JP3294101B2 - Seedling planting mechanism - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotating case rotatably supported around a first axis with respect to a planted transmission case, and relatively rotatable around a second axis parallel to the first axis. A planetary gear fixed to a support shaft that supports a planting claw support having a planting claw attached thereto, and supports the planting claw support in a state of being integrally rotated; a planting transmission case A sun gear fixed non-rotatably to the first intermediate gear meshing with the sun gear; a second intermediate gear rotating around an eccentric rotation axis and meshing with the planetary gear with the rotation axis of the first intermediate gear; Gear, an eccentric crank type rotation transmission mechanism for unequally interlocking the first intermediate gear and the second intermediate gear, and with the rotation of the rotating case, the tip of the seedling claw has a substantially elliptical locus. Seedling planting provided with relative rotating means for relatively rotating the planting claw support and the rotating case as depicted. About the structure.

[0002]

2. Description of the Related Art The above-described seedling planting mechanism is constructed as disclosed in, for example, Japanese Patent Application No. 7-76112. That is, as shown in FIG.
With the rotation of 0, the first intermediate gear 31 rotates for meshing with the sun gear 23. At this time, the first intermediate gear 31
And the second intermediate gear 32, the rotation axis of which is eccentric, and the rotation power is transmitted by the eccentric crank type rotation transmission mechanism D, so that the planetary gear 30 meshing with the second intermediate gear 32 is not The planting claw support 13 is rotated at a constant speed with respect to the rotating case 10. That is, in driving the seedling-claw so that the tip of the seedling-claw draws a substantially elliptical trajectory, circular gears are employed as the planetary gear 30, the intermediate gears 31, 32, and the sun gear 23, and each gear is set to a non-geared state. This makes it possible to produce the gear at a lower cost than a circular gear and to smoothly rotate the gear with less backlash caused by backlash. Furthermore, the support shaft 14 that supports the planting claw support 13 can be more firmly supported by the rotating case 10 in a double-supported state than when the eccentric crank type rotation transmission mechanism D is provided on the support shaft 14. It was made. In addition, the crank type rotation transmission mechanism D, which is relatively easy to generate vibration due to crank transmission, is located closer to the rotation axis X1 of the rotation case 10 than the support shaft 14 and generates vibration in the rotation case 10. This makes it possible to smoothly drive the rotating case 10 in spite of employing the crank type rotation transmission mechanism D.

[0003] In this kind of seedling planting mechanism, conventionally, FIG.
As shown in FIG. 2, a cam groove 39 is provided in the first intermediate gear 31, and a roller 36 which slides into the cam groove 39 to interlock the first intermediate gear 31 and the second intermediate gear 32 is provided.
By providing a in the second intermediate gear 32, an eccentric crank type rotation transmission mechanism D was configured.

[0004]

A seedling having a strong root is used as a seedling to be supplied to the seedling planting mechanism, and when the seedlings are taken out of the seedlings or when the seedlings are planted. If a strong reaction force is applied to the seedling claw due to hitting the soil mass or a stone being stuck in the seedling removal outlet, a large driving load is applied to the intermediate gear. For this reason, as a gear support shaft that supports the first intermediate gear and the second intermediate gear, a gear support shaft that is supported by the rotating case at both ends and supports the first intermediate gear and the second intermediate gear between both ends, If a so-called rotating case is used with a gear support shaft that is supported in a double-supported state, the gear support shaft is less likely to deform or break even if a large load is applied to the intermediate gear. This is advantageous because the gear is firmly supported. When the doubly supported gear support shaft is adopted as described above, the connecting shaft portion connecting the shaft portion supporting the first intermediate gear and the shaft portion supporting the second intermediate gear among the gear support shafts is the first intermediate shaft portion. It will be between the gear and the second intermediate gear. For this reason, if a conventional rotation transmission mechanism using a roller is adopted, it is necessary to configure the roller so as to revolve around the connecting shaft portion without hitting the connecting shaft portion of the gear support shaft. On the other hand, a relatively thin pin must be used as a transmission pin for linking the two intermediate gears, and the transmission strength of the rotation transmission mechanism has been relatively low.

