JP2006141262A - Pressurizing device of transplanter - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a pressurizing device for packing the upper surface of a ridge without damaging seedlings on the upper surface of the ridge by enabling the timing of upper and lower movements of a transplanting tine and a pressurizing body to be easily regulated. <P>SOLUTION: The pressurizing device of a sweet potato-seedling transplanter 1 has a pressurization-driving structure 35 for turning a pressurizing roller 34 in the upper and lower direction by being synchronized with the transplanting action of the transplanting tines 20L and 20R. The pressurization-driving structure 35 has an arm member 54 continuously rotatably driven in one direction, a cam member 55 connected and fixed to the arm member 54 and having a notched part formed at a part of a circumferential part 55a, an engaging arm 57 swingingly operated while contacting an engaging part 62 with the circumferential part 55a of the cam member 55, a link structure 36 linking the engaging arm 57 and the pressurizing roller 34 through a link rod 64, and a first regulating structure for regulating the timing of the upper and lower movement of the pressurizing roller 34 and the upper and lower movement for transplanting 20. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a pressing device for a transplanter, and more particularly, to a pressing device provided with a pressing drive mechanism that raises and lowers a pressing body intermittently relative to a transplanter body such as a sweet potato seedling transplanter.

  2. Description of the Related Art Conventionally, in a seedling transplanter for transplanting vegetable seedlings such as sweet potatoes, a configuration including a planting device that moves a planting claw up and down along a predetermined planting locus is known. With these planting claws, the seedling is pinched and grabbed, the seedling is released at the lowest position of the planting locus in the basket, and the seedling that has been grabbed is transplanted into the basket. In such a transplanter, a pressing device including a pressing body such as a pressing roller is disposed behind the planting claw of the transplanting unit. The pressing body of the pressing device presses or rolls the planting surface on the ridge after planting the seedling, thereby ensuring the retention of the seedling transplanted in the cocoon and improving the activity of the root of the seedling. It is configured.

  In Patent Document 1, when an engagement plate is engaged with a rotating cam member, a roll-like member as a pressing body attached to the arm tip via a link mechanism is raised, and the engagement with the cam member is released. A seedling transplanter has been proposed that includes a pressing device configured to drop a roll-shaped member under its own weight. This seedling transplanting machine interlocks the rotation of the cam member and the raising and lowering of the roll-shaped member, and intermittently drops the roll-shaped member by its own weight, so that the heel surface after transplanting the seedling by the planting claw is a roll-shaped member. It is made to squeeze and crush (refer patent document 1).

Further, in Patent Document 2, the driving force from the transmission case causes the driving shaft and the cam to rotate integrally, the swinging arm is swung via a roller, a rod, and the like, and a pressure attached to the tip of the swinging arm. A pressing device is disclosed in which a pressure-reducing wheel as a body is intermittently dropped on the upper surface of the heel. Also in this pressing device, the operation mechanism of the pressure reducing wheel is configured at the timing when the planting claw comes out of the bag just before the pressure reducing wheel falls on the upper surface of the bag (see Patent Document 2).
JP 2002-136205 A JP 2003-88212 A

  Certainly, according to the pressing device described in Patent Document 1 or Patent Document 2, the pressing body is intermittently moved up and down by the engagement state of the engagement plate or roller and the cam member, and the pressing body is It is preferable in that a seedling transplanted therein is not damaged, and a good suppression effect can be obtained.

  However, in the reciprocating mechanism from the seedling delivery position to the middle of the cocoon by the planting claw, and the pressing drive mechanism that causes the pressing body to fall to the upper surface of the cocoon after the planting claw releases the seedling in the cage and retreats upward. It was not easy to adjust the timing for interlocking the vertical movement of the nail and the pressing body. Therefore, once the timing of the vertical movement between the planting claw and the pressing body is shifted, the seedling may be damaged by the pressing body, or the seedling may not be held in the basket.

