JP2000166301A - Power transmission system for walking type working machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a driving transmission gear for walking type working machine enabling a slow start in high speed position as well as in low speed position preventing sudden acceleration in starting time in high speed position that is existing in conventional walking type implement comprising a gear mechanism accompanying anxiety on sudden acceleration. SOLUTION: A differential gear 2b is installed in the driving transmission gear 2 of a walking type working machine comprising a gear mechanism on a transmission path from an input shaft to a final shaft, one of the output shaft of the differential gear 2b is set as a driving shaft and the other shaft is set as a control shaft, a loading device 2e is installed on the control shaft and prevents the sudden acceleration by relieving sudden driving of the output shaft in the cooperation with the differential gear 2b.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a walking type working machine having a traveling transmission comprising a gear mechanism, and more particularly to a traveling transmission incorporating a differential.

[0002]

2. Description of the Related Art There are many known walking type working machines which transmit power from a prime mover to a traveling device via a traveling transmission device including a gear mechanism. This causes a sudden start phenomenon that is likely to occur at the start of high-speed traveling, and this sudden start phenomenon gives the driver a sense of danger and anxiety, and involves inconvenience and inconvenience in operation.

[0003]

SUMMARY OF THE INVENTION In a walking type working machine having a traveling transmission device composed of a gear mechanism, an apparatus having a configuration in which a sudden start phenomenon is prevented even at the time of high-speed running start is used. In the device.

[0004]

SUMMARY OF THE INVENTION In a walking type work machine having a traveling transmission device including a gear mechanism, a differential device is incorporated in a transmission path from an input shaft of the traveling transmission device to a final shaft portion, and a differential gear is provided. The driving force input for the operation is not applied to the traveling output shaft instantaneously while passing through the gear train, so that the sudden start phenomenon is suppressed.

In a walk-behind type working machine having a traveling transmission device including a gear mechanism, a differential device is incorporated in a transmission path from an input shaft of the traveling transmission device to a final shaft portion, and a two-way differential of the differential device is provided. One of the output side is a traveling output shaft and the other is a control axis, the differential effect is enlarged by braking the rotation speed of the control shaft, and the input driving force is related to the rotation speed of the control shaft. By transmitting the power to the traveling output shaft, the speed is gradually increased from the slow start even at the high speed stage.

In a walk-behind work machine having a traveling transmission device including a gear mechanism, a differential device is incorporated in a transmission path from an input shaft of the traveling transmission device to a final shaft portion, and a two-way device included in the differential device is provided. One of the output sides is a traveling output shaft and the other is a control axis, and a load device that generates a load according to the rotational speed is attached to the control axis, and the input driving force is instantaneously input by a differential action. The control shaft with a light load is applied, and the driving force is transmitted to the traveling output shaft in accordance with the load on the control shaft, thereby alleviating sudden start.

In a walk-behind working machine having a traveling transmission device composed of a gear mechanism, a differential device is incorporated in the traveling transmission device, and a load is generated on a control shaft mounted on the differential device in accordance with the rotational speed. A load device is mounted, and the load is gradually increased until the load device reaches a predetermined rotation speed, and when the load device exceeds the predetermined rotation speed, a maximum load is generated. The rotation speed is controlled so that the input driving force is not applied instantaneously and collectively to the traveling output shaft.

In a walking type working machine having a traveling transmission device comprising a gear mechanism, a differential device is built in the traveling transmission device, and a centrifugal force brake is mounted on a control shaft mounted on the differential device as a load device. Attach the key and set the differential and centrifugal force
The maximum load is generated at a speed equal to or higher than a predetermined rotation speed, and conversely, the braking force is released by reducing the load as the input rotation speed decreases, thereby canceling the braking force. The rotation speed of the traveling output shaft is controlled according to the rotation speed of the control shaft.

[0009]

DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a diagram of a transmission mechanism of a traveling transmission according to a main part of the present invention. FIG. 2 is a front view of an embodiment as a load device according to the main part of the present invention, and FIG. 3 is a side sectional view of the embodiment as a load device according to the main part of the present invention. FIG. 4 is an overall side view of the cutting and binding machine according to the embodiment of the present invention. FIG. 5 is an overall rear view of the cutting and binding machine according to the embodiment of the present invention. FIG. 6 is an overall plan view of a mowing and binding machine according to an embodiment of the present invention. FIG. 7 is a side view of a traveling clutch operating unit of the reaper and tying machine according to the embodiment of the present invention, and FIG.