[0005] Further, instead of employing the above-mentioned double-supported gear support shaft as the gear support shaft, the first intermediate gear and the second intermediate gear are separately supported, and are supported by the rotating case only at one end. Even when the cantilever type gear support shaft is adopted, the end of the gear support shaft supporting the first intermediate gear projects toward the second intermediate gear due to the configuration of the gear support shaft, or the like. When the end on the side supporting the second intermediate gear projects toward the first intermediate gear, the roller revolves around the protruding end without hitting the protruding end of the gear support shaft. Must be configured. For this reason, even when a cantilever type gear support shaft is employed, a relatively thin pin must be employed as a transmission pin for supporting a roller, as in the case of employing a dual support type gear support shaft. The transmission power by the mechanism was relatively low. An object of the present invention is to provide a seedling planting mechanism capable of increasing the transmission strength of a rotation transmission mechanism.

[0006]

The constitution, operation and effect of the invention according to claim 1 are as follows.

[Structure] A seedling is mounted on a rotating case rotatably supported about a first axis relative to a planting transmission case so as to be relatively rotatable about a second axis parallel to the first axis. A planetary gear fixed to a support shaft that pivotally supports the planted claw support to which the claw is attached, and pivots the planted claw support integrally, so that it cannot rotate with the planting transmission case. A fixed sun gear, a first intermediate gear meshing with the sun gear, a second intermediate gear rotating around an eccentric rotation axis and meshing with the planetary gear, and a first intermediate gear with the rotation axis of the first intermediate gear. It has an eccentric crank type rotation transmission mechanism for unequally interlocking the gear and the second intermediate gear, and planting so that the tip of the seedling claw draws a substantially elliptical locus as the rotating case rotates. In a seedling planting mechanism having a relative rotating means for relatively rotating the nail support and the rotating case, A cam groove is provided in one of the one intermediate gear and the second intermediate gear, and a crank pin that slides into the cam groove to interlock the first intermediate gear and the second intermediate gear with each other is provided. An eccentric crank type rotation transmission mechanism is provided on the intermediate gear, and the crank pin is formed as a non-circular pin having a notch at a location of the outer peripheral portion facing the intermediate gear rotation axis. It is.

[Operation] If a crank pin that does not rotate is employed as a transmission pin for interlocking the two intermediate gears, the notch provided at a position facing the rotation axis of the intermediate gear does not come into contact with the inner surface of the cam groove. Thus, the notch is not involved in interlocking the two intermediate gears. Thereby, while using a thick pin so as to provide high transmission strength, and even if a double-supported or cantilevered gear support shaft as described at the beginning is adopted,
The interlocking of the two intermediate gears by the crankpin can be performed while preventing the crankpin from hitting the end of the gear support shaft or the connecting shaft portion so as not to function.

[Effect] Even if the double-supported or cantilevered gear support shaft described above is employed as the gear support shaft, the crankpin can be made thicker, so that the transmission strength of the eccentric crank type rotation transmission mechanism can be reduced. It is possible to use the seedlings with strong roots, or to have strong durability in driving the seedling claw even when there is soil in the field or when stones are caught in the seedling removal outlet. Now you can do it. In addition, it is possible to use the double-supported gear support shaft to favorably support the intermediate gear in terms of strength, and from this viewpoint, it is possible to improve the driving strength and durability.

The construction, operation and effect of the invention according to claim 2 are as follows.

In the structure according to the first aspect of the present invention, the distance between the peripheral surface of the crank pin at the notch portion and the rotation axis of the intermediate gear is larger than the radius of the shaft hole of the intermediate gear. Largely formed.