  That is, conventionally, in order to adjust the vertical movement timing of the planting claw and the pressing body, the constituent members such as the reciprocating mechanism and the pressing drive mechanism are replaced, or the mounting positions of the constituent members disposed inside the machine body are changed. It was necessary for the operator to make changes, which was troublesome for the operator. In particular, the timing of vertical movement between the planting claw and the pressing body may have to be finely adjusted during work depending on the state of the cocoon and the type of seedling when planting the seedling. Adjustment was difficult and workability was poor.

  Therefore, the present invention relates to a pressing device for a transplanter, which solves the above-described conventional problem, and makes it possible to easily adjust the timing of the vertical movement of the planting claw and the pressing body without damaging the seedling on the upper surface of the cocoon. An object is to propose a pressing device that suppresses the upper surface.

  The problem to be solved by the present invention is as described above. Next, means for solving the problem will be described.

  That is, in Claim 1, it is the pressing apparatus of the transplanter provided with the press drive mechanism which rocks the pressing body in the vertical direction in conjunction with the planting operation of the planting claw, and the press drive mechanism is unidirectional. An arm member that is continuously driven to rotate, a cam member that is connected and fixed to the arm member, and a notch is formed in a part of the circumferential surface, and a swing operation that abuts along the circumferential surface of the cam member An engaging arm, a link mechanism for connecting the engaging arm and the pressing body via a link arm, and an adjusting means for adjusting the vertical movement timing of the pressing body with respect to the vertical movement of the planting claw. Is.

  According to a second aspect of the present invention, the adjusting means rotates the cam member in the circumferential direction to relatively change the fixing position with the arm member.

  According to a third aspect of the present invention, the adjusting means includes a movable piece that changes a notch shape of the notch portion by changing an attachment position with respect to the cam member, and adjusts a length that the pressing body is grounded to the upper surface of the collar. To do.

  In Claim 4, it is arrange | positioned at the transplanting machine provided with the planting apparatus which can change the planting attitude | position of the seedling by the said planting nail | claw.

  As effects of the present invention, the following effects can be obtained.

  Since it is set as the structure shown in Claim 1, according to the cocoon state at the time of planting a seedling, the kind of seedling, etc., the timing of the vertical movement of the planting claw and the pressing body can be easily finely adjusted during the operation, and the pressing body The seedling can be sufficiently retained in the cocoon without damaging the seedling.

  Since it was set as the structure shown in Claim 2, the timing of the vertical movement of a planting nail and the vertical movement of a press body can be made to correspond substantially easily. In addition, by appropriately increasing or decreasing the timing of repression by the pressing body, the transplanted seedlings are not damaged, and the repression timing is delayed, so that the vicinity of the roots of the seedlings in the persimmon cannot be repressed and the seedlings in the reed Can not be held. Furthermore, since it is provided in the pressing drive mechanism configured in the pressing device, the accuracy of adjustment is high, and the adjustment work is easy for the operator.

  Since it was set as the structure shown in Claim 3, it can adjust the pressure suppression work by a press body by changing the length by which a press body is grounded on a cocoon upper surface, and it presses according to the state, the kind, size, etc. of a cocoon By changing the length of body suppression, the seedling in the cocoon can be held more fully, and the suppression effect can be improved. Moreover, since it is provided in the press drive mechanism comprised by a press apparatus, the precision of adjustment is high and adjustment work is easy for an operator.

  Since it was set as the structure shown in Claim 4, even if the timing of the vertical motion of a planting nail and a press body changes by changing the planting attitude | position of a planting nail, this can be finely adjusted easily.

Next, the best mode for carrying out the invention will be described with reference to the drawings.
1 is a side view showing an overall configuration of a sweet potato seedling machine provided with a pressing device according to an embodiment of the present invention, FIG. 2 is a plan view of the sweet potato seedling machine of FIG. 1, and FIG. 4 is a side view showing a moving path of a planting claw at the time of planting the ship bottom, FIG. 5 is a side view showing a reciprocating mechanism of the nail at the time of planting the ship bottom, and FIG. FIG. 7, FIG. 7 is a side view showing a moving path of the planting claw when obliquely planted, FIG. 8 is a side view of the pressing device, FIG. 9 is a plan view of the pressing device of FIG. 11 is a plan view of the pressing drive mechanism of FIG. 10, FIG. 12 is a side view showing a state in which the pressing roller presses the upper surface of the bag, and FIG. 13 is a side view showing a state in which the pressing roller is swung upward. FIG. 14 is a side view showing an attachment state of the arm member and the cam member in the first adjustment mechanism, and FIG. Side view showing the mounting state between the cam member and the movable piece in the second adjustment mechanism, FIG. 16 is a plan view showing another embodiment of a support structure of the pressure roller.