First, an overall configuration of a mowing and binding machine as an embodiment according to the present invention will be described with reference to FIGS.
A mowing part (9) is continuously provided at the front of the traveling device (1) equipped with the traveling wheel (1a), and the mowing part (9) is a pair of raising devices (4) arranged side by side on the front surface. (4) a cutting blade device (5) installed on both left and right pipes of the cutting frame (11) below the rear part of the raising devices (4) and (4); and the cutting blade device (5). The cut stalks are transported backward and tied to a tying device (1
0), a bundling device (10) for bundling the cereal stems inherited from the lower carriages (7) and (7), and discharging the culm from the back, and a bundling device (7). 10) A pair of upper transporters (6) and (6) for nipping and transporting the united grain culm released from 10) and the upper transporters (6) and (6)
The main component is a horizontal transporter (8) that transports and releases the bound grain culms conveyed by the machine to the side of the machine, and these component components are integrally connected via a cutting frame (11). I have.

[0011] A pair of raising devices (4) (4), which are located on the front surface of the mowing part (9) and are arranged side by side on the left and right, are provided with a chain with a raising tine attached to a cultivated cereal stem, regardless of whether or not it falls. The stalk posture is adjusted while raising by the orbiting action upward, and the cutting blade device (5) is attached backward and inclined so as to assist the cutting action.

The upper transport bodies (6) and (6) have a pair of elastic transport endless belts disposed symmetrically to the left and right. Each of the upper transport bodies (6) and (6) wraps in a substantially triangular shape in plan view. The binding device (10) with the front end wider than the rear end in a letter shape
It is configured to make it easier to take in the united cereals released by the above, and at the same time, to prevent the turbulence of the united culm, to adjust the posture of the united cereal, and to make the transfer to the horizontal conveyor (8) smooth. Carriers (7) and (7) are also composed of chains with tines, which are also arranged in a pair on the left and right. The front end is wider than the rear end in a substantially figure-eight shape, and cut by the cutting blade device (5). The lower part of the culm is trimmed and forcibly sent to the binding device (10) to assist the smooth operation of the binding device (10). The fed cereal stems are bound by the binding device (10) and released by the release arm (1).
It is discharged to the rear through 4), and the upper carrier (6) (6)
And is conveyed backward, and is inherited by the horizontal conveyance body (8).

On the other hand, one side of the upper transport body (6) stretched in a substantially triangular form is a transport section to the lateral side, and the horizontal transport body (8) is located at a relative position which is substantially the same height as the transport section. The united grain culms conveyed from the upper carrier (6) are confronted and arranged side by side, and are transported to the lateral side of the machine and released by the cooperation of the horizontal carrier (8) and the upper carrier (6). .

As shown in FIGS. 4 to 6, the main body of the body directly connects the engine (18) and the traveling transmission (2), and is connected to the traveling output shaft (2c) of the traveling transmission (2). An axle case (1b) is additionally provided, and the axle case (1b)
Is arranged below the engine (18), that is, on the center line of the fuselage, so that the left-right balance is harmonized, and the traveling wheels (1a) are extended via the traveling axle extending left and right equally from the axle case (1b). Is driven.

Here, the main parts of the present invention are shown in FIGS.
It will be described in detail with reference to FIG. A differential (2b) is mounted on the final shaft (2f) of the traveling transmission (2), and the differential (2
b) has one of the two output sides on the traveling output shaft (2).
c) and the other as the control axis (2d),
A centrifugal brake (3) is mounted on the d) as a load device (2e), and a load is generated in accordance with the rotation speed of the control shaft (2d). The control shaft (2d) is configured to be braked.

