JPH06200989A - Rotational output device - Google Patents

Abstract

PURPOSE:To lightly perform idling of a drum and prevent unreasonable enlargement of the size of the drum. CONSTITUTION:This rotational output device is provided with a drum 2 and a reduction gear 3 which is received in the drum 2 and provided with an internal gear 31 for output on the outermost circumference, and the power oil pressure 5 can be transmitted to the drum 2 through the reduction gear 3. The internal gear 31 is fittedly mounted on the inner circumference of the drum 2 rotatably and movably in the axial direction, the internal gear 31 is fitted on the outer circumference of a core member 1 holding the reduction gear 3 movably in the axial direction, and a hydraulic actuator 5 for reciprocating the internal gear in the axial direction against the drum is constituted by the use of the core member 1 and the internal gear 31, and an engaging part 6 to engage or disengage by reciprocating movement of the internal gear 31 is provided between the internal gear 31 and the drum 2.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary output device applicable to winches, wheel drive devices and the like.

[0002]

2. Description of the Related Art A rotary output device of this type, for example, a winch mounted on a truck or the like, transmits the rotary power of a prime mover such as a hydraulic motor to a drum as a rotary output body through a speed reducer. However, a device in which the speed reducer is housed in the drum has also been developed. In many of such winches, a clutch is provided between the prime mover and the drum so that the drum can idle when necessary.

The method for making the drum idle is as follows:
A clutch device is installed between the input shaft of the speed reducer and the prime mover, or a special clutch device is connected to the output shaft of the speed reducer, and the rotational power of the output shaft is transmitted to the drum through the clutch device. There are known ones that are designed to do so.

[0004]

However, in the case where the clutch device is provided between the speed reducer and the prime mover, since the resistance of the speed reducer itself is added to the drum when idling, a large operating force is required, In particular, when the reduction gear ratio becomes large, it becomes impossible for the human power to idle the drum. In addition, a device in which a special clutch device including a clutch plate and an actuator for urging the clutch plate is interposed between the speed reducer and the drum is used when the speed reducer is housed in the drum. There is a problem that the device also needs to be arranged in the drum, and the drum becomes unnecessarily large.

An object of the present invention is to eliminate all such problems.

[0006]

The present invention takes the following means in order to achieve such an object. That is, the rotation output device according to the present invention comprises a rotation output body having a hollow body shape, and a reduction gear housed in the rotation output body and provided with an output internal gear at the outermost periphery, A rotary output device configured to be able to transmit the power of a prime mover to the rotary output body via the speed reducer,
The internal gear is fitted to the inner periphery of the rotation output member so as to be rotatable and axially movable, and the internal gear is externally fitted to the outer periphery of the core member holding the reduction gear so as to be axially movable,
Using this core member and the internal gear, a hydraulic actuator for reciprocating the internal gear in the axial direction with respect to the rotary output body is constituted, and between the internal gear and the rotary output body. An engaging portion that is engaged and disengaged by the reciprocating motion of the internal gear is provided.

When the present invention is applied to, for example, a winch, the rotary output body corresponds to a drum, and when it is applied to a wheel drive device, the output rotary body is a wheel of a drive wheel. It will be equivalent.

[0008]

With such a structure, the rotational power of the prime mover is transmitted to the rotary output body through the speed reducer, and the rotary output body rotates at the reduced speed. The state can be interrupted by advancing and retracting the internal gear of the speed reducer in the axial direction by the hydraulic actuator to disengage the engaging portion. Then, when the engagement state of the engagement portion is released, the rotation output body is separated from the speed reducer and is allowed to idle.

In this device, the internal gear, the hydraulic actuator, and the engaging portion can perform a function equivalent to that of a conventional clutch device. Since it is one component of the speed reducer, and the hydraulic actuator is configured by using the internal gear and the core member that holds the speed reducer, compared to the case where a special clutch device is provided. Therefore, the number of parts can be significantly reduced. Therefore, the components for exerting the deceleration function and the clutch function can be housed in the rotation output body without difficulty, and the rotation output body can be prevented from being unduly increased in size.

[0010]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment in which the present invention is applied to a winch will be described below with reference to the drawings.

As shown in FIGS. 1 to 3, in this winch, a drum 2 which is a rotary output member is rotatably supported by a core member 1, and a differential planetary speed reducer 3 is housed in the drum 2. In other words, the power of the hydraulic motor 4 as a prime mover can be transmitted to the drum 2 via the differential planetary speed reducer 4.