  Hereinafter, as a transplanter, a sweet potato seedling machine 1 for grasping a sweet potato seedling placed on the seedling carrier 12 with the planting claws 20L and 20R and planting it in a cocoon will be described. However, the transplanter is not limited to this.

First, the overall configuration of the sweet potato seedling machine 1 will be outlined below.
As shown in FIGS. 1 and 2, the sweet potato seedling machine 1 is a walking self-propelled working machine that automatically plants sweet potato seedlings (hereinafter referred to as seedlings) in the cocoon while running along the cocoon. A pair of left and right front wheels 2, 2 and rear wheels 3, 3 traveling in the valley portion 17, and a traveling machine body 4 positioned above the eaves are disposed. The main frame of the traveling machine body 4 is configured by connecting and fixing a front engine frame 5, a central transmission case 6 and a rear handle frame 7 in the front-rear direction. The device is supported.

  The traveling machine body 4 includes, as the various devices, a saddle guide device 8, a front wheel support device 9, an engine 10, a rear wheel support device 11, the transmission case 6, and a saddle height detection device 16 from the front to the rear in the traveling direction. The seedling carrier 12, the planting device 13, the pressing device 14, and the operation unit 15 are provided. In these various devices, the device disposed on the front side of the mission case 6 is supported by the engine frame 5, and the device disposed on the rear side of the mission case 6 is supported by the handle frame 7.

  Next, the configuration of each apparatus will be described below with reference to FIGS.

<畝 guide device 8>
The cocoon guide device 8 is a device for guiding the traveling direction of the sweet potato seedling machine 1 that travels along the cocoon, and a pair of left and right cocoon guide rollers 8a and 8a for contacting the left and right side surfaces (slopes) of the cocoon. I have. By holding the cocoon between these cocoon guide rollers 8a and 8a, or rolling while making contact with the inclined surface, the sweet potato seedling machine 1 is driven in this state, thereby controlling the direction of the sweet potato seedling machine 1 by driving operation. It is possible to run along the ridge without doing.

<Front Wheel Support Device 9 and Rear Wheel Support Device 11>
The front wheel support device 9 includes a front wheel support shaft 9a that is fixed to the engine frame 5, and front wheel arms 9b and 9b that are rotatable about the front wheel support shaft 9a and support the front wheels 2 and 2. The rear wheel support device 11 is configured in the same manner as the front wheel support device 9, and includes a rear wheel support shaft 11a fixed to the transmission case 6 and a rear wheel support shaft 11a that is rotatable around the rear wheel support shaft 11a. Supporting chain cases 11b and 11b are provided. A drive shaft for the rear wheels 3 and 3 is built in the rear wheel support shaft 11a, and the rotational drive of the drive shaft is applied to each rear wheel 3 and 3 via a chain in the chain case 11b. Communicated.

  The front wheel arm 9b and the chain case 11b are connected via a connecting shaft (not shown), and the front wheel arm 9b and the chain case 11b are configured as parallel links. When the front wheel arm 9b or the chain case 11b is rotated, the vertical height of the traveling machine body 4 with respect to the front wheels 2 and 2 and the rear wheels 3 and 3 is variable. As a means for rotating the chain case 11b with respect to the traveling machine body 4, an actuator 19 is provided for connecting and shortening the engine frame 5 and the chain case 11b. When the actuator 19 is extended and contracted, the parallel link is operated, and the traveling machine body 4 is moved up and down with respect to the front wheels 2 and 2 and the rear wheels 3 and 3. By comprising in this way, the height position with respect to the collar upper surface 18 of the traveling body 4 can be adjusted.