[0016] From the engine (18) to the traveling transmission (2)
Is transmitted to the control shaft (2d) with a small load instantaneously in the initial stage, and when a load is generated according to the rotation speed of the control shaft (2d), the driving force is transmitted to the traveling output shaft (2c) side. When the transmission of the driving force is accelerated and the control shaft (2d) exceeds the predetermined rotational speed and is braked by the centrifugal brake (3) attached to the shaft, the driving force is increased by the differential device (2b). The whole is transmitted to the traveling output shaft (2c).

As described above, the differential effect is enlarged by the cooperation of the centrifugal brake (3), which is the load device (2e), and the differential device (2b), and the input driving force is controlled by the control shaft (2d). ), The transmission is transmitted to the traveling output shaft (2c) to gradually increase the speed from a slow start even in a high-speed stage. ) Is applied with a driving force, and when the load on the control shaft (2d) increases with the rotation speed, the driving force is transmitted to the traveling output shaft (2c) to prevent sudden start.

That is, by using the centrifugal brake (3) as the load device (2e), the load increases up to a predetermined rotation speed, but when the rotation speed exceeds the predetermined rotation speed and reaches the maximum load, the control shaft (2d) is used. ), The rotation of the traveling output shaft (2c) is increased by the action of the differential action so that the input driving force is not instantaneously applied to the traveling axle at once. Devised.

A centrifugal brake (3) as an embodiment of the load device (2e) in the present invention will be described. As shown in FIGS. 2 and 3, the centrifugal brake (3) has an outer brake flange (3).
a), inner brake flange (3b) and swing lever (3)
On the basis of d), a swing arm (3c) which swings by centrifugal force is divided into three equal parts on the outer peripheral portion of the inner brake flange (3b) and pivotally connected, and this swing arm (3c) is attached. A swing lever (3d) is pivotally connected via the swing lever (3d), and the swing lever (3d) is pushed up to the swing arm (3c) with the swing fulcrum (3e) as a base point as the control shaft (2d) rotates. It is configured such that its tip projects and expands in the outer peripheral direction.

Further, the boss portions of the outer brake flange (3a) and the inner brake flange (3b) are fitted and engaged by a spiral spring (3f) wound around the boss portion.
There is a lock ring (3h) fitted concentrically to the boss of the outer brake flange (3a) on the outer peripheral side of the inner brake flange (3b). The lock ring (3h) is a lock spiral spring (3). 3k) through the outer brake flange (3
a) and the inner brake flange (3b). The lock ring (3h) is formed in a cylindrical shape having a bottom, a mounting boss is provided on the bottom, and a lock claw is projected at three equally spaced positions on the peripheral edge of the cylinder, and the lock claw is an inner brake flange (3b). The swing arm (3c) is located at a position relative to the pivotal arm of the swing arm (3c) protruding at three places on the outer periphery of the swing arm (3c).
It is assembled to follow and rotate.

Accordingly, when the swing arm (3c) is in the overhanging braking state with the rotation of the control shaft (2d), the lock ring (3) that tunes and follows the swing arm (3c) and rotates.
In (h), the lock claw is brought into contact with the swing arm (3c), and the swing arm (3c) is pressed and locked by the rotational force to maintain the braking state. On the other hand, when the driving force of the control shaft (2d) is cut and the rotational force is lost, the inner brake flange (3b) and the lock ring (3h) are returned by the spring force of the spiral spring (3e) and the lock spiral spring (3k). The swing arm (3c) is returned to its original position by sliding in the direction, and the braking state is released. The outer brake flange (3a) is axially attached to the control shaft (2d) via a key, and the inner brake flange (3b) and the lock ring (3h) fitted to the boss portion together with the control shaft (2d). It is constituted so that it may rotate integrally.

That is, with the rotation of the control shaft (2d), the inner brake flange (3) is moved through the outer brake flange (3a).
When b) rotates and the centrifugal force increases as the rotation speed increases, the centrifugal force causes the swing arm (3c) to rise, and the swing lever (3d) moves to the swing fulcrum (3e). The frictional surface (a), (b), and (c) at the tip of the swing lever (3d) is pressed against the braking body (3g) to generate a braking force. At this time, the friction surfaces (a), (b), and (c) differ in position from the respective fulcrum (3e), and the friction surfaces are sequentially added from (a) to (c) as the rotation speed increases. The locking ring (3h) presses and locks the oscillating arm (3c) standing up to maintain the braking state at a predetermined rotation speed or higher. Also, when the driving force is cut and the rotational force is lost, the friction surface (a)
(B) and (c) are separated from the braking body (3g) to eliminate the braking force.