[Operation] Even if the distance between the peripheral surface of the crankpin and the intermediate gear rotating shaft center is formed to be the same as the radius of the intermediate gear shaft hole, the double-sided or cantilevered type described at the beginning is used. Even when the gear support shaft is employed, the crank pin revolves around the gear support shaft while slidingly contacting the end of the gear support shaft and the connecting shaft portion in the notch, thereby performing gear interlocking. However, in this case, the intermediate gear abuts on the gear support shaft inside both the support shaft hole and the notch portion in the circumferential direction where the crank pin exists, and supports the support shaft in the position where the crank pin does not exist. It contacts the gear spindle only inside the shaft hole. That is, it rotates while abutting on the gear support shaft in a wider area than the place where the crankpin is present than the place where the crankpin is not present. For this reason, universal wear tends to occur on the gear support shaft and the intermediate gear. On the other hand, in the case of the present invention, the distance between the peripheral surface of the crankpin and the intermediate gear rotating shaft center is larger than the radius of the intermediate gear shaft hole, so that the two-sided or single-sided type described at the beginning is used. Even if a holding-type gear support shaft is used, there is a gap between the notch of the crankpin and the end of the gear support shaft or the connecting shaft, and the intermediate gear is supported only inside the support hole. Sliding contact with the axis. As a result, the intermediate gear rotates while abutting on the gear support shaft in the same area at both the position where the crankpin exists and the position where the crankpin does not exist, and it is difficult for universal wear to occur on the gear support shaft and the intermediate gear.

[Effects] The gear shaft and the intermediate gear are less likely to be worn around, and the rotation transmitting mechanism has a high durability so that it can operate smoothly for a long period of time.

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS As shown in FIG.
And a plurality of planting transmission cases 3 connected to the main frame 1 at appropriate intervals in the body width direction and connected to the feed case 2 connected to a substantially central portion in the body width direction. It is. At the front of the frame, a seedling mounting table 4 is mounted so as to be reciprocated at a constant stroke in the lateral direction of the machine body.
A seedling planting device 5 is provided on the left and right sides of each rear portion so as to be drivable, and a plurality of ground floats 6 arranged in the machine body lateral direction are attached to the bottom of the frame body to constitute a seedling planting apparatus A. The seedling planting apparatus A is operated so as to be lifted and lowered via a link mechanism (not shown) at the rear of a traveling machine (not shown), and is transmitted from the self-propelled machine to the feed case 2. To form a riding type rice transplanter. Then, as the airframe runs, the ground float 6 touches the mud surface of the field to support the weight of the airframe and level the mud surface, and each seedling planting mechanism 5 has a mat mounted on the seedling mounting table 4. A part of the seedling is cut out and planted at the leveling place by the ground float 6.

As shown in FIGS. 1 and 2, each of the plurality of seedling planting mechanisms 5 has a rotating case 10 on the side of the rear part of the planting transmission case 3 around the first shaft center X1 in the machine body lateral direction. Are mounted so that they can be driven to rotate in the rotation direction F. The seedlings are separated from the first axis X1 of the rotation case 10 and have a phase difference of 180 degrees with respect to each other in the rotation direction of the rotation case 10. A planting nail support case 13 as a planting nail support provided with the planting nail 12 and the seedling pushing tool 15
Is mounted so as to rotate around a second axis X2 parallel to the first axis X1, and the planting claw support case 13 and the rotating case 10 are driven to rotate relative to each other as the rotating case 10 is driven to rotate. A relative rotation means S is provided between each planting claw support case 13 and the planting transmission case 3, and a seedling pushing-out operation mechanism E that operates the seedling pushing-out tool 15 as the rotating case 10 is driven to rotate. Each of the planting claw support cases 13 is provided.

The rotating case 10 is formed by tightening and connecting the two half case portions 10A and 10B with connecting bolts so that the rotary case 10 can be divided into two half case portions 10A and 10B along the dividing line Y. A central portion in the longitudinal direction of one half case portion 10A of the rotating case 10 is rotatably attached to the rear side of the planting transmission case 3 via a bearing 7 at a rear side of a body boss portion 3a of the body, and the other half portion. Bearing part 1 located at the center in the longitudinal direction of case part 10B
0a is rotatably supported by the planting transmission case 3 via a bearing 9 and is connected to the end of the output shaft 8 passing through the boss 3a so as to rotate integrally with a tapered pin 11. . The output shaft 8 is rotationally driven by rotational power transmitted from the feed case 2 via a transmission chain (not shown). This allows
The rotating case 10 is supported by the planting transmission case 3 so as to rotate around a first axis X1 which is the axis of the output shaft 8, and is driven by the output shaft 8 in the rotation direction F.

