JPH02290786A - Speed change mechanism in crawler traveling device - Google Patents

Abstract

PURPOSE:To permit the traveling in an arbitrary turning radius by installing a pair of side clutches which cut off the transmission from a common transmission system in a speed change gear to the right and left output shafts and installing a speed change gear for outputting a power for the gentle speed revolution between the right and left output shafts and each side clutch. CONSTITUTION:In a speed change gear 13 of a combine, a turning moment is transmitted to an advance/retreat selecting device 41 from a differential gear device 31 by a traveling output gear 31a, and the turning moment is transmitted to the drive gear 45 of a clutch shaft 44 through a back haft 42 or transmission shaft 43 from the device 41. In this case, the right and left side clutches 46 and 47 are externally fitted onto the both sides of the driving gear 45, and the transmission gears 55 and 54 which are meshed with the side clutches 46 and 47 are externally fitted with an intermediate shaft 51. The output gears 57 and 58 on the output shafts 55 and 56 are meshed with the small diameter gears of the transmission gears 53 and 54. Further, a speed change gear device 67 for gentle turn which consists of a free gear 63 meshed with an output gear 48 for turn traveling and a frictional clutch 65 is installed at one edge of the intermediate shaft 51.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a speed change mechanism in a crawler traveling device.

Prior Art> Steering operations in a crawler traveling device are performed by placing the crawler traveling body in three states: a driving state, a clutch disengaged state, and a braking state. There are two turning methods: one is to determine the direction, the other is to disable the drive of the crawler body using the side clutch, allowing free rotation on the disengaged side of the side clutch, and a gentle turn by driving the crawler body on the opposite side. there were.

Problems to be Solved by the Invention> However, in the above-mentioned conventional traveling device, there are two turning methods.
The drawback was that there were only streets, making it difficult to turn in any direction depending on the road surface situation.

In addition, when turning, the crawler scrapes the road surface and makes it rough, and if the aircraft sinks into soft ground, the clutch must be turned on and off in an inching manner to gradually turn the crawler running body. There were problems such as having to rotate the vehicle to escape. It is especially desirable to solve these problems with mobile agricultural machines that travel on farmland.

Means for Solving the Problems> In order to solve the above problems, the present invention provides a transmission 13 that separately outputs power from a prime mover to the left and right crawler traveling bodies 3. From the transmission system to the left and right output shafts 55. Side clutches 46 and 47 are provided to turn on and off the transmission to the left and right output shafts 55 and 56, respectively. 56 and the clutch shaft 44 of the side clutch, a transmission device 67 is provided which receives power from the common transmission system and transmits power for slow rotation to the output shaft on the clutch disengaged side. It is a feature.

Action> From the transmission 13 to each output shaft 55. The power output to 56 is connected and disconnected by left and right side clutches 46 and 47.

When turning, use the side clutch 4 in the turning direction.
6 (or 47) is turned off. When turning slowly,
In addition, the transmission device 67 for slow turning operates and the clutch 46
Since slow rotation is given to the output shaft 55 on the cut side, the crawler traveling body on the turning direction side is slowed down, and the machine body can turn gently.

<Example> Hereinafter, an example of the present invention will be described based on the drawings.

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

FIG. 1 is a sectional view showing the internal mechanisms of the counter device 11 and transmission 13 of the combine main body 1. As shown in FIG.

A counter input shaft l5 protrudes from the counter device 11 to input power from a prime mover, and a counter input shaft 17 is attached to the tip of the shaft l5, and the power is transmitted by a belt. A main clutch 16 is provided between the counter input coupler l7 and the counter input coupler shaft 15.
The 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 through several gears while being changed in speed. A stepless output pulley 2I is attached to the counter output shaft 19. Stepless output pulley 2
The width of ``l'' is adjusted by an adjustment device also mounted on the counter output shaft hl9, and the transmission speed is adjusted without permission. A cam lever 23 operates the adjustment device using hydraulic pressure. A constant speed output shaft 25 projects from the side opposite to the side where the counter output shaft 19 projects, and a constant speed output boot 926 is fixed thereto. The stepless output coupler 21 and the constant speed output coupler 26 rotate in opposite directions.

Next, the internal mechanism of the transmission 13 will be explained.

A speed change input shaft 27 and a constant speed input shaft 28 protrude left and right from the counter device 11 side of the transmission 13.

And Kashaf for both! -27. 28, the differential gear device 3 provided inside the transmission 13 is located at the butt portion.
1 is provided.

- At the protruding ends of the 4-speed manual shaft 27 and the constant speed manual shaft 28, a stepless man caboo 929 and a constant speed man caboo 30 are provided.
are installed, and the same rotational force is transmitted in the opposite direction via the transmission belt. A reaping output shaft 38 is inserted and supported adjacent to the differential gear device 3I, and the reaping output shaft 3
8 is provided with a switching device 34. The switching device 34 includes a high speed gear 33 and a low speed gear 35 that are rotatably attached to the reaping output shaft 38, and a switching gear 37 that rotates integrally with the reaping output shaft 38 and is provided so as to be slidable in the axial direction. ing. A reaping output pulley 39 is attached to the protruding end of the reaping output shaft 38 and transmits rotational force to the drive system of the reaping machine 7. Therefore, the reaping drive speed of the reaping machine conveying section 7a changes depending on the change in the rotational speed of the reaping output shaft 38.

The high speed gear 33 meshes with a gear 32 fixed to the speed change input shaft 27, and the low speed gear 35 is connected to the outside of the differential gear device 31. It meshes with the provided reaping output gear 3lb. The switching gear 37 slides along the reaping output shaft 38, meshes with internal teeth of either the high speed gear 33 or the low speed gear 35, and outputs high speed rotation or low speed rotation from the reaping output shaft 38. Since the low-speed gear 35 has a smaller diameter than the high-speed gear 33, the rate at which the rotational speed increases with respect to the increase in the rotational speed of the reaping output gear 3lb is greater than that of the high-speed gear 13. Therefore, when traveling at low speeds, the reaping drive speed is lower when the low speed gear 35 is engaged than when the high speed gear 33 is engaged, but when traveling at high speeds, the reaping drive speed is lower when the high speed gear 35 is engaged.
The reaping drive speed is slower in the case of three meshes.

Next, the traveling transmission system will be explained.

Rotational force is transmitted from the differential gear device 31 to the forward/reverse switching device 41 by a travel output gear 31a formed on the outer periphery. 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. A left side clutch 46 and a right side clutch 47 are fitted onto both sides of a drive gear 45 provided at the center of the clutch shaft 44 so as to be able to slide and rotate independently of the clutch shaft 44, and the drive gear 45 is fitted around the outer periphery of the drive gear 45. A pinion is formed that meshes with the internal gear. Both side clutches 46, 47 are always urged toward the drive gear 45 by springs and engaged, and are released from engagement with the drive gear 45 by the operation of the side clutch cylinders 76, 77. Further, a turning output gear 48 is fixed to one end of the clutch shaft 44 so as to be able to rotate together with the clutch shaft 44, and meshes with a free gear 63, which will be described later.

On the intermediate shaft 51 adjacent to the clutch shaft 44, a side clutch 46. Transmission gears 53. and 47 mesh with each other. 54 is rotatably fitted on the outside.

Therefore, the intermediate shaft 51 and the transmission gear 53. 54 can each rotate independently. Also, transmission gear 53. 5
4 consists of a large diameter gear and a small diameter gear, and meshes with the large diameter gear or the side clutch 46, 47.

Transmission gear 53. The small diameter gear 54 is connected to an output shaft 55 that protrudes from both sides of the transmission 13. It meshes with output gears 57 and 58 fixed to output gears 57 and 56, respectively. By the rotation of 58, driving force is output to the left and right crawler traveling bodies 3. Attached to the tip of the output shaft 55 is a running wheel 60 made of a drive subrocket.
The crawler belt is driven by the rotation of 0.

During normal straight-ahead driving, the left and right side clutches are 46.4
7 is in a human state, and the left and right output shafts 55. Power is transmitted to 56 independently. At this time, the intermediate shaft 5l is freely rotating.

The slow rotation transmission system will be explained.

Output shaft 55. Between 56 and 56 is a transmission device 61 for transmitting running wheels.
In the mechanism of this embodiment, the running wheel transmission transmission device 61 is comprised of a differential gear device 59.

On the other hand, a free gear 63 is rotatably fitted onto one end of the intermediate shaft 51, and a friction clutch 65 is provided between the intermediate shaft 51 and the free gear 63. Friction Kura Nochi 65
is off during normal straight running, and the rotational force transmitted from the turning output gear 48 to the free gear 63 is
Normally, it is not transmitted to the intermediate shaft 51.

The friction clutch 65 is turned on and off by a slow turning operation cylinder 66.

A gear 51a that rotates integrally with the intermediate shaft 51 is formed, and the gear 51a meshes with a swing drive input gear 59a provided in a differential gear device 59. Therefore, in the straight traveling state, the differential gear device 59 is connected to the output shaft 55. 56, and the intermediate shaft 5l also rotates via the swing drive input gear 59a and the gear 51a.

Here, the output gear 48 for turning, the intermediate shaft 51, the free gear 63, and the friction clutch 65 constitute a transmission device 67 for slow turning.

The slow turning transmission system consists of a slow turning transmission 67 and a running wheel transmission transmission 61. That is, in the mechanism of this embodiment, the turning driving output gear 48, the free gear 63, the friction clutch 65, the intermediate shaft 51. Gear 51a, swing drive input gear 59
a and a differential gear device 59.

For example, when turning slowly to the left, the left side clutch 46 is set to the disengaged state, and the friction clutch 65 is set to the human state. As a result, the input to the output gear 57 is removed from the output shaft 55, and the rotational force transmitted to the intermediate shaft 5l via the friction clutch 65 is input to the differential gear device 59, and from the differential gear device 59 to the output shaft The rotational force is output to 55. Then, 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, and the rotational speed of the output shaft 55 decreases accordingly. Therefore, a difference in rotational speed occurs between the crawler traveling body on the right side and the crawler traveling body on the left side, and the aircraft moves while turning gently in the left direction with fewer rotations.

When making a gentle turn to the right, the right side clutch 47 may be disengaged and the friction clutch 65 may be operated in the same manner.

Next, a super pivot turning transmission system for driving the left and right crawler traveling bodies 3 in opposite directions to make a super pivot turning in a fixed position will be described.

A brake 7l is provided at the end of the intermediate shaft 51 opposite to the end where the friction clutch 65 is attached.
is operated by the super pivot turning operation cylinder 72. By operating the brake 71, the intermediate shaft 51 is fixed and rotation is stopped.

The brake 71 and the intermediate shaft 51 constitute a super pivot turning transmission 69. The transmission system for super pivot turning consists of a super pivot turning transmission 69 and a traveling wheel transmission transmission 61. In the mechanism of this embodiment, a brake 71, an intermediate shaft 51, a gear 51a, a swing drive input gear 59a and a differential gear device 59.

For example, when making a counterclockwise turn, if the left side clutch 46 is disengaged and the play cow 71 is activated, the rotation of the intermediate shaft 5l is stopped and the turning drive input gear 59a
stops rotating. Due to the action 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, which is in a free state, and rotates at the same number of rotations as the output shaft 56.

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

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

FIG. 3 is a hydraulic circuit diagram of a combine harvester using this embodiment. The slow turning operation cylinder 66 and the super turning operation cylinder 72 are single-acting cylinders that are always biased in the contraction direction. The slow turning operation cylinder 66 and the super turning operation cylinder 72 are connected to a single three-position four-way switching solenoid valve 73, and a circuit is connected so that hydraulic pressure always acts on only one side. Also, each cylinder 66. 72 has electrically controlled variable IJ
Leaf valve 74. 75 is connected, cylinder 6
6. The pressure applied to 72 is controlled. Here, the variable relief valve 7 connected to the slow swing operation cylinder 66
Reference numeral 4 denotes a normally closed type relief valve, which controls the pressure applied to the slow swing operation cylinder 66 to gradually decrease. Further, the variable relief valve 75 connected to the super pivot turning operation cylinder 72 is a normally open type IJ IJ-F valve, and controls the pressure applied to the super pivot turning operation cylinder 72 to gradually increase from 0. It is possible.

78 and 77 are side clutch cylinders, which are controlled by a switching solenoid valve 78 for clutch operation.

Further, 79 indicates a continuously variable speed operation cylinder. The continuously variable speed operating cylinder 79 is operated by a continuously variable speed operating solenoid valve 8l to adjust the width of the continuously variable output boolean 21 and to turn on and off the main clutch I6. That is, when the continuously variable output pulley 21 is in the lowest speed state, the main clutch l6 is disengaged, and by driving the continuously variable speed operation cylinder 79, the main clutch 16 is brought into the human state, and at the same time, the continuously variable output pulley 21 is moved in the speed increasing direction. drive

The electrically operated valves 73, 74, 75 described above. 78
is controlled by an operation section 80 provided on the operation panel 5.

As shown in FIG. 4, the operating section 80 is composed of one lever that swings in the left-right direction. A sensor 82 for detecting the operating position of the operating section 80 is attached to the swing center of the operating section 80 . Then, as shown in FIG. 4, at each swing position 0, A, B, C, A', B', C', the signal from the sensor 82 changes, and each electrically operated valve changes accordingly. 3, 74, 75. 78 is switched or the operating amount changes.

FIG. 5 shows the operating position of the operating section 80 and each cylinder 66, 72.
．． 76 is a graph showing the relationship between the pressure applied to 76 and the rotation speed of the output shaft.

Below, based on FIG. 3, FIG. 4, and FIG.
The steering operation will be explained below. FIG. 5 shows a case where the vehicle turns left.

When the operation section 80 is in the upright state, both side clutches 46, 4
7 is in the human condition, and the pressure in the side clutch cylinders 76 and 77 is O. Now, tilt the operation unit 80 to the left and
When positioned at a point, the signal from sensor 82 causes
The clutch operation switching solenoid valve 78 is switched, the side clutch cylinder 76 is driven, and the left side clutch 46 is in the disengaged state. At the same time, the electromagnetic valve 73 is excited and switched, and pressure is applied to the gentle swing operation cylinder 66. Therefore, the friction clutch 65 is in the human state, the intermediate shaft 51 rotates, and rotational force is transmitted to the output shaft 55.

Here, when the operation part 80 is further tilted in the direction of point B, the variable relief valve 74 responds to the change in the amount of electricity from the sensor 82.
is activated, and the pressure in the slow rotation operation cylinder 66 begins to decrease. Therefore, it is possible to change the friction force of the friction clutch 65 in accordance with the operation amount of the operation unit 80, and to continuously change the speed of the rotational force of the crawler traveling body 3 in the turning direction, so that a desired turning radius can be achieved. The aircraft can be rotated.

The pressure in the slow swing operation cylinder 66 changes as shown in the lower column of FIG. 5 in accordance with the amount of operation of the operation section 80. This rate of change can be obtained by changing the amount of electricity transmitted to the variable relief valve 74 and the sensor 82 and the solenoid valve 74. 75
It is preset by an electric control device provided between the two.

With the operation part 80 reaching point B, the gentle rotation operation cylinder 6
6 becomes O, and the rotation speed of the output shaft 55 becomes O.

When the operation part 80 is further pushed down, the dead area for preventing simultaneous engagement has passed, and the signal from the sensor 82 causes the
The solenoid valve 73 is switched and pressure is applied to the super pivot turning operation cylinder 72. On the other hand, the variable IJ IJ ++ valve 75 acts in the closing direction according to the amount of operation of the operation part 80, and the fifth
The oil pressure inside the cylinder changes as shown in the bottom column of the figure. The rate of change in the oil pressure is set to show a rate of change that is symmetrical to the change in the oil pressure of the slow swing operation cylinder 66. Therefore, the operator can operate the operation unit 80 with substantially the same feeling for slow turning operations and super steady turning operations, resulting in excellent operability.

The intermediate shaft 51 completely stops at point C, and the left and right output shafts 55.
56 rotates in the opposite direction at the same rotation speed, and the aircraft makes a sharp turn. The upper column of FIG. 5 shows how the rotational speed of the output shaft on the rotating direction side changes in response to changes in cylinder pressure. In addition, the dead area at point B is related to the amount of operation of the operating unit 80. It can also be prevented. In addition, as shown in Fig. 4, each operation angle is between O point and A point, between A point and B point, and between B point and B point.
The swing angles between the points C and C are set to be equal, so that it is possible to make a bow turn and a pivot turn with the same feeling of operation.

Effects of the Invention According to the mechanism of the present invention configured as described above, slow rotation is applied to the output shaft on the clutch disengaged side by the transmission, so that it is possible to travel with an arbitrary turning radius. Furthermore, even if the aircraft sinks into soft ground, it can easily escape by gradually applying slow rotation to one of the crawlers, and the effect is that the ground on which it is running is less likely to be disturbed.

Furthermore, since the left and right output rotations are operated by a single transmission, the transmission does not need to be large, and it has the advantage of being easy to operate and requiring only a simple communication mechanism for the operation system.

[Brief explanation of drawings]

Figure 1 is a sectional view showing the counter device and internal mechanism of the transmission, Figure 2 is a perspective view of the entire combine, Figure 3 is a hydraulic circuit diagram for operating the cylinders, Figures 4 and 5 are the operating section. FIG. 6 is a graph showing the relationship between the operating position of the operating section, each cylinder pressure, and the rotation speed of the output shaft. 3: Crawler traveling body 13: Transmission 44; Clutch shaft 46, 47: Side clutch nozzles 55, 56: Output shaft 61; Traveling wheel transmission transmission 65: Friction clutch 66: Slow turning operation cylinder 67; Slow turning transmission 69 :Transmission device for super swing turning 73:Solenoid valve 80:Operation unit patent
Applicant: Mitsubishi Agricultural Machinery Co., Ltd.

Claims (1)

[Claims] 1) In the transmission (13) that outputs power from the prime mover to the left and right crawler traveling bodies (3) separately, the transmission (13)
) from the common transmission system to the left and right output shafts (55), (5
a side clutch (46) that turns on and off the transmission to 6);
(47), and the left and right output shafts (55
), (56) and the side clutches (46), (47)
In the crawler traveling device, a transmission device (67) is provided between the clutch shaft (44) and the transmission system (67), which receives power from the common transmission system and transmits the power for slow rotation to the output shaft on the clutch disengaged side. Transmission mechanism.