On the other hand, the traveling clutch operating section (30) is shown in FIG.
As shown in FIG. 8, a clutch cam (32) and a guide fitting (33) are formed integrally with the traveling clutch lever (31).
The clutch cam (32) has a pair of upper fulcrums (A) and lower fulcrums (B) fixed to a pair of left and right sides on a clutch cam body (32a) having a U-shaped cross section. 32b) is fixed to the inside of a U-shape by a bridge.

When the traveling clutch lever (31) is operated in forward and backward clutch operation, an integral clutch cam (3) is formed.
2) is integrated with the clutch lever (31) using a pair of left and right upper fulcrums (A) or lower fulcrums (B) inserted into an arc-shaped lead hole drilled in the guide fitting (33) as rotation fulcrums. To rotate. At this time, when the clutch lever (31) is pushed forward, the upper fulcrum (A) becomes a pivot, and when it is pulled backward, the lower fulcrum (B) becomes a pivot. The rotation fulcrum shifts between the upper fulcrum (A) and the lower fulcrum (B) depending on the front-rear operation direction of the clutch lever (31). A coil spring (32c) is attached to the clutch cam (32) via the spring hook (32b).
c) The operation of the traveling clutch lever (31), which exceeds the upper fulcrum (A) when moving forward and the lower fulcrum (B) when moving backward to stabilize the operating position of the traveling clutch lever (31). I have.

A brake lever (34) attached to the traveling clutch lever (31) is pivotally attached to a brake lever fulcrum (C) fixed to the outer wall of the clutch cam body (32a). However, the tip of the brake lever (34) is attached to one end of a brake tip lever (35), which is disposed so as to rotate separately at the tip lever fulcrum (D). Lever
It is in contact with a brake return spring (36) mounted on (35). Further, the other end of the brake lever (35) comes into contact with the brake return pin (37) abutting on the lower end of the clutch cam body (32a) during the reverse operation of the traveling clutch lever (31). , The brake is released.

A brake lever projection (38) is fixedly mounted on the brake lever (34), and when the traveling clutch lever (31) is operated forward, the brake lever projection (3) is provided.
8) comes into contact with the traveling clutch lever (31), and when the braking lever (34) is pulled, the traveling clutch lever (31) is automatically returned to the neutral position by the braking lever projection (38). At the same time, the brakes work.
Conversely, when the traveling clutch lever (31) is operated forward, the brake lever projection (38) is pushed to release the brake. Therefore, the brake is automatically released in any of the clutch connection operations in the forward and backward directions. When the brake is activated, the traveling clutch lever (31) is configured to automatically return to the neutral position in any of the forward and backward directions, so that the clutch operation and the brake operation are easily performed in conjunction with each other. I have.

The operation of the traveling clutch operating section (30) configured as described above is as follows. Travel clutch lever
When (31) is tilted forward, the upper fulcrum (A) becomes the fulcrum, the clutch cam (32) rotates, the coil spring (32c) moves over the fulcrum, the clutch wire is loosened and the clutch is connected to the forward movement. When the traveling clutch lever (31) is pulled rearward, the lower fulcrum (B) becomes the fulcrum, the clutch cam (32) rotates in the direction opposite to that in the forward movement, and the coil spring (32c) moves over the fulcrum to engage the clutch. The clutch is connected to the reverse by pulling the wire. In any case, the attached brake lever
When (34) is activated, the traveling clutch lever (31) is interlocked via the brake lever projection (38) or the brake return pin (37) fixed to the brake lever (34). To return to the neutral position.

In the prior art, a configuration in which the clutch wire is pushed / pulled to connect / disconnect the traveling clutch for forward / backward traveling is disclosed as a known one, but one end of the clutch wire is connected to the traveling clutch via a return spring. It is generally connected to. In this case, in the position where the clutch wire is pushed or pulled against the return spring in the process of the intermittent operation, the operation load becomes high and the clutch operation becomes heavy, but in the traveling clutch mechanism such as the embodiment by the above configuration, ,
Forward and backward clutch operation can be performed with a single clutch wire, and the clutch operation force can be reduced even if the operation load increases at a position against the return spring formed by a tension coil spring.

