JP2971890B2 - Transmission mechanism in crawler traveling device - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to a speed change mechanism in a crawler traveling device.

<Prior Art> The steering operation in the crawler traveling device is performed by setting the crawler traveling body in a driving state, a clutch disengaged state, and a braking state, for example, by stopping one of the left and right crawler traveling bodies and performing a spin turn. How to decide
Method 2 in which the driving of the clara traveling body is disengaged by the side clutch, and free rotation on the side where the side clutch is disengaged and gently turning by driving the crawler traveling body on the opposite side.
There were street turning methods.

<Problems to be Solved by the Invention> However, in the above-described conventional traveling apparatus, there are only two methods of turning, and there is a disadvantage that it is difficult to turn in an arbitrary direction according to the condition of the road surface.

Also, when making a turn, the crawler has the disadvantage that the crawler cuts the road surface and roughens the road, and when the aircraft sinks on a soft ground, it performs inching operation to engage and disengage the clutch and gradually moves the crawler traveling body. There was a problem that it was necessary to rotate to escape. It is particularly desired that these problems be solved for mobile agricultural machines traveling on farmland.

<Means for Solving the Problems> The present invention for solving the above-described problems is directed to a transmission 13 that outputs power from a prime mover to the left and right crawler traveling bodies 3 separately. Left and right output shaft 5
Side clutches 46 and 47 for turning on and off the transmission to the transmissions 5 and 56 are provided on the input side of output shafts 55 and 56 provided separately on the left and right, and the clutch shaft 44 of the side clutches 46 and 47 is provided.
A transmission 67 is provided on the output side for transmitting power for slow rotation to the output shaft on the off side of the side clutches 46, 47 by obtaining power from the clutch shaft 44. Single intermediate shaft that transmits slow rotation to the output shaft
51, and one friction clutch 65 for transmitting the slow rotation to the intermediate shaft 51.

<Operation> The power output from the transmission 13 to the output shafts 55 and 56 is connected and disconnected by the left and right side clutches 46 and 47. When turning, the side clutch 46 (or 47) in the turning direction
Is turned off. In the case of gentle turning, a transmission 67 for gentle turning further acts to make the output shaft of the side clutch 46 disengaged.
Since the slow rotation is given to the 55, the crawler traveling body on the turning direction side becomes slow, and the aircraft can turn slowly.

An example of the present invention will be described below with reference to the drawings.

FIG. 2 is an overall perspective view of the combine. The combine main body 1 is mounted on the left and right crawler traveling bodies 3, has a driver's seat 4 and an operation panel 5 on the front right side, and a reaping machine 7 is provided at a front end portion so as to be able to move up and down.

FIG. 1 is a sectional view showing an internal mechanism of the counter device 11 and the transmission 13 of the combine main body 1.

A counter input shaft 15 for inputting power from the prime mover protrudes from the counter device 11, and a counter input pulley 17 is attached to a tip of the shaft, and power is transmitted by a belt. A main clutch 16 is provided between the counter input pulley 17 and the counter input shaft 15, so that an input from the prime mover can be turned on and off.

Two output shafts protrude from the counter device 11. Power is transmitted to each output shaft via several stages of gears while being shifted. A stepless output pulley 21 is attached to the counter output shaft 19. The width of the output pulley 21 is adjusted by an adjusting device also provided on the counter output shaft 19, and the transmission speed is adjusted steplessly. twenty three
Is a cam lever for operating the adjusting device by hydraulic pressure. On the side opposite to the side where the counter output shaft 19 protrudes, a constant speed output shaft 25 protrudes, and a constant speed output pulley 36 is fixed. The stepless output pulley 21 and the constant speed output pulley 36 rotate in mutually opposite directions.

Next, the internal mechanism of the transmission 13 will be described. transmission
A speed change input shaft 27 and a constant speed input shaft 28 protrude left and right on the 13 counter device 11 side. A differential gear device 31 provided inside the transmission 13 is provided at a portion where both input shafts 27 and 28 abut.