<Head height detection device 16>
The heel height detection device 16 includes a sensor roller 16a that contacts the heel surface 18 and a sensor arm 16b that supports the sensor roller 16a and is provided rotatably on the engine frame 5. In response to the tilt of the sensor arm 16b, the spool of a hydraulic valve (not shown) is pushed and pulled to control the operation of the hydraulic actuator 19, and the separation distance between the engine frame 5 and the upper surface 18 is constant. Thus, the height position of the traveling machine body 4 is controlled so as to be maintained. The vertical movement of the traveling machine body 4 is performed based on the detection of the kite height by the kite height detection device 16.

  In addition to the actuator 19, an actuator (not shown) for rotating (tilting) one of the left and right chain cases 11b with respect to the other chain case 11b is provided. It is configured to be possible.

<Seedling carrier 12>
The seedling transport stand 12 is a device that automatically transports and supplies seedlings stored in a seedling storage case (not shown) to the planting claws 20L and 20R provided in the planting device 13. The seedling transport table 12 is provided with an endless belt-shaped transport belt 21 that rotates counterclockwise in the front-rear direction, and a pair of resin materials made of an elastic body such as a sponge are disposed oppositely on the outer periphery of the transport belt 21. The holding portions 22 thus formed are arranged at equal intervals as means for holding the seedlings. The upper surface of the conveyor belt 21 is a mounting portion that holds the seedling taken out from the seedling storage case, and the lower end position of the conveyor belt 21 is a delivery position 21d that takes over the seedling to the planting claws 20L and 20R. The seedling carrier 12 is configured such that power from the PTO shaft of the transmission case 6 is transmitted, and the conveyor belt 21 is intermittently rotated in conjunction with the planting device 13 described later. Yes.

<Planting device 13>
As shown in FIGS. 3 and 4, the planting device 13 includes a pair of left and right planting claws 20L and 20R, and a claw reciprocation mechanism 24 that reciprocates the planting claws 20L and 20R from the delivery position 21d to the center of the cage. ing. The planting claws 20L and 20R transplant the seedlings delivered from the delivery position 21d of the seedling carrier 12 into the cage and hold the seedlings by holding and separating the left and right planting claws 20L and 20R. It is configured so that it can be released. The uppermost position of the reciprocating movement of the planting claws 20L and 20R is the delivery position 21d. The planting claws 20L and 20R sandwich and hold the seedlings at the delivery position 21d, and the lowest position of the reciprocating movement in the cage. The seedlings are transplanted into the cage by releasing the seedlings at the position and retreating upwards.

  The claw reciprocating mechanism 24 is configured as a crank mechanism that converts the rotational movement of the planting drive shaft 25 into the reciprocating movement of the planting claws 20L and 20R from the seedling carrier 12 into the cocoon. Power from the PTO shaft of the mission case 6 is transmitted to the planting drive shaft 25. The claw reciprocating mechanism 24 includes a first link arm 26 that rotates integrally with the planting drive shaft 25, and a second link arm 28 that is rotatably provided on the attitude adjustment shaft 27.

  The attitude adjustment shaft 27 is fixed to the handle frame 7 via a support member, and is disposed above the planting drive shaft 25. Both shafts are disposed in the left-right direction. A first fulcrum shaft 29 is fixed to the tip of the first link arm 26, and a second fulcrum shaft 30 is fixed to the tip of the second link arm 28. The first fulcrum shaft 29 and the second fulcrum shaft 30 pivotally support the claw support case 31 that supports the planting claws 20L and 20R, respectively. Even if the first fulcrum shaft 29 and the second fulcrum shaft 30 are rotatable with respect to the claw support case 31, the first fulcrum shaft 29 and the second fulcrum shaft 30 are fixed to the claw support case 31. The distance to the fulcrum shaft 30 is always constant. The distance from the planting drive shaft 25 to the first fulcrum shaft 29 and the distance from the posture adjustment shaft 27 to the second fulcrum shaft 30 are also constant.