That is, in the above configuration, when the traveling clutch lever (31) is tilted forward and the clutch is connected forward, the coil spring (32c) exceeds the fulcrum with the upper fulcrum (A) as the fulcrum, and pushes the clutch wire. Therefore, the direction of pushing back is also applied to the return spring composed of the extension coil spring connected to the traveling clutch, and the spring force of the return spring is also applied,
The clutch operating force is light. Conversely, the traveling clutch lever
When the clutch (31) is pulled rearward and the clutch is connected to the reverse, the coil spring (32c) goes over the fulcrum with the lower fulcrum (B) as the fulcrum. Since the fulcrum moves to the fulcrum (B), the length of the fulcrum and the force applied to the traveling clutch lever (31) becomes longer, and the clutch operating force is reduced. In this way, the fulcrum of the traveling clutch lever (31) is shifted between the upper fulcrum (A) and the lower fulcrum (B) with respect to the forward / rearward operation direction of the traveling clutch lever (31), so that it can be moved forward and backward. A traveling clutch operating section (30) characterized in that it is configured to reduce any forward operating force.

[0030]

The present invention is embodied in the form described above and has the following effects.

In a walking type working machine having a traveling transmission (2) composed of a gear mechanism, a differential gear is provided in a transmission path from an input shaft (2a) to a final shaft portion (2f) of the traveling transmission (2). (2b) is incorporated so that the driving force input by the differential action is not instantaneously applied to the traveling axle via the gear train instantaneously, thereby suppressing the sudden start phenomenon. In any shift position, it is possible to prevent instantaneous sudden start during the operation of connecting the traveling clutch, and it is possible to safely and easily operate.

In a walking type work machine having a traveling transmission (2) comprising a gear mechanism, a differential gear is provided in a transmission path from an input shaft (2a) of the traveling transmission (2) to a final shaft portion (2f). (2b), one of the two output sides of the differential device (2b) is a traveling output shaft (2c) and the other is a control shaft (2d), and the rotational speed of the control shaft (2d) is By increasing the differential effect by braking, the input driving force is transmitted to the traveling axle in relation to the rotation speed of the control shaft (2d), so that the speed gradually increases from a slow start even at a high speed stage. With this configuration, it is possible to avoid sudden start and enable safe operability and easy operability even at the time of clutch connection operation from the high speed stage as well as at the low speed stage.

In a walking type work machine having a traveling transmission (2) comprising a gear mechanism, a differential gear is provided in a transmission path from an input shaft (2a) of the traveling transmission (2) to a final shaft portion (2f). (2b), one of the two output sides of the differential device (2b) is a traveling output shaft (2c) and the other is a control shaft (2d), and the control shaft (2d) has a rotational speed. A load device (2e) that generates a load is attached with
The input driving force is applied to the control shaft (2d) with a small load instantaneously at the beginning of the input by the differential action, and when the load on the control shaft (2d) increases with the rotation speed, the traveling output shaft (2d)
Since the driving force is transmitted to the traveling axle via c), the differential effect is enlarged by the rotation speed of the control shaft (2d), and the sudden start can be more reliably prevented.

In a walking type working machine having a traveling transmission (2) composed of a gear mechanism, a differential (2b) is built in the traveling transmission (2) and mounted on the differential (2b). A load device (2e) that generates a load in accordance with the rotation speed is mounted on the control shaft (2d), and the load device (2e) gradually increases the load up to a predetermined rotation speed, and when the load device exceeds the predetermined rotation speed. The maximum load is generated, the rotation of the control shaft (2d) that is supported is braked, and the rotation speed of the traveling output shaft (2c) is gradually increased in cooperation with the differential device (2b). As a result, the driving force input to the traveling axle is not applied instantaneously and collectively, so that the rapid transmission of the driving force can be alleviated and sudden start can be prevented, making the driving operability easy and safe. It can be.

