JP2001335287A - Clutch changeover device for winch - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the working efficiency by reducing the labor before the clutch hoisting is started. SOLUTION: A clutch is in an open condition with the power transmission is shut off under a condition where a clutch recessed part 11a cut in a ring gear 11 of a planetary gear type reduction gear 2 interposed on a power transmission system between a hydraulic motor 1 and a winch drum 3 is uncoupled from a clutch projecting part 23d formed on a lower end of a clutch shaft 23. When an operator turns ON a drive switch in this condition, the hydraulic motor 1 is driven by the pressure oil to be fed from a hydraulic pump, a piston pin 32 of a hydraulic actuator 33 is protruded to rotate a clutch cylinder 24, and to rotate the clutch shaft 23 in the same direction via an engagement pin 27. When the clutch shaft 23 is rotated, the clutch shaft is supported by a roller pin 29 engaged with a cam groove 28 formed in the clutch shaft 23, and the clutch shaft 23 is lowered, the clutch projecting part 23d is fitted to the clutch recessed part 11a cut in the ring gear 11, and the ring gear 11 is fixed in a clutch coupled condition.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a winch clutch switching device in which a clutch function is obtained by fixing and releasing a ring gear of a planetary gear type reducer interposed between a hydraulic motor and a winch drum. .

[0002]

2. Description of the Related Art Generally, as shown in FIGS. 15 to 17, a winch A using hydraulic pressure is composed of a hydraulic motor 1, a speed reducer 2, a winch drum 3 for winding a wire rope, and a hydraulic motor. A clutch mechanism 4 for intermittently transmitting power transmitted from the first to the winch drum 3 is provided.

The reduction gear 2 is constituted by a reduction mechanism using gears. There are a planetary gear type and an external gear type. The planetary gear type is smaller than the external gear type. Relatively many are adopted.

[0004] Such a winch A is used when loading the luggage by fixing the base 5 to the front part of the bed of a vehicle such as a truck. That is, first, the operator rotates the clutch knob 7 protruding from the clutch operating portion main body 6a of the gear case 6 while pulling the same, and the roll pin mounted on the clutch shaft 8 for attaching the clutch knob 7 to the rear end. 9 is replaced with the upper groove 10b from the lower groove 10a of the hook plate 10 fixed to the clutch operating portion main body 6a (see FIG. 17).

[0005] Then, the tip of the clutch shaft 8 is provided with a clutch recess 11a formed on the outer periphery of a ring gear 11 provided in the planetary gear type reduction gear 2 housed in the gear case 6.
And the ring gear 11 and the planetary gear 13 are in a clutch released state in which the idle rotation occurs.

In this state, after the wire rope wound around the winch drum 3 is pulled out to the rear of the vehicle body and its tip is connected to the load, the worker once returns from the place where the load is present to the position where the winch is located, By rotating the clutch knob 7 in the opposite direction while pulling it again, the roll pin 9 is switched from the upper groove 10b to the lower groove 10a.

[0007] Then, the lower end of the clutch shaft 8 engages with the clutch concave portion 11a formed in the ring gear 11 of the planetary gear type speed reducer 2, and the clutch engages to fix the ring gear 11.

Thereafter, when a drive switch (not shown) is turned on, the hydraulic motor 1 rotates, and a planetary gear 13 disposed between the sun gear 12 and the ring gear 11 formed on the rotary shaft 1a rotates and revolves. The rotation force due to the revolution is transmitted to the winch drum 3 via the planetary carrier 14, and winding is started.

As described above, conventionally, when it is attempted to load a load on the carrier using the winch A, the worker once returns from the place where the load is present to the position where the winch A is located, and engages the clutch of the winch A. After that, the drive switch had to be turned on, which required a lot of work until the start of winding, and the work efficiency was poor.