  When the planting drive shaft 25 is rotated, the claw support case 31 rotates around the planting drive shaft 25 and the posture of the claw support case 31 changes. That is, since the distance from the first fulcrum shaft 29 to the second fulcrum shaft 30 is constant, the second link arm 28 is moved to the posture adjusting shaft 27 along with the revolution of the claw support case 31 (rotation around the planting drive shaft 25). A reciprocating motion is performed on the surrounding circular arc trajectory, and the relative position between the first fulcrum shaft 29 and the second fulcrum shaft 30 changes. For this reason, the attitude | position of the nail | claw support case 31 changes and the attitude | positions of the planting nail | claw 20L * 20R change.

  By the claw reciprocating mechanism 24, the tips of the planting claws 20L and 20R reciprocate along an outer circumferential path R1 of a substantially crescent moon (see FIG. 3). And the tip of the planting claws 20L and 20R when planting while running the main body is a movement by the claw reciprocating mechanism 24 (reciprocating movement of the outer periphery of the crescent moon) and a movement by the traveling of the sweet potato seedling machine 1 (linear movement) Are combined to form an “α” -shaped route R2 that intersects at one point along the moving route (see FIG. 4).

  The intersection position P1 of the route R2 is moved up and down by changing the traveling speed of the sweet potato seedling machine 1 at the time of planting, and the traveling speed of the sweet potato seedling machine 1 is such that the intersection position P1 is located near the upper surface 18 of the pod. Is set. By setting it as such a structure, the opening width in the heel surface 18 of a planting hole is made small. In planting multi-film laid ridges, as the opening width of the planting hole (opening width of the heel surface) becomes smaller, the cut width of the multi-film at the time of planting can be reduced. In particular, when the planting claws 20L and 20R enter the heel and the exit positions from the heel substantially coincide with each other, a cutting blade (not shown) provided at the tip of the planting claws 20L and 20R is used to If the multi-film on the surface is cut, there is no problem even when leaving. That is, there is no need to separately install a multi-film cutting device to prevent the planting claws 20L and 20R from being caught by the multi-film.

  The planting claws 20 </ b> L and 20 </ b> R are substantially V-shaped with one side being three times longer than the other side, and are portions that enter into the cage as the first link arm 26 rotates. It is comprised with the part connected to the inside link. The planting claws 20L and 20R are moved from the open position to the closed position at the uppermost position of the reciprocating movement, and the seedlings are grasped from the seedling transport table 12, and are moved from the closed position to the opened state at the lowermost position of the reciprocating movement. Open and close to release the seedlings in the cage.

  With the above configuration, the planting holes are formed only inside the cocoon by the planting claws 20L and 20R, and the cocoon upper surface 18 is not torn in the front-rear direction, and the planting hole in the cocoon upper surface 18 is formed. The opening width is minimized. Therefore, when seedling transplantation is performed using the planting claws 20L and 20R, the seedling is not exposed from the soil, and the seedling is reliably planted.

<Planting posture switching mechanism>
This sweet potato cutting seedling machine 1 is configured to change the planting posture of the seedling. Specifically, the claw reciprocating mechanism 24 can switch the reciprocating path of the planting claws 20L and 20R in a plurality of patterns. It is configured. The path of the reciprocating motion of the planting claws 20L and 20R is determined by the following three positional relationships. That is, the positional relationship between the position of the first fulcrum shaft 29, the position of the second fulcrum shaft 30, and the position of the attitude adjustment shaft 27 that gives the swing range of the second fulcrum shaft 30. By changing these relative positions, seedlings can be planted in different planting postures. Specifically, the planting posture of the seedling is “planting the seedling” so that the seedling is laid sideways like the shape of one end of the bottom of the ship, and the seedling is planted along an oblique direction (for example, 45 ° direction). It is configured so that it can be switched to "diagonal planting".