The planting claw support case 13 includes the rotating case 10
Is connected to the end of the support shaft 14 rotatably supported via a pair of bearings 24 and 25 and protruding from the rotating case 10 to the outside. Planting nail support case 13
The flange portion 27 integrally formed with the
By attaching the support shaft 14 to the support shaft 14 such that the end of the support shaft 14 enters the through hole 29 of the support shaft 14 and tightening and connecting the flange portion 26 fixed to the support shaft 14 with a bolt 28, The support shaft 14 is allowed to rotate integrally. Thereby, the planting claw support case 13 is rotatably supported by the rotating case 10 around the second axis X2 of the support shaft 14 parallel to the first axis X1.

As shown in FIGS. 2 and 3, the pair of relative rotation means S and S are a sun gear 23 which is rotatably fitted on the output shaft 8 and a planet gear which is mounted on the support shaft 14. A first intermediate gear 31 and a second intermediate gear 32 disposed between the planetary gear 30 and the sun gear 23 and rotatably supported on the rotating case 10 via a gear support shaft 50; It is constituted by a crank type rotation transmission mechanism D provided between 31 and 32.

The sun gear 23 is arranged so that its axis is located on the axis of the first axis X1. By engaging the meshing claw B formed on the boss of the sun gear 23 with the meshing claw formed on the end of the boss 3a of the planting transmission case 3, the planting transmission case is formed. Numeral 3 fixes the sun gear 23 so that it cannot rotate. Planetary gear 3
Numeral 0 is connected to the planting claw support case 13 so as to rotate integrally with the support shaft 14 by engaging the support shaft 14 with the key 30a so as to rotate together. Thereby, the planetary gear 30 is a gear for rotating the planting claw support case 13 with respect to the rotating case 10. First intermediate gear 31
Are eccentric to the first shaft center X1 by being fitted to the sun gear 23 and externally rotatably fitted to the first shaft 51 at one end of the gear shaft 50. The first support shaft 51 is rotatably supported by the rotating case 10 around the third shaft center X3. The second intermediate gear 32 is meshed with the planetary gear 30, and is located at the other end of the gear support shaft 50 and is displaced toward the first shaft center X <b> 1 with respect to the first support shaft portion 51. The second shaft portion 52 is rotatably fitted around the second shaft portion 52 so as to be rotatable around the fourth shaft center X4 closer to the first shaft center X1 than the third shaft center X3. It is supported by a rotating case 10. Each of the sun gear 23, the planetary gear 30, the first intermediate gear 31, and the second intermediate gear 32 is formed as a circular gear whose pitch circle is a perfect circle. As shown in FIG. 2, the thrust collar 40 as shown in FIG. 7 fitted externally to the first support shaft portion 51 of the gear support shaft 50, and the thrust collar as shown in FIG. 7 fitted externally to the second support shaft portion 52. The collar 41 includes the intermediate gears 31 and 32 and the rotating case 1.
The friction between the intermediate gears 31 and 32 is reduced, and the rotation of the intermediate gears 31 and 32 is facilitated.