For this reason, recently, various techniques have been proposed in which a clutch provided on the winch A can be remotely engaged. For example, JP-A-11-1397
No. 73 discloses that a hydraulic actuator is provided on one side in the face width direction of a ring gear constituting a planetary gear type speed reducer, and when hydraulic pressure is supplied to a hydraulic winch, the hydraulic motor rotates and the hydraulic actuator protrudes. There is disclosed a technique in which a ring gear is slid in the axial direction, and a clutch shaft provided in a radial direction of the ring gear is engaged with a clutch recess formed in an outer periphery of the ring gear to fix the ring gear. I have.

[0011]

However, in the above-described prior art, the ring gear is pressed from the face width direction by a hydraulic actuator, and the ring gear is slid in the axial direction.
In order to slide the ring gear while keeping it parallel to the axial direction without tilting, a mechanism such as applying the pressing force of the hydraulic actuator evenly to the side surface of the ring gear is required. The configuration of parts at the boundary with the side surface of the ring gear becomes complicated.

When the clutch is released, the ring gear must be returned to the initial position. The return spring for returning the ring gear to the initial position has a structure in which the ring gear is slid while maintaining the parallel state without tilting. This requires a large component configuration.

As a result, there is a disadvantage that the clutch mechanism becomes complicated and large, and the gear case for accommodating them becomes large inevitably.

In view of the above circumstances, the present invention does not significantly change the configuration of the components housed in the existing gear case, does not increase the size of the entire device, has a simple structure, and reduces the time required for starting the winch winding. It is an object of the present invention to provide a winch clutch switching device that can perform the operation.

[0015]

In order to achieve the above object, a winch clutch switching device according to the present invention has a hydraulic motor connected to a winch drum via a planetary gear type speed reducer. A clutch recess is formed on the outer periphery of the provided ring gear, and a clutch shaft that can be freely engaged and disengaged from the radial direction in the clutch recess is supported on a gear case accommodating the planetary gear type reducer so as to be able to advance and retreat. A cam mechanism for converting the rotational movement of the ring gear into a linear movement in the radial direction with respect to the ring gear, and a hydraulic actuator for applying a rotational movement to the clutch shaft in the radial direction of the clutch shaft. .

In such a configuration, when the hydraulic oil is supplied to the hydraulic motor, the hydraulic motor is driven, and when the hydraulic oil is supplied to the hydraulic actuator, the hydraulic actuator applies a rotational force to the clutch shaft. Then, the clutch shaft rotates by a predetermined angle, and the cam mechanism connected to the clutch shaft causes the clutch shaft to linearly move radially with respect to the ring gear provided in the planetary gear type speed reducer.

In this case, the hydraulic actuator operates with pressure oil for operating the hydraulic motor, and when the clutch shaft rotates due to the operation of the hydraulic actuator, the clutch shaft engages with the clutch recess formed in the ring gear. It is characterized in that it moves linearly in the direction in which it matches.

[0018]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to FIGS. FIG. 1 shows a side sectional view of the winch. The configuration of the winch B employed in the present embodiment is basically the same as the conventional winch A except for the clutch mechanism. Therefore, the same reference numerals are given to the same components as in the related art, and the detailed description is omitted.

Reference numeral 21 in FIG. 1 denotes a clutch operating portion main body constituting a clutch mechanism, which is provided on an upper portion of the gear case 6. The hydraulic motor 1 is fixedly mounted on the left side surface of the gear case 6, and one end of a drum shaft 3 a that supports the winch drum 3 is pivotally supported on the right side surface, and the other end of the drum shaft 3 a stands upright on the base 5. The bracket 22 is pivotally supported.

The sun gear 12 of the planetary gear type reduction gear 2 housed in the gear case 6 is formed integrally with the rotary shaft 1a of the hydraulic motor 1, and the planetary carrier 14 is spline-engaged with the drum shaft 3a.

The ring gear 11 is fitted into a guide groove 6b formed on the inner wall of the gear case 6 and is rotatably supported. A plurality of clutch concave portions 11a are formed at predetermined intervals on the outer periphery of a flange portion 11b integrally formed on one side in the tooth width direction from the ring gear 11.

