tubes 78, 80 against the urging force of
Is moved toward the wet-type multi-plate brake mechanism 52, and the distance between the rotating plate 44 and the fixed plate 46 can be adjusted according to the displacement.

The braking force enough to brake the rotation due to the inertia of the drum 1 is small, and when the wet multi-plate brake mechanism 52 having a capacity capable of obtaining the braking force required at the time of winding or the like is used, the inertial rotation is braked. In order to generate a sufficient braking force, it is necessary to use fluid friction and boundary friction as shown in FIG. Therefore, the semi-braking cylinders 70, 7
The hydraulic pressure supplied to the cylinder 2 and the cylinder diameters of the semi-braking cylinders 70 and 72 need only be such that a thrust capable of adjusting the plate gap can be obtained, and a small force is sufficient compared to the external force at the time of winding described above.

Supply pipes 86 and 88 for supplying hydraulic oil are connected to the semi-braking cylinders 70 and 72, and are provided so as to move together with the cylinder tubes 78 and 80. Nozzles 90 and 92 opened in the case 38 are connected to the supply pipes 86 and 88.
Is provided in parallel with the axial direction of the cylinder rods 74 and 76, and is opened on the side opposite to the wet-type multi-plate brake mechanism 52.

Opposite to the nozzles 90, 92, valve bodies 94, 96 capable of opening and closing the nozzles 90, 92 are provided, and the valve bodies 94, 96 are provided with hydraulic oil discharged from the nozzles 90, 92. As shown in FIG. 2, when the operator depresses the brake pedal 98, the operation force of the master cylinder 100 that discharges the working oil is received in the opposite direction. .

In this embodiment, the wet multi-plate brake mechanism 52
And the hydraulic oil supplied to the release cylinders 58, 60 and the semi-brake cylinders 70, 72 are shared by the same fluid, and are both stored in the tank 102. Cooling oil is drawn from the tank 102 by a cooling pump 104 and supplied to the case 38 from the supply hole 48 through a cooling passage 109 in which a filter 106 and a cooler 108 are provided. . Filter 1
A check valve 110 is connected in parallel to 06.

Further, the operation pump 11 is supplied from the tank 102.
The hydraulic oil pumped and pressurized by the pump 2
4. The throttle 118 is connected to the release cylinders 58 and 60 via a release passage 117 in which the throttle 118 is provided. The release valve 114 shuts off the communication between the operating pump 112 and the release cylinders 58 and 60 when the excitation signal is not input and shuts off the communication between the release cylinders 58 and 60 and the tank 102 when the excitation signal is input. A communication position 114b for connecting the operation pump 112 to the release cylinders 58 and 60 is provided.

Operating pump 112 and semi-braking cylinder 7
0, 72 are the throttle 120, the supply passage 121, the supply pipe 8
The supply passage 121 is connected to the tank 102 via a relief valve 122. The discharge side of the operation pump 112 is connected to the tank 102 via a relief valve 126. Relief valve 1
Reference numeral 26 indicates that the discharge pressure from the operating pump 112 is maintained at a set pressure, and the set pressure of the relief valve 122 is set lower than the set pressure of the relief valve 126.

The above-described nozzles 90, 92 and valve bodies 94, 9
Reference numeral 6 denotes control valves 130 and 132 for controlling hydraulic oil supplied to the semi-braking cylinders 70 and 72. In FIG.
Shown by symbol. In this embodiment, the semi-braking cylinders 70, 7
2. The semi-braking mechanism 134 is constituted by the master cylinder 100 and the control valves 130 and 132. The discharge hole 50 of the case 38 is connected to the tank 102 via a return passage 135, and the cooling passage 109 and the return passage 135 are connected by a check valve 136.

Next, the operation of the above-described winch braking device of this embodiment will be described. First, when the wire 2 is wound up, the disconnection valve 114 is not output to the excitation signal, and is set to the cutoff position 114a. Therefore, the release cylinders 58 and 60 are communicated with the tank 102 via the throttle 118 and the release valve 114, and the cylinder rods 54 and 56 are protruded by the urging forces of the brake springs 66 and 68.

As a result, the cylinder rods 74 and 76 are pushed, and the semi-braking cylinders 70 and 72
Hydraulic oil is discharged from the case 92 into the case 38. And
As shown in FIG. 3, an external force corresponding to the urging force of the brake springs 66, 68 is applied to the wet multi-plate brake mechanism 52 via the cylinder tubes 78, 80. Accordingly, in the wet multi-plate brake mechanism 52, the rotating plate 44 and the fixed plate 46 are pressed against each other,
The rotation of the carrier shaft 30 is restricted.