As shown in FIGS. 3 and 5, the crank type rotation transmission mechanism D has a pair of projections 39, 39 on the side of the first intermediate gear 31 facing the second intermediate gear 32. A cam groove 38 formed in the direction along the radial direction of the first intermediate gear 31 and the first intermediate gear 3 of the second intermediate gear 32;
The crank pin 36 is provided so as to protrude from the side surface facing the side 1 in a non-rotatable manner. The crank pin 36 is
The second intermediate gear 32 is disposed at an eccentric position with respect to the fourth axis X4, which is the rotation axis of the second intermediate gear 32, and is formed so as to slide freely into the cam groove 38 of the first intermediate gear 31. Thereby, the rotating case 10 is driven to rotate, and when the first intermediate gear 31 rotates around the third axis X3 due to the rotating operation by the rotating case 10 and the meshing with the sun gear 23, this rotating force is cranked. The pin 36 transmits to the second intermediate gear 32, and the second intermediate gear 32 rotates around the fourth axis X4. Since the third axis X3 and the fourth axis X4 are eccentric, the crank pin 36
Transmits the rotational force while reciprocatingly sliding inside the cam groove portion 38 in the radial direction of the first intermediate gear 31. Therefore, even if the first intermediate gear 31 rotates at a constant speed, the crank-type rotation transmission mechanism D rotates the second intermediate gear 32 at an unequal speed. The first intermediate gear 31 and the second intermediate gear 32 are unequally linked so that the intermediate gear 32 rotates in conjunction with the phase relationship M1 shown in FIG.

The relationship between the mounting positions of the sun gear 23, the first intermediate gear 31, the second intermediate gear 32, the planetary gear 30, and the rotating case 10 is shown by the phase relationship N1 shown in FIG. Is set so as to rotate relative to each other. Thereby, the relative rotation means S
Drives the pair of planting claw support cases 13 and 13 and the rotating case 10 to rotate relative to each other in a phase relationship N1 in FIG. 11 as the rotating case 10 is driven to rotate.
The pair of planting claw support cases 13 and 13 is caused to perform a planting movement in which the tip of the planting claw 12 draws a substantially elliptical locus T1 shown in FIG. 9. Note that when the phase of the planetary gear 30 changes in the negative direction, the planting claw support case 13 rotates in the ground rising direction U shown in FIG. 11, and when the phase of the planetary gear 30 changes in the positive direction. Then, the planting claw support case 13 rotates in the ground descending direction D shown in FIG.

As shown in FIG. 4, the seedling extruder 15
The planting claw support case 13 is fixed to one end of a support rod 15a that supports the planting claw supporting member 13 so as to slide along the planting claw 12. It is supported to move. As shown in FIGS. 2 and 4, the seedling pushing operation mechanism E includes a cam shaft 16 provided inside a planting claw support case 13 and a balance arm 2.
0, an extruding spring 22, a connecting rod 18 connected to an end of the camshaft 16 protruding from the implanted claw support case 13 to the outside, and the like. The camshaft 16 is supported by the planting claw support case 13 so as to be rotatable around the same axis as the second axis X2.
5 is provided integrally with a cam 17 for operating the same.
The balance arm 20 is supported by a support shaft 20 a of the planting claw support case 13.
Is rotatably supported. One end of the balance arm 20 is connected to the support rod 15 a by a link 19, and the other end of the balance arm 20 is provided with a cam follower 21 acting on the cam 17. The push-out spring 22 urges the balance arm 20 to swing by using the planting claw support case 13 as a reaction force member, thereby forming the support rod 15a.
Are slidably biased to the side protruding from the planting claw support case 13, and the cam follower 21 of the balance arm 20 is pressed against the peripheral surface of the cam 17. Connecting rod 18
Is mounted over the cam shaft 16 of the one planting claw support case 13 and the cam shaft 16 of the other planting claw supporting case 13, and the planting claw supporting case 13 rotates with respect to the rotating case 10. Also, the cam shaft 16 is supported so that the cam shaft 16 does not rotate with respect to the rotating case 10. As a result, the planting claw support case 13 and the camshaft 16 are relatively rotated as the planting claw 12 performs the planting movement,
The balance arm 20 is oscillated about the support shaft 20a for the pressing operation of the cam 17 against the cam follower 21 and the operation by the push-out spring 22 to slide the support rod 15a. Thus, the seedling pushing operation mechanism E is driven by the rotating force of the rotating case 10 as the seedling-claw 12 performs the seedling movement, and the seedling pushing tool 15 is moved as shown by the two-dot chain line in FIG. The pushing operation is performed by the operating force of the resilient restoring force of the pushing spring 22 to the working position located on the distal end side of the attached claw 12, or as shown by the solid line in FIG. The retraction operation is performed by the operation force of the cam 17 to the inoperative position located.