A clutch shaft 23 and a clutch cylinder 24 are rotatably inserted into an axis of the clutch operating portion main body 21 extending radially with respect to a clutch recess 11a formed in the ring gear 11. I have. The upper part of the clutch cylinder 24 is protruded from the clutch operation part main body 21 to the outside.
Has been planted.

As shown in FIGS. 3 and 4, the clutch shaft 23
The large-diameter shaft portion 23a, the medium-diameter shaft portion 23
b, formed in three stages of thickness of the small diameter shaft portion 23c,
At the lower end of the large-diameter shaft portion 23a, a clutch projection 23d that can be engaged with and disengaged from the clutch concave portion 11a formed in the ring gear 11 is protruded.
Are inserted into the shaft center of the clutch cylinder 24 so as to be able to advance and retreat.

A preload spring 26 is loosely inserted into the outer periphery of the small-diameter shaft portion 23c, and the upper and lower ends of the preload spring 26 contact the upper surface of the inner wall of the clutch cylinder 24 and the upper end of the medium-diameter shaft portion 23b. 23 is constantly biased toward the ring gear 11.

An engagement pin 27 is mounted on the middle diameter shaft portion 23b of the clutch shaft 23 in a direction perpendicular to the axis. Both ends of the engagement pin 27 are formed in a longitudinal groove 2 formed in the clutch cylinder 24.
4a. The clutch shaft 23 and the clutch cylinder 24 are connected to each other with the engagement pin 27 permitting movement in the axial direction.

As shown in FIGS. 7, 10 and 12,
A cam groove 28 is formed on the outer periphery of the large diameter shaft portion 23a formed on the clutch shaft 23. The cam groove 28 is formed in a triangular shape, and a roller pin 29 is engaged in the cam groove 28. As shown in FIG.
Is projected from the tip of the bolt 30, and this bolt 30
Is screwed into the clutch operating portion main body 21 from one side.

As shown in FIG. 7, when the roller pin 29 is located at the top 28a of the cam groove 28, the clutch shaft 2
Reference numeral 3 denotes a clutch member for projecting downward by receiving the urging force of the preload spring 26, and engaging a clutch projection 23d formed at the lower end with a clutch recess 11a formed in the ring gear 11 to fix the ring gear 11. (Fig. 1,
(See FIG. 2).

As shown in FIG. 10 or FIG.
When the roller pin 29 is located at the skirts 28b and 28c of the cam groove 28, the clutch shaft 23 retreats upward, and the clutch projection 23d formed at the lower end is separated from the clutch recess 11a formed in the ring gear 11. The engaged clutch is released (see FIG. 8).

Further, a detent mechanism 31 is provided on the opposite side with respect to the shaft center from the top 28a provided in the cam groove 28 of the clutch shaft 23.
Are arranged. The detent mechanism 31 is used for positioning when the roller pin 29 reaches the top 28a of the cam groove 28.
a, a positioning groove 31a formed along the axial direction, and a ball 31 disposed in the clutch operating portion main body 21 so as to be freely retractable.
b and a preload spring 31 for pressing the back surface of the ball 31b
c and the preload spring 3
1c and a bolt 31d for pressing the back surface.

The lateral groove 2 is formed on the outer periphery of the clutch cylinder 24.
4b is formed, and the tip of the piston pin 32 faces the lateral groove 24b. As shown in FIGS. 6 and 9, the piston pin 32 is exposed from the radial direction to a position deviated to one side with respect to the axis of the clutch cylinder 24. The bottom outer edge of the U-shaped lateral groove 24b is pressed to rotate the clutch cylinder 24 clockwise in the drawing.

A rear portion of the piston pin 32 is provided with a hydraulic actuator 33 fixed to one side of the clutch operating portion main body 21.
And the oil chamber 33a of the hydraulic actuator 33
When the hydraulic pressure is drained, it is returned to the initial position by the urging force of the return spring 33b.