On the other hand, high-pressure hydraulic oil is supplied to the hydraulic motor 6, the built-in brake 8 is released, and the first sun gear 10 is rotated. Therefore, the first planetary gears 12 and 14 revolve around the first sun gear 10 while rotating, and the first carrier 1
The second sun gear 20 rotates via 8. And the second
The planetary gears 22 and 24 rotate, the drum 1 rotates via the first internal gear 16 and the second internal gear 26, and the wire 2 is wound up. The wire 2 can be paid out by rotating the hydraulic motor 6 in the reverse direction.

When the wire 2 is wound up and a hammer club (not shown) is lifted to a predetermined height and then dropped freely, an excitation signal is output to the release valve 114 to switch to the communication position 114b. Thereby, the release cylinder 5
High pressure hydraulic oil is supplied to the pumps 8 and 60 from the operating pump 112 via the release valve 114 and the throttle 118.

As shown in FIG. 4, the release cylinders 58, 6
No. 0 pulls the cylinder rods 54, 56 against the urging force of the braking springs 66, 68, and the cylinder tubes 78, 8 via the cylinder rods 74, 76 and the coil springs 82, 84.
0 moves in a direction away from the wet-type multi-plate brake mechanism 52.

Accordingly, since the application of the external force to the wet-type multi-plate brake mechanism 52 is released, the carrier shaft 30 can freely rotate. Thus, even when the built-in brake 8 is in the braking state, the first planetary gears 12 and 14 and the second planetary gears 22 and 24 are freely rotatable, so that the drum 1 can freely rotate. Thereby, the wire 2 is pulled out, and the hammer club falls by its own weight.

In this state, the operator operates the brake pedal 98
Is depressed, hydraulic oil is supplied from the master cylinder 100 to the control valves 130 and 132. Thereby, the valve element 9
4 and 96 move toward the nozzles 90 and 92 under the action force. Therefore, the opening areas of the nozzles 90 and 92 decrease, the pressure in the supply pipes 86 and 88 increases, and hydraulic oil is supplied to the semi-braking cylinders 70 and 72.

As shown in FIG. 5, the cylinder tube 7
8, 80 are pushed toward the wet multiple disc brake mechanism 52 against the urging force of the coil springs 82, 84 and displaced. At this time, the supply pipes 86 and 88 also move, and the valve bodies 94 and 88 are moved.
The distance between the nozzle 96 and the nozzles 90 and 92 increases. Then, the acting force on the valve bodies 94 and 96 by the hydraulic oil discharged from the nozzles 90 and 92 decreases, and the master cylinder 100
Since the acting force on the valve bodies 94 and 96 by the hydraulic oil from the valve body exceeds, the valve bodies 94 and 96 move following the nozzles 90 and 92.

The supply pipes 86, 8 are balanced by a balance between the acting force of the working oil from the nozzles 90, 92 on the valve bodies 94, 96 and the working force of the working oil from the master cylinder 100.
The working oil pressure in 8 is determined. When the brake pedal 98 is strongly depressed, the operating oil pressure in the supply pipes 86 and 88 increases, and when the brake pedal 98 is lightly depressed, the supply pipe 8
The working oil pressure in 6,88 also decreases. In addition, supply pipe 8
When the working force of the working oil pressure supplied to the semi-brake cylinders 70, 72 from the 6, 88 and the biasing forces of the coil springs 82, 84 are balanced, the cylinder tubes 78, 80 stop their displacement.

Accordingly, the cylinder tubes 78, 80 are displaced in accordance with the amount of depression of the brake pedal 98, and the gap between the rotating plate 44 and the fixed plate 46 is reduced in accordance with the displacement, and the fluid friction, A braking force due to boundary friction acts on the carrier shaft 30. As a result, the drum 1 is also semi-braked when the carrier shaft 30 is semi-braked, but the braking force is such that the rotation is braked by the inertia of the drum 1 itself.

Therefore, since the free fall of the hammer club is only braked by a slight braking force, the reduction of the bite into the ground by the free fall is slight. When the hammer club digs into the ground, the rotation of the drum 1 due to inertia is stopped by the semi-braking of the wet-type multi-plate brake mechanism 52, so that the wire 2 does not fly out and the wire 2 is prevented from being turbulently wound.

On the other hand, the cooling pump 1
Hydraulic oil discharged from 04 is supplied through the filter 106 and the cooler 108 to cool the wet multi-plate brake mechanism 52 during semi-braking. Then, it is returned to the tank 102 from the discharge hole 50 via the return passage 135.