On the other hand, a continuously variable input pulley 29 and a constant speed input pulley 30 are attached to protruding ends of the speed change input shaft 27 and the constant speed input shaft 28, and rotational forces in opposite directions are transmitted via a transmission belt. A cutting output shaft 38 is inserted and supported adjacent to the differential gear device 31, and a switching device 34 is provided on the cutting output shaft 38. Switching device 34 is a reaping output shaft
High-speed gear 33 and low-speed gear 35 rotatably mounted on 38
Further, the switching gear 37 is configured to rotate integrally with the cutting output shaft 38 and to be slidable in the axial direction. A cutting output pulley 39 is attached to a protruding end of the cutting output shaft 38, and transmits torque to a drive system of the cutting machine 7. Therefore, the cutting drive speed of the cutting unit transport unit 7a changes according to the change in the number of rotations of the cutting output shaft 38.

The high-speed gear 33 is a gear 32 fixed to the speed change input shaft 27.
, And the low-speed gear 35 meshes with a cutting output gear 31b provided outside the differential gear device 31. Switching gear 37
Slides along the cutting output shaft 38 to
It meshes with the internal teeth of either 33 or the low-speed gear 35, and outputs the high-speed rotation or the low-speed rotation from the cutting output shaft 38. Since the low-speed gear 35 has a smaller diameter than the high-speed gear 33, the rate of increase in the number of rotations with respect to the number of rotations of the cutting output gear 31b is greater than that in the high-speed gear 33. Therefore, in low-speed running, the mowing drive speed is lower in the case of meshing with the low-speed gear 35 than in the case of meshing with the high-speed gear 33, but in high-speed running, the mowing drive speed is lower in the case of meshing with the high-speed gear 33. Become.

 Next, the traveling transmission system will be described.

From the differential gear device 31, a traveling output 31 formed on the outer periphery is provided.
The rotational force is transmitted to the forward / reverse switching device 41 by a. Rotational force is transmitted from the forward / reverse switching device 41 to the drive gear 45 of the clutch shaft 44 via the back shaft 42 or the transmission shaft 43. Drive gear provided at the center of the clutch shaft 44
Left side clutch 46 and right side clutch 47 on both sides of 45
Is externally slidably and rotatably fitted independently of the clutch shaft 44, and a pinion that meshes with the internal gear of the drive gear 45 is formed on the outer periphery. And both side clutches
46 and 47 are always urged toward the drive gear 45 by a spring and mesh with each other, and the side clutch cylinders 76 and 7 are
By the operation of 7, the engagement with the drive gear 45 is released. Further, an output gear 48 for turning traveling is fixed to one end of the clutch shaft 44 so as to be able to rotate integrally therewith, and meshes with a free gear 63 described later.

The intermediate shaft 51 adjacent to the clutch shaft 44 has transmission gears 53, 54 meshing with the side clutches 46, 47, respectively.
Are rotatably fitted to the outside. Therefore, the intermediate shaft 51 and the transmission gears 53 and 54 can rotate independently.
The transmission gears 53 and 54 are composed of large-diameter and small-diameter gears,
The large-diameter gear meshes with the side clutches 46,47.

The small-diameter gears of the transmission gears 53, 54 mesh with output gears 57, 58 fixed to output shafts 55, 56 projecting from both sides of the transmission 13, and the rotation of the output gears 57, 58 causes the left and right crawler traveling bodies 3 to rotate. The driving force is output. A traveling wheel 60 composed of a driving sprocket is attached to the distal ends of the output shafts 55 and 56, and the crawler belt is driven by the rotation of the traveling wheel 60.

During normal straight running, the left and right side clutches 46, 47
, And power is transmitted independently to the left and right output shafts 55 and 56. At this time, the intermediate shaft 51 is rotating freely.

 The gentle turning transmission system will be described.

A transmission 61 for traveling wheel transmission is provided between the output shafts 55 and 56, and the transmission 61 for traveling wheel transmission comprises a differential gear device 59 in the mechanism of the present embodiment.