As described above, since the clutch cylinder 24 and the clutch shaft 23 operate integrally in the rotational direction via the engagement pin 27, when the clutch cylinder 24 rotates, the clutch shaft 23 rotates in the same direction. At this time, the clutch shaft 23 moves downward while being supported by the roller pin 29 relatively moving along the cam groove 28.

When the piston pin 32 reaches the protruding end,
The roller pin 29 is set so as to reach the top 28a of the cam groove 28. At this time, the ball 31b of the detent mechanism 31 is engaged with the positioning groove 31a and positioned.

Accordingly, the clutch shaft 23 is rotatable within the range of both skirts 28b and 28c of the cam groove 28, and the clutch protrusion 23d protruding from the lower end of the clutch shaft 23 is provided at a position exactly in the middle thereof. 11 is engaged with a clutch recess 11a formed in the clutch 11.

If the relationship between the cam groove 28 and the roller pin 29 is shown by the position of the operation lever 25 shown in FIG. 5, when the roller pin 29 is engaged with one skirt 28b of the cam groove 28, the operation lever Reference numeral 25 denotes an automatic clutch release position indicated by a one-dot chain line on the right side of the drawing. ,or,
When the roller pin 29 is engaged with the top 28a, the operation lever 25 is at the clutch engagement position in the center of the drawing.

As shown in FIG. 12, when the roller pin 29 is engaged with the other skirt 28c and the manual clutch is released, the lateral groove 24 formed in the clutch cylinder 24 is opened.
The bottom outer edge of b is rotated to a position where interference with the piston pin 32 is avoided (see FIG. 11).

Next, a basic configuration of a hydraulic circuit for supplying hydraulic pressure to the hydraulic motor 1 and the hydraulic actuator 33 will be described with reference to FIG. Two input / output passages 36a and 36b are connected to the hydraulic motor 1, and during normal rotation, one input / output passage 36a functions as an input passage, and the other input / output passage 36b functions as an output passage. At the time of reverse rotation, the other input / output passage 36b functions as an input passage,
One input / output passage 36a functions as an output passage.

Each of the input / output passages 36a and 36b is selectively connected to a main passage 38 and a drain passage 43 via a direction switching valve 37. The upstream of the main passage 38 is connected to a supply passage 41 in which a hydraulic pump 40 is interposed. Further, the supply passage 41 is connected to an upstream bypass passage 42a, and the downstream bypass passage 42b is connected to a drain passage 43. , The two bypass passages 42a, 42
A connection between 2b and a direction switching valve 37 can be freely connected and disconnected. In the main passage 38, a check valve 44 for preventing a reverse flow of the hydraulic pressure from the hydraulic motor 1 is provided.

Further, the supply passage 4 on the downstream side of the hydraulic pump 40
1 and the drain passage 43 communicate with each other via a relief passage 45, and a relief valve 46 for maintaining the oil pressure projected from the hydraulic pump 40 at a predetermined value or less is interposed in the relief passage 45. Reference numeral 47 denotes an oil filter, and 48 denotes an oil pan. Also, the hydraulic pump 40
Are driven to rotate using the power of an engine (not shown).

The directional control valve 37 has a forward operation solenoid 4
9, a reverse operation solenoid 50, and these solenoids 49, 50 are connected to a forward contact 51a and a reverse contact 51b of a remotely operable drive switch 51 shown in FIG. Reference numeral 52 denotes a battery mounted on the vehicle.

The directional control valve 37 shown in FIG. 13 has the drive switch 51 in the neutral position where the bypass switch 42a and 42b are in communication with each other, and the main switch 38 and the other input / output switch. 36b is shut off, and one input / output passage 36a is connected to the drain passage 43.

The forward contact 51a of the drive switch 51
Is turned ON, the forward rotation operation solenoid 49 is turned ON, the two bypass passages 42a and 42b are shut off, the main passage 38 is connected to one input / output passage 36a, and the other input / output passage 36b is connected to the drain. It is communicated with the passage 43.