  The claw reciprocating mechanism 24 is provided with a configuration for changing the positions of the second fulcrum shaft 30 and the posture adjusting shaft 27 as means for changing the reciprocating motion path. One is a configuration that allows the attachment position of the second fulcrum shaft 30 to the claw support case 31 to be changed. The other is a configuration in which the attachment position of the attitude adjustment shaft 27 with respect to the handle frame 7 can be changed.

  As shown in FIG. 5, the claw support case 31 is formed by sequentially connecting and fixing the following three parts, an opening / closing mechanism case 37, a boss 38, and a posture adjusting plate 39 in a substantially straight line. The opening / closing mechanism case 37 includes a link mechanism for opening and closing the planting claws 20L and 20R. The boss 38 has a built-in bearing for rotatably supporting the first fulcrum shaft 29. The posture adjusting plate 39 is formed with a mounting long hole 39a and a mounting hole 39b as means for enabling the mounting position of the second fulcrum shaft 30 to be changed. In a state where the second fulcrum shaft 30 is inserted into the attachment long hole 39a or the attachment hole 39b, the second fulcrum shaft 30 can be pivotally supported on the posture adjusting plate 39 by a bolt or the like. The long mounting holes 39a and the mounting holes 39b are arranged so as to be gradually separated from the axial center of the boss 38, and are provided at positions rotated by a predetermined angle counterclockwise around the boss 38.

  Since the attachment long hole 39a is opened to the long hole, the attachment position of the second fulcrum shaft 30 with respect to the attitude adjustment plate 39 is continuously set by inserting the second fulcrum shaft 30 into the attachment long hole 39a. It can be changed and positioned. The mounting position of the second fulcrum shaft 30 can be positioned and fixed at three positions in the mounting elongated hole 39a, and positioning holes 39c, 39d, and 30e are formed at the end of the posture adjusting plate 39 on the side opposite to the boss 38, A positioning plate 40 is attached to this. In the positioning plate 40, positioning holes 40d are formed so as to correspond to the plurality of positioning holes 39c, 39d, and 30e provided in the posture adjusting plate 39.

  By positioning the positioning plate 40 around the first fulcrum shaft 29, one of the positioning holes 39c, 39d, and 30e is aligned with the positioning hole 40d, and each positioning hole is simultaneously inserted using the pin 43 to adjust the posture. The positioning plate 40 can be positioned and fixed with respect to the plate 39. In this way, the positioning plate 40 can be attached to the posture adjusting plate 39 in three different postures.

  The posture adjusting plate 39 and the positioning plate 40 are respectively formed with insertion holes so that the second fulcrum shaft 30 can be inserted through the posture adjusting plate 39 and the positioning plate 40 at the same time according to the three mounting postures described above. ing. The insertion holes formed in the posture adjustment plate 39 are the attachment long holes 39a and the attachment holes 39b. The insertion holes formed in the positioning plate 40 are a receiving long hole 40a and a receiving hole 40b. The receiving long hole 40a corresponds to the mounting long hole 39a, and the mounting hole 39b corresponds to the receiving hole 40b.

  When the positioning plate 40 is positioned at any one of the three positions described above with respect to the attitude adjustment plate 39, a joining portion between the receiving long hole 40a and the mounting long hole 39a is formed, and through this joining portion, The second fulcrum shaft 30 can be inserted. Depending on the positioning of these three locations, the formation lengths of the receiving long hole 40a and the mounting long hole 39a are formed so that different joining portions are formed between the receiving long hole 40a and the mounting long hole 39a. The sheath forming direction is appropriately set. In particular, when the positioning plate 40 is positioned with respect to the posture adjusting plate 39 by one of the three positions, the positioning hole 39e, the receiving hole 40b and the mounting hole 39b overlap, and the overlapping both holes are interposed. Thus, the second fulcrum shaft 30 can be inserted.