The core member 1 has a base end portion 12 having a mounting flange 11, a shaft-shaped tip end portion 13, and a plurality of cylinders interposed between the tip end portion 13 and the base end portion 12. A body 14 and a bolt 15 which is inserted into the axial center portion of each of the cylindrical bodies 14 and fastens and fixes the tip end portion 13 to the base end portion 12 via the cylinder body 14, One end of the drum 2 is supported on the outer periphery of the base end portion 13 via a bearing 16, and the tip end portion 13 is also supported.
The other end of the drum 2 is supported via a bearing 17. The outer periphery of the base end portion 12 near the tip has a stepped shape including a small-diameter outer peripheral surface 12a, a large-diameter outer peripheral surface 12b, and a medium-diameter outer peripheral surface 12c.

The drum 2 is of a hollow cylindrical body having flange portions 21 at both ends, and a wire (not shown) can be wound around the outer periphery thereof.

The differential planetary speed reducer 3 is capable of rotating and moving axially in the large-diameter outer peripheral surface 12b and the medium-diameter outer peripheral surface 12c of the core member 1 with the axial center n aligned with the drum 2 and the core member 1. A cylindrical internal gear 31 that is externally fitted to the external gear, a pair of external gears 32 that are eccentrically arranged inside the internal gear 31, and a needle bearing 33 on the inner circumference of each external gear 32. Eccentric cams 34 respectively installed through
The input shaft 35 is rotatably disposed in the hollow center of the core member 1 so that the axis of the eccentric cam 34 is rotated by the input shaft 35. As a result, the external gear 32 becomes the internal gear 3
The eccentric rotation motion is performed along the inner circumference of the first unit. The number of external teeth 32a of the external gear 32 is equal to that of the internal gear 31.
Is set to be slightly smaller than the number of teeth of the internal gear 31a, and while the eccentric cam 34 makes one rotation and the external gear 32 makes one eccentric rotational movement, 31 and the external gear 32 are adapted to rotate by the difference in the number of teeth.
The both external gears 32 are set so as to perform eccentric rotation motion in a state where their phases are different from each other by 180 degrees.

Then, the core member 1 and the internal gear 3
1 to form the hydraulic actuator 5 for reciprocating the internal gear 31 with respect to the drum 2 in the axial direction. More specifically, the internal gear 31 has the internal teeth 31a only on the inner circumference on the tip side, and on the inner circumference on the base end side, as shown in FIG. A first inner peripheral surface 31b slidably fitted onto the medium diameter outer peripheral surface 12c and a second inner peripheral surface 12b slidably fitted onto the large diameter outer peripheral surface 12b of the core member 1.
The inner peripheral surface 31c is provided, and the hydraulic pressure introducing space 51 is formed between the second inner peripheral surface 31c of the internal gear 31 and the medium diameter outer peripheral surface 12c of the core member 1. A hydraulic pressure introducing port 52 formed in the core member 1 communicates with the hydraulic pressure introducing space 51. The hydraulic pressure introducing port 52 can be selectively connected to the hydraulic pressure source 54 or the tank 55 by a direction switching valve 53. On the other hand, the internal gear 31
End surface 31d provided on the outer periphery of the drum and the inner surface 18 of the drum 2
A compression coil spring 56 is interposed between the internal gear 31 and the internal gear 31.
Is urged in a direction in which the hydraulic pressure introducing space 51 is contracted, that is, in the left direction in the drawing. The hydraulic pressure introducing space is provided between the medium-diameter outer peripheral surface 12c and the first inner peripheral surface 31b and between the large-diameter outer peripheral surface 12b and the second inner peripheral surface 31c which are in sliding contact with each other. Sealing O-ring 57 for sealing 51
Is installed. A locking ring 58 for locking the internal gear 31 at the most advanced position is attached to the base end surface of the internal gear 31.

An engaging portion 6 which is engaged and disengaged between the internal gear 31 and the drum 2 by the reciprocating motion of the internal gear 31.
Is provided. Specifically, the engaging portion 6 is configured by the internal teeth 31a of the internal gear 31 and the external teeth 61a of the auxiliary gear 61 fixed to the inner surface 18 of the drum 2, and the external teeth 61a and the inner teeth 31a can be meshed with each other. At the required position of the internal gear 31, a tooth cutting portion 62 is formed by continuously cutting the internal teeth 31a in the circumferential direction, and the internal gear 31 is moved to the most advanced position shown in FIG. The outer teeth 61a of the auxiliary gear 61 are set so as to be located in the tooth cutting portion 62 in a state where the outer gear 61 is advanced to the position.

Next, the operation of this embodiment will be described.