On the other hand, the reverse contact 51 of the drive switch 51
When b is turned on, the reverse operation solenoid 50 is turned on to shut off the bypass passages 42a and 42b, the main passage 38 is connected to the other input / output passage 36b, and the one input / output passage 36a is connected to the drain passage. 43. Each passage connected to the drain passage 43 side of the direction switching valve 37 is provided with an orifice.
When the hydraulic motor 1 is rotating forward or backward, a predetermined hydraulic pressure is held in the passage upstream of the orifice.

An actuator operating passage 53 communicating with an oil chamber 33a of the hydraulic actuator 33 is branched and connected to one input / output passage 36a. As described above, when the hydraulic motor 1 is in operation, a predetermined hydraulic pressure is held in the passage upstream of the orifice. The hydraulic pressure is also applied during the reverse rotation, and the piston pin 32 maintains the projected state.

Next, the operation of the winch B configured as described above will be described in accordance with the operation procedure. When the hydraulic motor 1 is rotated using the driving force of the engine, the drive switch 51 is in the OFF state.
However, when in the neutral position as shown in FIG. 13, the pressure oil protruding from the hydraulic pump 40 is returned to the drain passage 43 through the bypass passages 42 a and 42 b communicated via the direction switching valve 37. The supply of the pressure oil to the hydraulic motor 1 is shut off.

Since one input / output passage 36a communicating with the hydraulic motor 1 is communicated with the drain passage 43, the hydraulic oil supplied to the hydraulic motor 1 and the oil chamber 33a of the hydraulic actuator 33 is also drained. Hydraulic motor 1
Stops, and the piston pin 32 of the hydraulic actuator 33 retreats under the urging force of the return spring 33b, and enters a standby state.

In this state, when the operation lever 25 is at the automatic clutch release position shown by the dashed line in FIG. 5, the bottom outer edge of the lateral groove 24b formed in the clutch cylinder 24 is retracted as shown in FIG. The cam groove 28 formed in the clutch shaft 23, which is located in the vicinity of the piston pin 32 waiting at the position and is integrally rotated with the clutch cylinder 24, as shown in FIG. Since it is guided to the hem 28b, the clutch shaft 2
8 is lifted upward against the urging force of the preload spring 26, as shown in FIG. 8, and a clutch projection 23d projecting from the lower end is formed on the outer periphery of the ring gear 11 of the planetary gear type speed reducer 2. The clutch is released from the clutch recess 11a.

Then, after the operator unwinds the wire rope wound around the winch drum 3 and connects the tip of the wire rope to the load, the operator turns the drive switch 51 installed at a predetermined location to the forward contact. ON by connecting to 51a side
Make it work.

Then, the forward operation solenoid 49 operates, the direction switching valve 37 shuts off between the bypass passages 42a and 42b, the main passage 38 communicates with one of the input / output passages 36a, and the other input / output passage 36a. The passage 36 b communicates with the drain passage 43.

The hydraulic oil supplied from the hydraulic pump 40 is supplied to the hydraulic motor 1 through the main passage 38 and one input / output passage 36a, and is supplied to the one input / output passage 36a.
Is supplied to the oil chamber 33a of the hydraulic actuator 33 through the actuator operation passage 53 branched and connected to the hydraulic actuator 1 and the hydraulic motor 1 rotates forward, and the piston pin 32 projects by the pressure oil supplied to the oil chamber 33a of the hydraulic actuator 33. I do.

When the piston pin 32 protrudes, its tip presses the bottom outer edge of the lateral groove 24b formed in the clutch cylinder 24, and rotates the clutch cylinder 24 clockwise from the state shown in FIG. 9 to the direction shown in FIG. .

Then, the clutch shaft 23 rotates in the same direction via an engagement pin 27 which is mounted on the clutch cylinder 24 and the cam groove 2 formed on the side surface of the clutch shaft 23.
Rotational motion is converted to linear motion in the axial direction by a cam mechanism of a clutch pin 8 and a roller pin 29 protruding from the clutch operating portion main body 21 engaged with the clutch shaft. With the urging force of 26,
It comes close to the clutch concave portion 11a formed in the ring gear 11 from the radial direction.