Therefore, when the rotating case 10 is rotationally driven, each of the seedling-claw supporting cases 13, 13 is rotated.
In addition to the orbital rotation around the first axis X1 for the rotation of 0, and the rotation about the second axis X2 due to the action of the relative rotation means S, the tip of the seedling-claw 12 is substantially elliptical. The seedling placement claw 12 is caused to perform a seedling movement so as to rotate up and down between the seedling removal opening of the seedling placement table 4 and the field along the locus T1. A seedling pushing operation mechanism E
Is driven by the rotational force of the rotating case 10 to move the seedling pushing tool 15 between the non-acting position and the acting position in conjunction with the seedling movement of the seedling-claw 12. As a result, the seedling mounting nails 12 of the one seedling mounting nail support case 13 and the seedling mounting nails 12 of the other seedling mounting nail support case 13 are alternately placed on the seedling mounting table 4. The block seedlings of one plant are cut and taken out from the seedlings, transported down to the field and planted on the same planting strip. Then, while each of the seedling-claws 12 is moved downward from the top of the seedling outlet of the seedling mounting table 4 to the seedling-planting position, the seedling pushing-out tool 15 is in the non-operating position and the seedling-claw 12 is removed. When the planted seedlings 12 reach the field and perform seedling planting, the seedling pushing tool 15 is in the operating position, and the planted planting claws 12 can be held.
The extruding operation is performed so that the seedlings held by the user can be easily separated from the seedlings 12.

The gear support shaft 50 is, as shown in FIG.
The first round shaft 51 having the shaft core X3 and the lightening hole 54 is located at one end, the second round shaft 52 having the shaft X4 and the lightening hole 54 is facing the other end, It is formed by a member formed so as to be provided with a connecting shaft portion 53 between them. The connecting shaft portion 53 has an outer diameter smaller than the outer diameters of the first round shaft portion 51 and the second round shaft portion 52 so as not to interfere with the crank pin 36, and The second round shaft portion 52 and the shaft center X of both shaft portions 51 and 52
3, X4 are formed so as to be connected in an eccentric state. End 5 of first round shaft 51 opposite to connecting shaft 53
1a is formed in a connecting portion configured to be inserted into a shaft mounting hole of the shaft supporting portion 10b of the half case portion 10A, and an end portion of the first round shaft portion 51 on the side where the connecting shaft portion 53 is located. 51b is formed in a gear supporting portion configured so that the first intermediate gear 31 is rotatably fitted to the outside. An end portion 52a of the second round shaft portion 52 opposite to the connection shaft portion 53 is formed as a connection portion configured to be inserted into a shaft mounting hole of the shaft support portion 10c of the half split case portion 10B, An end portion 52b of the second round shaft portion 52 on the side where the connecting shaft portion 53 is located is formed as a gear support portion configured so that the second intermediate gear 32 is rotatably fitted to the outside. In other words, the first round shaft portion 51 forms the first support shaft portion 51 for supporting the first intermediate gear 31 on the rotating case 10 so as to be rotatable around the third shaft center X3. The second support shaft portion 52 for supporting the second intermediate gear 32 on the rotating case 10 so as to be rotatable around the fourth shaft center X4 is formed. As a result, the gear support shaft 50 includes a connecting portion 51a formed at the end of the first round shaft portion 51 and a connecting portion 5 formed at the end of the second round shaft portion 52.
The first and second intermediate gears 31, 32 are supported in a state where both ends of the second gear 2a are connected to the rotating case 10 and are supported at both ends.

As shown in FIG. 8, the first support shaft 51,
The three shaft portions of the second support shaft portion 52 and the connection shaft portion 53 are formed as separate components. The connecting shaft portion 53 is provided with connecting shaft portions 53a at both ends, and both connecting shaft portions 53a,
A rod member having a spacer portion 53b having an outer diameter larger than both connecting shaft portions 53a, 53a is formed between the connecting shaft portions 53a, and one connecting shaft portion 53a of the connecting shaft portion 53 is The other connecting shaft portion 53 is inserted into the mounting hole 51c.
b is inserted into the assembling hole 52c of the second support shaft 52, and the three shafts of the first support shaft 51, the second support shaft 52, and the connection shaft 53 are combined. That is, the gear support shaft 50 is formed by combining three parts forming the three shaft portions 51, 52, and 53 separately. Spacer part 5
3b is a distance between the first support 51 and the second support 52,
If the crank pin 36 interferes with the first intermediate gear 31,
The interval is set so that the protrusion 39 does not interfere with the second intermediate gear 32.

The crank pin 36 is shown in FIGS.
As shown in the figure, a non-circular pin having a notch C on the outer periphery is formed. The notch portion C is a portion of the outer peripheral portion of the crank pin 36 facing the rotation axis X4 of the second intermediate gear 32, and does not contact the inner wall surface 38a of the cam groove portion 38. 31 and 32 at a position not involved in interlocking, and the rotation axis X of the second intermediate gear 32
It is formed in an arc shape with a radius R1 centered at 4. The radius R1 is the radius R of the shaft hole 32a of the second intermediate gear 32.
By making it larger than 2, the peripheral surface 36a at the notch portion C of the crankpin 36 is formed into an arcuate surface, and the radius R1 as the interval between the peripheral surface 36a and the rotation axis X4 is set to the above-mentioned value. It is formed larger than the radius R2 of the shaft hole 32a. As a result, the connecting shaft 53 of the gear support shaft 50 enters the notch C, and the connecting shaft 53 and the peripheral surface 36
a between the two intermediate gears 31, 3 while the crank pin 36 revolves around the connecting shaft 53a without abutting against the connecting shaft 53a of the gear support shaft 50.
Link 2

The connecting shaft 53 of the gear shaft 50 is provided with
And a shaft end 53c protruding from the end surface of the second support portion 52 opposite to the first support portion 51 side.
c into the shaft support portion 10c of the half case portion 10B so as to enter the shaft portion c, and the shaft end portion 53
c constitutes a positioning mechanism 57 for setting the mounting position of the gear support shaft 50 with respect to the rotating case 10.
That is, the two intermediate gears 31,
32, followed by a half-split case part 10A, 1
When the second support shaft portion 52 of the gear support shaft 50 is mounted on the shaft support portion 10c of the half-split case 10B when the seedling planting mechanism 5 is mounted by combining the shaft support portion 0B with the shaft end portion 53,
c is inserted into the recess 56 and engaged therewith. Then, since the shaft end portion 53c is eccentric from the fourth shaft center X4, the second support shaft portion 52 is moved with respect to the half case 10B due to the engagement between the shaft end portion 53c and the recessed portion 56. Even if it rotates by a slight angle due to the accommodation between the shaft end 53c and the recessed portion 56, the rotation is restricted so as not to rotate any more. The half-split case portion 10B at the time of the assembling operation is oriented such that the inner surface thereof faces upward, so that the rotational operation force caused by their gravity is less likely to act on the connection shaft 53 and the second support shaft portion 52. Further, the rotation of the connecting shaft portion 53 about the axis of the connecting shaft portion 53 with respect to the second support shaft portion 52 is restricted by friction between the two, and the second support shaft portion 51 is attached to the mounting hole 51 thereof.
The rotation about the connecting shaft portion 53 around the axis of c is restricted by the friction between them. For this reason, the positioning mechanism 57 sets the assembly position of the entire gear support shaft 50 in the circumferential direction of the gear support shaft with respect to the entire rotation case 10 by engaging the shaft end 53c with the recessed portion 56 as follows. That is, after assembling the intermediate gears 31 and 32 together with the gear support shaft 50 to the half case part 10B, the pair of half case parts 10A and 10B are connected to each other by the two case parts 10A and 10B.
When the connection bolt holes B are combined in a matching positional relationship, the connection portion 51a of the first support shaft portion 51 of the gear support shaft 50 is assembled.
And the gear support shaft mounting hole of the shaft support portion 10b of the half case 10A.