When the direction switching valve 53 is set to the A position and the hydraulic pressure introducing space 51 is connected to the tank, the internal gear 31 is retracted by the urging force of the compression coil spring 56 as shown in FIG. The engaging portion 6 is pushed back to the position and the engaging portion 6 is maintained in the engaged state. That is, the external teeth 61a of the auxiliary gear 61 fixed to the drum 2 are meshed with the internal teeth 31a of the internal gear 31 of the differential planetary speed reducer 3, and the output of the speed reducer 3 can be transmitted to the drum 2. It has become. Therefore, when the hydraulic motor 4 is operated to rotate the input shaft 35 of the differential planetary speed reducer 3, the rotation is reduced by the speed reducer 3 and the output internal gear 31 starts decelerating rotation. As a result, the drum 2 is rotationally driven, and the wire (not shown) can be wound up or down.

On the other hand, when the direction switching valve 53 is switched to the B position and the hydraulic pressure introducing space 51 is connected to the hydraulic pressure source 54, high pressure hydraulic pressure is introduced into the hydraulic pressure introducing space 51, and the internal gear 31 is provided with the compression coil spring 56. It can be advanced to the most advanced position against the power. That is, when the pressure in the hydraulic pressure introducing space 51 rises, the hydraulic pressure acting on the stepped end face 31e of the internal gear 31 facing the hydraulic pressure introducing space 51 exceeds the biasing force of the compression coil spring 56, The internal gear 31 slides to the right in the figure. As a result, as shown in FIG.
The shape state of the engaging portion 6 is released, and the drum 2 becomes idle.

With such a structure, the speed reducer 3
It is possible to perform the same function as when a special clutch device is interposed between the drum 2 and the drum 2, but in this embodiment, the internal gear 31 that is a component of the speed reducer 3 is
Since it also serves as a clutch plate and a cylinder for driving the clutch plate, the number of parts can be significantly reduced as compared with the case where a special clutch device is provided.

The speed reducer is not limited to that shown in the illustrated embodiment. For example, a sun gear is arranged at the center of the internal gear and a plurality of sun gears are provided between the sun gear and the internal gear. The planetary gear speed reducer formed by interposing the planetary gears and the flexspline capable of elastic deformation on the inner circumference of the internal gear,
It may be a so-called harmonic speed reducer or the like in which a part of the flex spline is sequentially engaged with the internal teeth of the internal gear by an eccentric cam to operate.

Further, the structure of the hydraulic actuator is not limited to that of the above-described embodiment. For example, when the hydraulic pressure is deenergized, the engagement between the speed reducer and the rotation output body is released. The engaging portion may be in an engaged state when hydraulic pressure is introduced.

Furthermore, in the above-mentioned embodiment, the case where the present invention is applied to the winch has been described. However, the present invention stores the reduction gear in the wheel of the wheel, and the rotational power from the prime mover such as the engine is stored. Can be similarly applied to a wheel drive device or the like in which is transmitted to the wheels via the speed reducer. In that case, the wheel corresponds to a rotary output body having a hollow body shape.

Besides, various modifications can be made without departing from the spirit of the present invention.

[0025]

As described in detail above, since the present invention is designed to intermittently connect the power transmission state between the speed reducer and the rotary output body, it is possible to avoid the resistance due to the speed reducer. It is possible to idle the rotation output body lightly. Moreover, since the internal gear of the reducer also plays a role corresponding to the clutch plate and the cylinder for urging the clutch plate, the components can be reasonably and reliably compared with the case where a special clutch device is provided. Can be reduced to Therefore, even though the clutch function is provided between the rotation output body and the speed reducer housed inside, the rotation output body can be prevented from being unduly upsized.

[Brief description of drawings]

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

FIG. 2 is a partial cross-sectional view showing an enlarged part of a hydraulic actuator of the same embodiment.

3 is a cross-sectional view taken along the line I-I in FIG.

FIG. 4 is an operation explanatory view of the same embodiment.

[Explanation of symbols]

 1 ... Core member 2 ... Rotation output body (drum) 3 ... Reduction gear (differential planetary reduction gear) 4 ... Motor (hydraulic motor) 5 ... Hydraulic actuator 6 ... Engagement portion 31 ... Internal gear

Claims (1)

[Claims] 1. A rotary output body having a hollow body and a speed reducer housed in the rotary output body and provided with an output internal gear at the outermost periphery thereof. The power of the prime mover is supplied to the speed reducer. A rotary output device configured to be transmitted to the rotary output body via a rotary output device, wherein the internal gear is fitted to the inner periphery of the rotary output body so as to be rotatable and axially movable, and A gear is externally fitted to the outer periphery of a core member holding a reduction gear so as to be movable in the axial direction, and the internal gear is reciprocated in the axial direction with respect to a rotation output body by using the core member and the internal gear. A rotary output device comprising a hydraulic actuator for causing the internal gear and an output part provided between the internal gear and the rotary output body to be engaged and disengaged by the reciprocating motion of the internal gear.