When the roller pin 29 reaches the top 28a of the cam groove 28, the ball 31b constituting the detent mechanism 31 receives the urging force of the preload spring 31c and engages with the positioning groove 31a formed on the clutch shaft 23. , The rotational direction of the clutch shaft 23 and the clutch shaft 2
3 is formed at the lower end of the ring gear 1.
1 is engaged with the clutch recess 11a formed in the clutch gear 1 and the clutch is engaged to fix the ring gear 11.

The clutch projection 23d is formed in the clutch recess 11a.
, The ring gear 11 is fixed, and the rotation of the hydraulic motor 1 is transmitted to the drum shaft 3a at a predetermined speed via the planetary gear type speed reducer 2 as in the related art,
The winch drum 3 attached to the drum shaft 3a rotates, and winding of the wire rope starts.

When the winding of the wire rope is stopped, for example, after the luggage connected to the wire rope is placed on the platform of the vehicle in a predetermined manner, the drive switch 51 is turned off.
The main passage 38 and one of the input / output passages 36a are shut off to communicate between the two bypass passages 42a and 42b, and to communicate the other input / output passage 36b with the drain passage 43.

Then, while the rotation of the hydraulic motor 1 is stopped, the pressure oil supplied to the oil chamber 33a of the hydraulic actuator 33 is drained, and the piston pin 32 is gradually retracted by receiving the urging force of the return spring 33b. , Returned to the initial position.

In this state, the operator moves the operation lever 25,
The clutch is rotated from the clutch engagement position shown in FIG. 5 to the clutch release position.

Then, the clutch shaft 23 rotates in the same direction via the clutch cylinder 24 and the engaging pin 27 connected to the operating lever 25, and the clutch shaft 23 is
The rotational motion is converted into a linear motion from the relationship between the clutch pin 11 and the roller pin 29, and rises against the urging force of the preload spring 26, so that the clutch convex portion 23 d formed at the lower end of the clutch shaft 23 has the clutch concave portion 11 a From the clutch. Then, the roller pin 29 is engaged with the skirt portion 28b of the cam groove 28, and the clutch disengagement posture of the clutch shaft 23 is maintained.

When the operating lever 25 is rotated to the manual clutch release position shown by the two-dot chain line in FIG. 5, the lateral groove 24b is avoided with respect to the protruding piston pin 32 as shown in FIG. The clutch cylinder 24 pivots in the direction, and the clutch shaft 23 rises from the relationship between the cam groove 28 and the roller pin 29 as shown in FIG. 12, and the roller pin 29 engages with the other skirt 28b. Is entered.
As a result, the clutch projection 23 d protruding from the lower end of the clutch shaft 23 is provided in the clutch recess 11
a, and the clutch can be forcibly released even though the hydraulic motor 1 is rotating.

The clutch operating section main body 21 is provided with a stopper member such as a stopper for preventing the operation lever 25 from rotating from the clutch engagement position to the manual clutch release side. Therefore, unless the operator removes the blocking member, the operation lever 25 cannot be turned to the clutch releasing side.

Since the clutch can be manually released while the hydraulic motor 1 is rotating, for example, at the time of initial setting when the winch B is mounted on the vehicle, the hydraulic pump 40 is not rotated without rotating the winch drum 3. The test operation of the operation solenoids 49 and 50 can be performed.
In addition, due to long-term use, for example, each operation solenoid 4
If contamination or the like is mixed into the components 9 and 50 and one of the operation solenoids 49 and 50 cannot be returned while being in the ON state, the engine is started and the hydraulic pump 40 is stopped.
When the supply of pressure oil is started, the hydraulic motor 1 is driven irrespective of ON / OFF of the drive switch 51. In such a case, the operation lever 25 is rotated in the manual clutch releasing direction. Accordingly, power transmission between the hydraulic motor 1 and the winch drum 3 can be forcibly cut off.

As described above, according to the present embodiment, since the winch B is basically the same as the conventional structure except for the clutch mechanism, it is possible to apply the winch B without largely changing the conventional components. Can be suppressed, and a rise in product cost can be suppressed.

The ring gear 11 of the planetary gear type speed reducer 2
The clutch shaft 23 with respect to the clutch recess 11a
As a means for engaging and disengaging the clutch projection 23d formed at the lower end of the clutch, a mechanism for converting the rotational movement of the clutch cylinder 24 into a linear movement of the clutch shaft 23 is adopted, so that a large-scale component configuration is not required, and Simplification and downsizing can be realized.

Further, the rotational movement of the clutch cylinder 24 when the clutch is engaged is performed by the hydraulic actuator which operates by using the pressure oil supplied to the hydraulic motor 1, so that the rotation of the hydraulic motor 1 and the rotation of the clutch mechanism are performed. The engagement operation can be started at the same time by turning on the drive switch 51, so that the clutch engagement can be remotely controlled, the time required to start the winch winding up can be reduced, and the working efficiency can be reduced. improves.

[0065]

As described above, according to the present invention,
Without significantly changing the configuration of the parts to be housed in the existing gear case, the entire device does not increase in size, the structure is simple, and the time required for starting the winch winding can be reduced, thereby improving work efficiency. it can.

[Brief description of the drawings]

FIG. 1 is a side sectional view of a winch when a clutch is engaged.

FIG. 2 is an enlarged view of part II in FIG.

FIG. 3 is an enlarged view of a part III in FIG. 2;

FIG. 4 is a sectional view taken along line IV-IV of FIG.

FIG. 5 is a view taken in the direction of arrow V in FIG. 1;

FIG. 6 is a sectional view taken along line VI-VI of FIG. 2;

7A is a sectional view taken along line VII-VII of FIG. 2, and FIG.

FIG. 8 is a side sectional view of a main part of FIG. 1 when the clutch is released.

9 is a sectional view taken along line IX-IX of FIG.

10 (a) is a sectional view taken along line XX of FIG. 8, and FIG. 10 (b) is a left side developed view of FIG. 8 (a).

FIG. 11 is a sectional view corresponding to FIG. 9 when the manual clutch is released.

12A is a cross-sectional view corresponding to FIG. 10 when a manual clutch is released, and FIG. 12B is a left side developed view of FIG.

FIG. 13 is a hydraulic circuit diagram of a winch.

FIG. 14 is a circuit diagram of a drive switch.

FIG. 15 is a side sectional view of a conventional winch.

16 is an enlarged view of the XVI part in FIG.

FIG. 17 is a side view of FIG.

[Explanation of symbols]

 B Winch 1 Hydraulic motor 2 Planetary gear type reducer 3 Winch drum 6 Gear case 11 Ring gear 11a Clutch recess 23 Clutch shaft 28, 29 Cam mechanism (cam groove, roller pin) 33 Hydraulic actuator

Claims (2)

[Claims] 1. A hydraulic motor is connected to a winch drum via a planetary gear reducer, a clutch recess is formed on the outer periphery of a ring gear provided on the planetary gear reducer, and the clutch recess is radially engaged with the clutch recess. A detachable clutch shaft is movably supported by a gear case accommodating the planetary gear reducer, and a cam mechanism for converting the rotational motion of the clutch shaft into a linear motion in the radial direction with respect to the ring gear is connected to the clutch shaft. A clutch actuator for a winch, wherein a hydraulic actuator for applying a rotational motion to the clutch shaft in a radial direction of the clutch shaft is provided. 2. The hydraulic actuator is operated by pressure oil for operating the hydraulic motor, and when the clutch shaft is rotated by the operation of the hydraulic actuator, the clutch shaft is brought into close engagement with the clutch recess formed in the ring gear. 2. The winch clutch switching device according to claim 1, wherein the clutch operation device performs a linear operation in a direction in which the clutch operates.