On the other hand, a free gear 63 is rotatably fitted to one end of the intermediate shaft 51, and a friction clutch 65 is provided between the intermediate shaft 51 and the free gear 63. The friction clutch 65 is in the off state during normal straight running, and the rotational force transmitted from the turning traveling output gear 48 to the free gear 63 is not normally transmitted to the intermediate shaft 51. The friction clutch 65 is a slow turning operation cylinder 66
Is turned on and off.

A gear 51a that rotates integrally with the intermediate shaft 51 is formed.
1a is a swing drive input gear 59a provided in the differential gear device 59.
And are engaged. Therefore, in the straight traveling state, the differential gear device 59 rotates in the same direction as the output shafts 55 and 56, and the intermediate shaft 51 also rotates via the turning drive input gears 59a and 51a.

Here, the turning traveling output gear 48, the intermediate shaft 51, the free gear
The slow turning transmission 67 is constituted by the friction clutch 63 and the friction clutch 65.

The slow turning transmission system includes a slow turning transmission 67 and a traveling wheel transmission transmission 61, that is, in the mechanism of the present embodiment, the turning traveling output gear 48, the free gear 63, the friction clutch 65, the intermediate shaft 51, Gear 51a, swing drive input gear 59a, and differential gear device 59
Composed of

For example, when turning slowly to the left, the left side clutch 46 is set to the off state, and the friction clutch 65 is set to the on state. As a result, the output shaft 55 has no input to the output gear 57, and the rotational force transmitted to the intermediate shaft 51 via the friction clutch 65 is input to the differential gear device 59, and the output shaft 55 The torque is output to 55. If the operating pressure of the friction clutch 65 is gradually released, the rotational force transmitted to the intermediate shaft 51 decreases depending on the degree of friction of the friction clutch 65,
Accordingly, the rotation speed of the output shaft 55 also decreases. Therefore, a difference in the number of revolutions is generated between the right crawler traveling body and the left crawler traveling body, and the aircraft body moves while gently turning leftward with a small number of revolutions.

When the vehicle turns slowly to the right, the right side clutch 47 may be disengaged, and the same operation may be performed on the friction clutch 65.

Next, a description will be given of a power transmission system for turning a super-site, in which the left and right crawler traveling bodies 3 are driven in opposite directions to perform a super-site turning in a fixed position. The intermediate shaft 51 is provided with a brake 71 at the end opposite to the mounting end of the friction clutch 65, and the brake 71 is a super pivot turning cylinder.
Operated by 72. Intermediate shaft by operation of brake 71
51 is fixed and rotation stops.

The brake 71 and the intermediate shaft 51 constitute a transmission pivot transmission 69. The power transmission system for turning the ground is composed of a transmission 69 for turning the ground and a transmission 61 for transmitting the running wheels. In the mechanism of this embodiment, the brake 71, the intermediate shaft 51, and the gear 51 are provided.
a, a turning drive input gear 59a and a differential gear device 59.

For example, in the case of a super-revolution turn in a counterclockwise direction, the left side clutch 46 is disengaged, and the brake 71 is operated.
The rotation of the intermediate shaft 51 stops, and the rotation of the turning drive input gear 59a stops. Due to the operation of the differential gear device 59, a rotational force in a direction opposite to that of the output shaft 56 is applied to the output shaft 55 in the free state, and the output shaft 55 rotates at the same rotational speed as the output shaft 56.

In the case of a clockwise turn, the left side clutch 47 may be disengaged and the brake 71 may be operated in the same manner.

Next, operation mechanisms of the friction clutch 65, the brake 71, and the side clutches 46, 47 will be described.

FIG. 3 is a hydraulic circuit diagram of a combine using the present embodiment. The gentle turning operation cylinder 66 and the super pivot turning operation cylinder 72 are single-acting cylinders, and are constantly urged in the contracting direction. Slow turning operation cylinder 66 and super pivot turning operation cylinder 72
Is connected to a single three-position four-way switching solenoid valve 73, and a circuit is connected such that hydraulic pressure always acts on only one of them. Further, electrically controlled variable relief valves 74 and 75 are connected to the respective cylinders 66 and 72 to control the pressure applied to the cylinders 66 and 72. Here, the variable relief valve 74 connected to the gentle turning operation cylinder 66 is a normally closed type relief valve, and controls the pressure applied to the gentle turning operation cylinder 66 to gradually decrease. The variable relief valve 75 connected to the super pivot operation cylinder 72 is a normally closed relief valve.
The pressure applied to the super pivot turning operation cylinder 72 can be controlled so as to gradually increase from zero.

Reference numerals 76 and 77 denote side clutch cylinders, which are controlled by a clutch operation switching solenoid valve 78.

Reference numeral 79 denotes a continuously variable transmission operation cylinder. The continuously variable transmission operation cylinder 79 is operated by a continuously variable transmission operation solenoid valve 81 to adjust the width of the continuously variable output pulley 21 and to perform the on / off operation of the main clutch 16. That is, a stepless output pulley
When 21 is in the lowest speed state, the main clutch 16 is disengaged,
By driving the continuously variable transmission operation cylinder 79, the continuously output pulley 21 is driven in the speed increasing direction at the same time that the main clutch 16 is engaged.

The electric operation valves 73, 74, 75, 78 described above are controlled by an operation unit 80 provided on the operation panel 5.

As shown in FIG. 4, the operation unit 80 is composed of a single lever that swings in the left-right direction. At the center of the swing of the operation unit 80, a sensor 82 for detecting the operation position of the operation unit 80 is attached. Then, as shown in FIG. 4, each swing position O,
In A, B, C, AV, BV, and CV, the signal from the sensor 82 changes, and accordingly, each of the electrically operated valves 73, 74, 75, and 78 switches or the amount of operation changes.

FIG. 5 is a graph showing the relationship between the operation position of the operation unit 80, the pressure applied to each of the cylinders 66, 72, and 76, and the rotation speed of the output shaft.

Hereinafter, based on FIG. 3, FIG. 4 and FIG.
Will be described. FIG. 5 shows a case where the vehicle turns left.

When the operating section 80 is in the upright state, the two side clutches 46 and 47 are in the engaged state, and the pressure of the side clutch cylinders 76 and 77 is zero. Here, when the operation unit 80 is tilted leftward and positioned at the point A, the clutch operation switching solenoid valve 78 is switched by a signal from the sensor 82, and the side clutch cylinder is switched.
76 is driven, and the left side clutch 46 is disengaged. At the same time, the solenoid valve 73 is excited and switched, and
Pressure is applied to 66. Therefore, the friction clutch 65 is engaged, the intermediate shaft 51 rotates, and the torque is transmitted to the output shaft 55.

Here, when the operation unit 80 is further tilted in the direction of the point B, the variable relief valve 74 is operated according to the change in the amount of electricity from the sensor 82, and the pressure of the gentle turning operation cylinder 66 starts to decrease. Therefore, it is possible to change the frictional force of the friction clutch 65 in accordance with the operation amount of the operation unit 80 and continuously change the rotational force of the crawler traveling body 3 in the turning direction side, and to achieve a desired turning radius. The aircraft can be turned.

The pressure of the gentle turning operation cylinder 66 changes according to the operation amount of the operation unit 80 as shown in the lower column of FIG. This change rate can be obtained by changing the amount of electricity transmitted to the variable relief valve 74, and is set in advance by an electric control device provided between the sensor 82 and the solenoid valves 74 and 75.