[Another embodiment] Crank type rotation transmission mechanism D
The cam groove 38 is provided on the side of the second intermediate gear 32 facing the first intermediate gear 31, and the first intermediate gear 31
A crank pin 36 eccentric from the rotation axis X3 of the first intermediate gear 31 is provided on the side surface facing the second intermediate gear 32, and the crank pin 36 applies the rotational force of the first intermediate gear 31 to the crank pin 36. The transmission to the cam groove portion 38 of the second intermediate gear 32 so that the second intermediate gear 32 rotates at a non-uniform speed around the fourth axis X4 even if the first intermediate gear 31 rotates at a constant speed. May be adopted.

[Brief description of the drawings]

FIG. 1 is a side view of the entire seedling planting apparatus.

FIG. 2 is a sectional view of a seedling planting mechanism.

FIG. 3 is a sectional view of a rotating case.

FIG. 4 is a sectional view of a planting nail supporting case.

FIG. 5 is a perspective view of the rotation transmitting mechanism in an exploded state.

FIG. 6 is a front view of a second intermediate gear.

FIG. 7 is a sectional view of a gear support shaft.

FIG. 8 is a perspective view of the gear support shaft in an exploded state.

FIG. 9 is an explanatory diagram of a seedling movement locus of a seedling-attached nail.

FIG. 10 is an explanatory diagram of an interlocking relationship between a first intermediate gear and a second intermediate gear.

FIG. 11 is an explanatory diagram of an interlocking relationship between a rotating case and a planetary gear.

FIG. 12 is a sectional view of a conventional seedling planting mechanism.

[Explanation of symbols]

 3 Planting Transmission Case 10 Rotating Case 12 Seedling Planting Claw 13 Planting Claw Support 14 Support Shaft 23 Sun Gear 30 Planetary Gear 31 First Intermediate Gear 32 Second Intermediate Gear 32a Support Shaft Hole 36 Crank Pin 36a Peripheral Surface 38 Cam Groove C Notch D Crank-type rotation transmission mechanism S Relative rotation means X1 First axis X2 Second axis X3, X4 Center T1 Elliptical locus R1 Interval R2 Radius

──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-8-266121 (JP, A) JP-A-6-133614 (JP, A) JP-B-49-17806 (JP, B1) (58) Field (Int.Cl. ⁷ , DB name) A01C 11/02 370-387

Claims (2)

(57) [Claims] 1. A seedling mounting claw that is rotatably supported about a second axis parallel to the first axis by a rotation case rotatably supported around a first axis relative to the planting transmission case. A planetary gear fixed to a support shaft that supports the planting claw support on which is mounted and that supports the planting claw support in a state in which the planting claw support rotates integrally, and is non-rotatably fixed to the planting transmission case. Sun gear, a first intermediate gear meshing with the sun gear, a second intermediate gear and a first intermediate gear that rotate about a rotation axis that is eccentric with the rotation axis of the first intermediate gear and mesh with the planetary gear. And an eccentric crank type rotation transmission mechanism that unequally interlocks the second intermediate gear with the second intermediate gear, with the rotation of the rotating case,
A seedling planting mechanism comprising relative rotation means for relatively rotating a planting claw support and a rotating case so that the tip of the seedling planting claw draws a substantially elliptical locus. A cam groove is provided in one intermediate gear of the gear and the second intermediate gear, and a crank pin that slides into the cam groove to interlock the first intermediate gear and the second intermediate gear is connected to the other intermediate gear. To form an eccentric crank type rotation transmission mechanism, wherein the crank pin is formed as a non-circular pin having a cutout portion at a portion of the outer peripheral portion facing the intermediate gear rotating shaft core. Seedling planting mechanism. 2. The space between the peripheral surface of the crank pin at the notch and the rotation axis of the intermediate gear is formed to be larger than the radius of a shaft hole of the intermediate gear. Seedling planting mechanism.