In a walking type working machine having a traveling transmission (2) composed of a gear mechanism, a differential (2b) is built in the traveling transmission (2) and mounted on the differential (2b). A centrifugal brake (3) is mounted on the control shaft (2d) as a load device (2e), and the output is controlled by combining the differential device (2b) and the centrifugal brake (3). Therefore, since the load is generated in accordance with the rotational speed of the control shaft (2d), the driving force input by the differential action initially flows to the control shaft (2d) side, and the control shaft (2d) 2
When a braking force is generated by the centrifugal brake (3) attached to d), the driving force is transmitted to the traveling output shaft (2c),
By the synergistic effect of the differential device (2b) and the centrifugal brake (3), it is possible to avoid a sudden start operation of the traveling device.

[Brief description of the drawings]

FIG. 1 is a transmission mechanism diagram of a traveling transmission device according to a main part of the present invention.

FIG. 2 is a front view of an embodiment as a load device according to a main part of the present invention.

FIG. 3 is a sectional view of an embodiment as a load device according to a main part of the present invention.

FIG. 4 is an overall side view of a cutting and binding machine according to an embodiment of the present invention.

FIG. 5 is an overall rear view of the cutting and binding machine according to the embodiment of the present invention.

FIG. 6 is an overall plan view of a cutting and binding machine according to an embodiment of the present invention.

FIG. 7 is a side view of a traveling clutch operating unit of the mowing and binding machine according to the embodiment of the present invention.

FIG. 8 is a cross-sectional view of a traveling clutch operating unit of the mowing and binding machine according to the embodiment of the present invention.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Traveling device 1a Running wheel 1b Axle case 2 Traveling transmission device 2b Differential device 2e Loading device 3 Centrifugal force brake 3a Outer brake flange 3b Inner brake flange 3c Swing arm 3d Swing lever 3h Lock Ring 4 Raising device 9 Cutting unit 10 Binding device 18 Engine 30 Traveling clutch operating unit 31 Traveling clutch lever 32 Clutch cam 34 Braking lever 35 Braking lever 38 Braking lever projection A Upper fulcrum B Lower fulcrum

Claims (5)

[Claims] 1. A walk-behind working machine having a traveling transmission (2) comprising a gear mechanism, wherein a difference in a transmission path from an input shaft (2a) of the traveling transmission (2) to a final shaft portion (2f) is provided. A traveling transmission device for a walk-behind working machine, wherein the traveling device (2b) is incorporated. 2. A walk-behind working machine having a traveling transmission (2) comprising a gear mechanism, wherein a difference in a transmission path from an input shaft (2a) of the traveling transmission (2) to a final shaft portion (2f) is provided. A driving device (2b), and one of two output sides of the differential device (2b) is a traveling output shaft (2c);
A traveling transmission device for a walking type working machine, characterized in that the other is a control shaft (2d). 3. A walk-behind working machine having a traveling transmission (2) comprising a gear mechanism, wherein a difference in a transmission path from an input shaft (2a) of the traveling transmission (2) to a final shaft portion (2f) is provided. A driving device (2b), and one of two output sides of the differential device (2b) is a traveling output shaft (2c);
A traveling transmission device for a walk-behind type working machine, characterized in that the other is a control shaft (2d), and a load device (2e) for generating a load according to a rotation speed is mounted on the control shaft (2d). 4. A walking type working machine having a traveling transmission (2) composed of a gear mechanism, wherein the traveling transmission (2) has a differential (2b) built therein, and the differential (2b) A load device (2e) that generates a load according to the rotation speed is mounted on the mounted control shaft (2d), and the load is gradually increased until the load device (2e) reaches a predetermined rotation speed. , The maximum load is generated and the control axis (2d)
The traveling transmission device for a walking-type working machine according to claim 3, wherein the rotational speed of the traveling output shaft (2c) is controlled by a differential action by braking. 5. A walking type work machine having a traveling transmission (2) comprising a gear mechanism, wherein the traveling transmission (2) has a differential (2b) built therein, and the differential (2b) has A centrifugal brake (3) is mounted as a load device (2e) on the installed control shaft (2d), and output control is performed by combining the differential device (2b) and the centrifugal brake (3). The traveling transmission device for a walking-type working machine according to claim 4, wherein: