JP2547583B2 - Rotary-planting device backlash removal device - Google Patents

Description

TECHNICAL FIELD The present invention relates to a backlash removing device for a rotary planting device.

(Prior Art) Conventionally, in a system in which a planetary gear mechanism drives a rotary planting pawl, two gears are provided side by side on a planetary gear shaft, and a spring is stretched between the equal gears so that one gear is rotated. The gear is loosened by advancing in the direction of rotation of the case and arranging the other gear as being delayed in the direction of rotation of the rotary case.

(Problems to be Solved by the Invention) According to the above, an attempt is made to eliminate the backlash of the planetary gears by the two gears and the spring, but the backlash is removed by the force of the spring. On the other hand, since the backlash changes depending on the rotation angle of the gear, the amount of bending of the spring changes greatly.

In order to obtain a large spring force in a narrow place, it is necessary to reduce the change in the amount of bending.

Therefore, it is an object of the present invention to obtain a backlash removing device for a rotary planting device in which the bending force of the spring does not change.

(Means for Solving Problems) The technical means of the present invention for solving the above technical problem is one in which a planetary gear mechanism drives a rotary planting pawl, and a sub gear is used with respect to a main gear. The backlash removing device of the rotary planting device is configured to reduce the amount of eccentricity and to cancel the deviation of the rotation angle due to the change of the backlash.

(Effect of the Invention) According to the technical means of the present invention, since the eccentric amount of the sub gear is made small with respect to the main gear, the bending amount of the spring does not change,
Therefore, it can be used with high stress, and a large spring force can be obtained in a narrow space.

Further, even over the entire rotation angle of the rotary, it is possible to prevent backlash by an average strong spring force.

(Example) Hereinafter, the Example shown in drawing is described.

First, a planetary gear provided with a backlash removing mechanism will be described.

The transmission shaft shown in FIG. 3, that is, the input shaft (1) is rotatable with respect to the planted transmission case (2).

 A sun gear (3) is loosely fitted on the transmission shaft (1).

However, it is fixed to the planting transmission case (2) via the sun gear phase adjusting member (4). This changes the relative position of the sun gear (3) with respect to the planted transmission case (2).

At the end of the transmission shaft (1), a hollow split rotary case (5) is mounted on the transmission shaft (1) by adjusting the position in relation to the upper stop position of the planting pawl. A rotary case (5) is attached and fixed to the transmission shaft (1) by a bolt (6).

The rotary case (5) as a rotating body meshes with the sun gear (3), and the intermediate gears (7) and (7) of the sun gear (3) and the same gear are freely rotatable through the intermediate shaft (8). And a planetary gear (10) having the same number of teeth as the sun gear (3) constantly meshed with the intermediate gear (7) on the intermediate shaft (8) on the cam shaft (9) as a planting shaft. ) Is fitted via a support member described later.

The sun gear (3), the intermediate gear (7), and the planetary gear (10) are gears that are appropriately decentered from the center of rotation.

The cam shaft (9) is also attached to the rotary case (5) via a position adjusting member (11).

A support member (12) is fitted on the cam shaft (9), and the planting arm (13) and the above-described planetary gear (10) are fixed to the support member (12).

By adjusting the position adjusting member (11) as described above, the extrusion timing of the extrusion claw is changed.

 The cam shaft (9) is provided with a cam (9a).

Now, when the rotary case (5) as a rotating body rotates about its rotation shaft in the direction of arrow a as shown in FIG. 8, the sun gear which cannot rotate with respect to the planting arm (13). The intermediate gear (7) meshing with (3) rotates in the direction of arrow b by the same rotation angle as the rotation angle of the rotation of the rotary case (5).

The planting claw case supporting member (12) which is interlocked with the intermediate gear (7) through the planetary gear (10) is rotated in the direction of arrow c by the rotation of the intermediate gear (7), that is, in the rotation direction of the rotary case (5). Since the planting arm (13) rotates in the opposite direction, the planting arm (13) pivots around the drive shaft (1) in a posture in which the planting arm (13) faces the seedling mounting table. When descending from the top side to the bottom side, after splitting only one seedling from the seedling mat on the seedling mounting table at the tip of the planting claw, planting in the field scene at the lower limit of the descending, and then It rises above the field, and the extruding claws extrude the seedlings during planting, so the seedlings separate from the planting claws.

Further, as shown in FIG. 8, all of the sun gear (3), the intermediate gear (7), and the planetary gear (10) are configured as eccentric gears with an appropriate eccentricity. The support member (12) revolves along with the rotation of the support member (12), and the rotation of the support member (12) itself in the direction c is accompanied by the rotation of the eccentric gears (3), (7), (7), (10) ( 1
0) It is configured to be faster or slower than the rotation speed of the rotary case (5) due to the difference in meshing pitch radius with respect to the rotation axis in each meshing.

Therefore, the time when the rotation of the planting claw case (13) in the c direction is delayed relative to the rotation of the rotary case (5) descends from the seedling picking position so as to approach the field scene of the planting arm (13). It is set to correspond to the timing, and on the other hand, the timing when the rotation of the planting arm (13) in the c direction becomes faster approaches the time when the planting arm (13) rises from the planting position so as to approach the upper limit of the rise of the planting arm (13). By doing so, each of the planting arms (13) is lowered in the rotary case (5) when descending so as to approach the field scene.
The rotation is slower in the c-direction than the rotation of the above, and the posture is changed downward by the revolution, and when it approaches the rising upper limit after planting, it advances more in the c-direction than the rotation of the rotary case (5) and rotates freely. As shown in FIG. 8, the closed loop of the movement locus of the claw tip is curved by one side, and the other side is a deformed elliptical closed loop curve closer to a straight line as shown in FIG.

In the conventional backlash removing mechanism of the rotary planting device as described above, two main gears (10a) and sub gears (10b) are provided on the planetary gear shaft (9) as shown in FIG. One of the gears (10a) with a spring stretched between the gears (10a) (10b)
To allow the rotary case (5) to advance in the rotational direction and the other gear (10b) to delay in the rotational direction of the rotary case (5). Specifically, each planetary gear (10a) ( As shown in FIG. 4, pins (14) and (15) of different lengths are projected on the side surface of 10b), and a spring (16) is stretched between the pins to equip one gear (10a) pin ( 14) is designed to be slidable in the elongated hole (17) of the other gear (10b).

 The illustrated spring uses a C-shaped spring.

Normally, a normal circular gear requires a certain amount of backlash in terms of processing accuracy, but the backlash of the meshing gear in the planetary gear mechanism is not good as that of a normal circular gear.

When an eccentric gear is used, the gear pitch circle comes closest to the position shown in FIG. 6A, and the meshing becomes deep. Therefore,
It must be kept farther than it would be if it were used as a normal gear between the gear axes.

Therefore, a large backlash occurs at the C position where the shaft center and the shaft center are aligned.

In any case, at the position shown in FIG. 6A, the axial distance is constant, but the axial distances are closer to the inner side, so the meshing is deeper, and the axial distance between the gears is higher than the axial distance (D) when the gears are horizontal. The core distance (D ') is small. Therefore, the gear shift is small and the backlash is small.

Since the backlash fluctuates as described above, it is necessary to forcibly eliminate the backlash in order to make this backlash constant, and the backlash can be eliminated by using a C-shaped spring. ,
The spring (16) expands and contracts according to the above displacement, and the pin (14) slides in the elongated hole (17).

Even if the backlash is large, it does not affect the seedling picking position and the planting position, and the most important seedling picking position is the position shown in FIG. 6B, which is almost the minimum and maximum backlash. Is in the middle of. When a C-shaped spring is used as the spring, the spring is compact and generates a large spring pressure, the expansion and contraction of the spring is small, and the fatigue of the spring is small.

That is, as described above, when the main gear and the sub gear both have a constant eccentricity, the shift amount changes as described above, and the C position is maximum and the A position is minimum. Here, the deviation amount is based on the line connecting the shaft centers, and FIG. 7 (a) shows it. Here, β ₁ > β ₂ .

Therefore, the distance between the pins (14) and (15) is changed, and the C spring is also subjected to the changing load, but since the expansion and contraction of the spring is relatively small, the fatigue of the spring is small.

FIG. 5 shows a method in which the spring (16) is stretched differently, and the engaging portions (16a) and (16b) are provided at the ends of the spring (16),
This is to be engaged with the engagement holes (18a) (18b) of the gears (10a) (10b). Here, the spring (16) is fitted in the circular groove (19) of the gear (10a) with a margin.

The present invention does not adopt the backlash removing mechanism as described above, but as shown in FIG. 1, the amount of eccentricity of the sub gear (10b) for removing the backlash is made smaller than that of the main gear (10a) to reduce the backlash. The deviation of the rotation angle due to the change of is canceled, and the change of the bending amount of the spring is reduced.

The one on the line A in FIG. 6 has a small backlash because the vehicle center is inward, and the gear shift is small and the backlash is small.

The one on the line C is a position where the vehicle center and the shaft center are arranged in a line in each gear, where the gear shift is large and the backlash is large.

Since the backlash fluctuates as described above, it is a conventional one to eliminate the backlash by using a C-shaped spring. As shown in FIG. Since the amount of flexure of the spring for eliminating backlash is small, a strong spring works, and the part on the E line at the planting position is also the deceleration section of the tip of the planting claw and the strong spring works. In addition, since the spring on the line C has a large amount of spring deflection to eliminate backlash, the spring force is weak.

As described above, since the spring tension changes in the conventional one, in order to eliminate this change, the present invention reduces the eccentric amount of the sub gear with respect to the main gear. Seventh
The figure (b) shows the difference in the amount of eccentricity.

The one shown by the solid line in FIG. 1 is the main gear,
The dotted line is the sub gear.

Although the backlash is small at the E position, the change in the backlash is canceled due to the difference in the amount of eccentricity between the main gear and the sub gear, so that the change in the spring tension can be eliminated.

That is, the main gear has a large amount of eccentricity and thus has a large rotation angle in the clockwise direction, but the sub gear has a small amount of eccentricity and therefore has a small rotation angle in the clockwise direction. You can cancel the backlash,
Therefore, the change in the tension of the spring can be eliminated.

In the C position, the main gear rotates clockwise by the amount of backlash and the sub gear rotates counterclockwise by the amount of backlash, so even if there is a large amount of backlash, this can be canceled, and therefore the tension of the spring The change in can be eliminated.

As described above, according to the present invention, since the flexure amount of the spring does not change, it can be used with high stress, and a large spring force can be obtained in a narrow space.

In addition, it is possible to prevent backlash by an average strong spring force over the entire rotation angle of the rotary.

A spring force is particularly required near the seedling picking position and the field entry, but this requirement can be sufficiently satisfied.

[Brief description of drawings]

FIG. 1 is a principle view of the present invention, FIG. 2 is a change diagram of spring tension over the entire rotation angle of a rotary, FIG. 3 is a sectional view of a rotary case, and FIGS. Partial views, FIGS. 6 and 7 (a) are backlash state explanatory diagrams, FIG. 7 (b) is an eccentricity amount diagram, and FIG. 8 is a planting locus explanatory diagram. (1) …… Input shaft (3) …… Sun gear (5) …… Rotary case (7) …… Intermediate gear (10) …… Planet gear (10a) …… Main gear (10b) …… Sub gear ( 16) …… Spring

Claims (1)

(57) [Claims] 1. A planetary gear mechanism for driving a rotary planting pawl, wherein the eccentric amount of the sub gear is small with respect to the main gear, and the rotary plant is configured to cancel the deviation of the rotation angle due to the change of the backlash. Backlash removal device for attached devices.