  As shown in FIGS. 5 and 6, the attitude adjustment shaft 27 is fixed to the handle frame 7 at any of a plurality of attachment positions, specifically, fixed to one end portion of the support arm 41. The other end of the support arm 41 is attached and fixed to a support plate 42 fixed to the handle frame 7, and the support plate 42 is provided with a plurality of attachment positions of the support arm 41. An insertion hole (not shown) formed in the support arm 41 is positioned by inserting pins 44 and 44 in accordance with the insertion hole (not shown) of the support plate 42, so that the support arm 41 is positioned with respect to the support plate 42. It can be positioned and fixed in two ways. Specifically, one mounting position is disposed above the planting drive shaft 25 (see FIG. 5), and the other mounting position is obliquely above and below the planting drive shaft 25, that is, opposite to the planting claws 20L and 20R. (See FIG. 6).

  As described above, the claw reciprocating mechanism 24 can change the attachment position of the second fulcrum shaft 30 to the claw support case 31 at four places, and can attach the attitude adjustment shaft 27 to the handle frame 7 at two places. It can be changed. Note that there are a total of eight possible patterns of reciprocating movements of the planting claws 20L and 20R that combine these mounting positions. In particular, in the sweet potato cutting seedling machine 1, four patterns are particularly effective planting postures. is there.

  As shown in FIG. 4 and FIG. 5, the case where the planting posture is “bottom planting” will be described. In such a case, the posture adjustment shaft 27 is the first fulcrum among the mounting positions that can be changed at two locations. It is attached at a position close to the shaft 29. When the first fulcrum shaft 29 and the posture adjustment shaft 27 approach each other, the posture change width (the swing width in the front-rear and vertical directions) of the planting claws 20L and 20R becomes larger. As an example, FIG. 4 shows a path of reciprocating movement of the planting claws 20L and 20R in the case where the second fulcrum shaft 30 is attached to the joining portion described above. As the distance from the junction to the first fulcrum shaft 29 becomes shorter, the movement path of the planting claws 20L and 20R in ship bottom planting becomes gentler, and the intersection position in the α-shaped path descends and approaches the surface of the ridge. It is supposed to be.

  As shown in FIGS. 6 and 7, the case where the planting posture is “oblique planting” will be described. In such a case, the posture adjustment shaft 27 is the first fulcrum shaft out of the mounting positions that can be changed at two locations. It is attached to a position far from 29. When the first fulcrum shaft 29 and the posture adjustment shaft 27 are separated from each other, the posture change width (the swing width in the front-rear and vertical directions) of the planting claws 20L and 20R becomes smaller. As an example, FIG. 7 shows a reciprocating path of the planting claws 20L and 20R when the mounting position of the second fulcrum shaft 30 is the mounting hole 39b. In such a case, since the forward path and the return path of the above-described reciprocating path substantially coincide with each other, the opening width of the planting hole formed in the basket by the planting claws 20L and 20R is minimized.

  With the configuration as described above, it becomes possible to plant sweet potato seedlings in a plurality of planting postures in a single sweet potato seedling seedling machine 1. For example, the planting postures of the seedlings are “bottom planting” and “diagonal planting”. ”Can be switched to improve planting workability. That is, by providing a mechanism that can change the planting posture of seedlings, it is possible to perform planting work according to various conditions such as the cocoon state, seedling type / size, and climate.

<Pressing device 14>
The pressing device 14 is configured to press the heel upper surface 18 into which the planting claws 20L and 20R are inserted, to break the planting holes formed by the planting claws 20L and 20R, and to ensure that the seedling is held in the cage. Is done. As shown in FIG. 8 and FIG. 9, the pressing device 14 includes a pressing roller 34 as a pressing body that is brought into contact with the heel surface 18, and the pressing roller 34 is moved up and down in conjunction with seedling transplantation by the planting claws 20 </ b> L and 20 </ b> R. A pressing drive mechanism 35 that is moved, a link mechanism 36 that links the pressing roller 34 in a swingable manner by the pressing drive mechanism 35, and the like are provided.