As described above, according to the winch braking device of the present embodiment, the wet multi-plate brake mechanism 52 semi-brakes by the displacement of the semi-braking cylinders 70 and 72 during free fall,
Rotation due to the inertia of the drum 1 can be suppressed, and turbulence of the wire 2 can be prevented, and the use of the wet multi-plate brake mechanism 52 can effectively prevent heat generation during semi-braking.

In this embodiment, both cylinder rods 54, 60 of the release cylinders 58, 60 and the semi-brake cylinders 70, 72 are used.
Although the two-stage cylinder is configured by connecting 56, 74, and 76, the invention is not limited thereto, and the invention can be implemented by disposing the release cylinders 58 and 60 and the semi-braking cylinders 70 and 72 in parallel.

The wet-type multi-plate brake mechanism 52 has a simple structure by also functioning as a means for braking the rotation of the carrier shaft 30 of the planetary reduction gear 4 when the hydraulic motor 6 rotates. When rotating via a speed reducer using a spur gear, the wet multi-plate brake mechanism 52 may be configured to directly brake the drum 1 instead of the carrier shaft 30.

Further, the semi-braking mechanism 134 includes the control valve 13
0,132 without using the semi-braking cylinders 70,7
The maximum stroke of 2 is configured so that the plate interval of the wet-type multi-plate brake mechanism 52 is narrowed by a predetermined amount to the extent that a braking force due to fluid friction and boundary friction can be obtained. , 72,
The present invention can also be implemented by performing a semi-braking by the displacement of the semi-braking cylinders 70, 72 .

As described above, the present invention is not limited to such embodiments at all, and can be implemented in various modes without departing from the gist of the present invention.

[0045]

As described above in detail, the winch braking device of the present invention performs half braking by the wet multi-plate brake mechanism by the displacement of the semi-braking cylinder at the time of free fall, suppresses the rotation due to the inertia of the drum, and suppresses the wire disturbance. This has the effect of preventing winding. Further, by using the wet multi-plate brake mechanism, heat generation at the time of semi-braking can be effectively prevented, and the size of the apparatus can be reduced by sharing the operating oil and the cooling oil of the wet multi-plate brake mechanism.

[Brief description of the drawings]

FIG. 1 is a schematic configuration diagram of a winch braking device as one embodiment of the present invention.

FIG. 2 is a hydraulic circuit diagram of the present embodiment.

FIG. 3 is a schematic configuration diagram of a main part in a state of winding up by a drum according to the present embodiment.

FIG. 4 is a schematic diagram of a main part of the embodiment in a free fall state.

FIG. 5 is a schematic diagram of a main part of a half-braking state according to the present embodiment.

FIG. 6 is a graph showing a relationship between a plate interval and a braking force of the wet multi-plate brake mechanism of the present embodiment.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 ... Drum 2 ... Wire 4 ... Planetary reduction gear 30 ... Carrier shaft 52 ... Wet multi-plate brake mechanism 54, 56, 74, 76 ... Cylinder rod 58, 60 ... Release cylinder 66, 68 ... Brake spring 70, 72 ... Semi-brake Cylinder 90, 92 ... Nozzle 94, 96 ... Valve 100: Master cylinder 130, 132 ... Control valve 134 ... Semi-braking mechanism

Claims (3)

(57) [Claims] 1. A brake mechanism for braking a drum around which a wire is wound by application of an external force, a brake spring for applying an external force to the brake mechanism, and a biasing force of the brake spring by an action of an introduced fluid pressure. A winch braking device comprising a release cylinder for releasing the application of the external force in opposition to the winch, wherein the brake mechanism is a wet-type multi-plate brake mechanism, and the distance between the plates of the wet-type multi-plate brake mechanism can be adjusted by displacement.
A semi-braking mechanism provided with a functional semi-braking cylinder;
A predetermined distance is set by introducing the fluid into the brake cylinder.
A winch braking device characterized by narrowing . 2. The semi-braking mechanism further includes a nozzle communicating with a supply passage for supplying a fluid to the semi-braking cylinder and opening to a low pressure side, and the nozzle moves in accordance with the displacement of the semi-braking cylinder. 2. The winch brake according to claim 1, further comprising a control valve disposed so as to be capable of operating and opposing a fluid pressure from a master cylinder and a fluid pressure discharged from the nozzle. apparatus. 3. A cooling oil for the wet multi-plate brake mechanism,
2. The system according to claim 1, wherein the fluid in the release cylinder and the fluid in the semi-braking cylinder are supplied to and discharged from the same tank.
Or the winch braking device according to claim 2 .