When the operation unit 80 reaches the point B, the gentle turning operation cylinder 66
Is zero, and the rotation speed of the output shaft 55 is zero. When the operating unit 80 is further tilted, the dead zone for preventing simultaneous meshing has passed, and the signal from the sensor 82 causes the solenoid valve 73 to move.
Is switched to apply pressure to the super pivot swing operation cylinder 72.
On the other hand, the variable relief valve 75 operates in the closing direction according to the operation amount of the operation unit 80, and the hydraulic pressure in the cylinder changes as shown in the lower column of FIG. The change rate of the oil pressure is set so as to indicate a change in the oil pressure of the gentle turning operation cylinder 66 and a target change rate. Therefore, the operator can operate the operation section 80 with the gentle turning operation and the super-revolution turning operation with almost the same operation feeling, and is excellent in operability.

At the point C, the intermediate shaft 51 stops completely, and the left and right output shafts 55, 56
Will rotate in the opposite direction at the same speed, and the aircraft will make a pivot turn. The upper part of FIG. 5 shows how the rotation speed of the output shaft on the turning direction side changes according to the change in cylinder pressure. In addition, the dead zone at point B is provided with a time lag between the operation of the gentle turning operation cylinder 66 and the super pivot turning operation cylinder 72, regardless of the operation amount of the operation unit 80, to prevent simultaneous meshing of the gears. You can also. Further, as shown in FIG. 4, the swing angles between the respective operation angles O, A, A, B, and B, C are set to be equal, so that a gentle turning and a pivoting can be performed with the same operation feeling. You can turn.

<Effect of the Invention> According to the mechanism of the present invention configured as described above, since the slow rotation is applied to the output shaft on the clutch disengagement side by the transmission, it is possible to travel with an arbitrary turning radius.
Also, even if the aircraft sinks on soft ground, you can easily escape by gradually applying slow rotation to one of the crawlers,
In addition, there is an effect that the running ground is not roughened.

At this time, since the transmission has only one friction clutch, the slow rotation is transmitted to the output shaft on the clutch disengagement side by the ON / OFF operation of the only friction clutch even when turning in either the left or right direction, There are advantages that the operation system can be simply configured, the transmission does not become large, the operation is simple, and the communication mechanism of the operation system can be simple.

In addition, since the side clutch is located on the input side of the transmission, the torque load on the side clutch is reduced,
In addition to improving the durability of the side clutch, since the transmission is located on the input side of the output shaft, when a wet clutch is used as the friction clutch of the transmission, the amount of oil for immersing the friction clutch (wet clutch) is small. There is also an effect that it can be done.

[Brief description of the drawings]

1 is a sectional view showing the internal mechanism of a counter device and a transmission, FIG. 2 is an overall perspective view of a combine, FIG. 3 is a hydraulic circuit diagram for operating a cylinder, FIG. FIG. 5 is a graph showing the relationship between the operation position of the operation unit, each cylinder pressure, and the rotation speed of the output shaft. 3: Crawler traveling body, 13: Transmission 44: Clutch shaft, 46, 47: Side clutch 55, 56: Output shaft 61: Transmission for traveling wheel transmission 65: Friction clutch, 66: Slow turning operation cylinder 67: Slow turning Transmission 69: Super pivot turning transmission 73: Solenoid valve, 80: Operation unit

──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-1-101272 (JP, A) (58) Fields investigated (Int. Cl. ⁶ , DB name) B62D 11/00-11/24

Claims (1)

(57) [Claims] 1. A transmission (13) for separately outputting power from a prime mover to left and right crawler traveling bodies (3), and a transmission system left and right output shafts (55) and (56) in the transmission (13). Clutches (46) and (47) for inputting the transmission to the motor are provided on the input sides of the output shafts (55) and (56) provided separately on the left and right, and the side clutches (46) and (47) On the output side of the clutch shaft (44) of (47), there is provided a transmission that receives power from the clutch shaft (44) and transmits power for slow rotation to the output shaft on the side clutch (46), (47) disengaged side. A transmission (67), the transmission (67) having one intermediate shaft (51) for transmitting slow rotation to one of the output shafts;
A speed change mechanism in a crawler traveling device including one friction clutch (65) for transmitting slow rotation to the intermediate shaft (51).