  A main frame 50 is disposed on the handle frame 7 on the left side of the body of the claw reciprocating mechanism 24, and a vertical surface 50a of the main frame 50 is disposed substantially parallel to the longitudinal direction of the body. A cover member (not shown) is detachably attached to the machine body side (left side) of the main frame 50. The press drive mechanism 35 is surrounded by a cover body formed by the main frame 50 and the like, and is configured so that sand, mud, and the like are not mixed into the press drive mechanism 35. A swing arm 56 is pivotally supported on the main frame 50. The swing arm 56 is swingable in the vertical direction from the pressing drive mechanism 35 via the link mechanism 36, and has a substantially cylindrical pressing roller 34 at the tip. Is attached (see FIGS. 9 and 16).

  The pressing device 14 is connected to a chain case 51 for the pressing device 14 installed in the rearward direction from the transmission case 6 (see FIG. 2). Specifically, the rear end portion of the chain case 51 is the above-described one. It is inserted inside the cover body. The output shaft 52 protrudes laterally from the rear side surface of the chain case 51, and the protruding end portion from the chain case 51 is connected to the drive shaft 53 of the pressing drive mechanism 35. The drive shaft 53 is supported by the chain case 51 and the output shaft 52 so as to be substantially horizontal to the vertical surface 50 a of the main frame 50. Power from the engine is transmitted from the output shaft 52 to the drive shaft 53 via a power transmission belt (not shown) in the chain case 51, and the pressing drive mechanism 35 is driven.

  The pressing drive mechanism 35 includes the drive shaft 53, an arm member 54 fixed to the drive shaft 53 so as not to rotate relative to the drive shaft 53, and a drive shaft 53 coaxial with the arm member 54. A cam member 55 that is freely fitted to a position, and an engagement arm that is positioned further outside the body than the arm member 54 and the cam member 55 and swings in the vertical direction along the circumferential surface of the cam member 55. 57 and so on. The arm member 54, the cam member 55, and the engagement arm 57 are disposed substantially in parallel along the longitudinal direction of the machine body.

  Then, the pressing drive mechanism 35 changes the mounting position of the cam member 55 with respect to the arm member 54 as an adjusting means for adjusting the vertical movement timing of the pressing roller 34 with respect to the vertical movement of the planting claws 20L and 20R. The first adjusting mechanism 46 that adjusts the timing of the vertical movement of the pressing roller 34 and the notch shape of the notched portion 55b formed in the cam member 55 are changed so that the contact length of the pressing roller 34 to the collar upper surface 18 is increased. A second adjustment mechanism 47 for adjustment is configured. Details of the first adjustment mechanism 46 and the second adjustment mechanism 47 will be described later (see FIGS. 14 and 15).

  As shown in FIGS. 10 and 11, the arm member 54 is formed in a substantially oval shape when viewed from the side, and has an insertion hole 54a formed on the base side, and the drive shaft 53 is inserted through the insertion hole 54a, so that relative rotation is impossible. Is fixed. Thus, by fixing the arm member 54 and the drive shaft 53, the arm member 54 is configured to continuously rotate in a fixed direction (leftward in FIG. 10) in conjunction with the drive shaft 53. The arm member 54 extends in the radial direction of the drive shaft 53, a mounting hole 54 b is formed at the tip, a positioning bolt 58 is inserted into the mounting hole 54 b, and the bolt 58 is fastened by a nut 59. . The attachment hole 54b is formed at a position where the arm member 54 and the cam member 55 overlap in a side view.

  The cam member 55 is formed with a circumferential portion 55a formed in a substantially arc shape by partially cutting a disk, and a cutout portion 55b formed by cutting out from the circumferential portion 55a in the inner circumferential direction. In the cam member 55, the circumferential portion 55a has a substantially arcuate shape with the drive shaft 53 as the center, a through hole 55c is formed at the center, and the drive shaft 53 is inserted into the through hole 55c to drive the cam member 55. The shaft 53 is loosely fitted so as to be rotatable relative to the shaft 53. The cutout portion 55b includes a vertical portion 55f cut vertically from an intersection with the circumferential portion 55a in the radial direction (rotational axis direction), and a gentle radial direction from the vertical portion 55f toward the circumferential portion 55a. An inclined surface 55g that is curved and cut out in a convex shape is formed. The cam member 55 is provided with a movable piece 61 that changes the mounting position to change the notch shape of the notch portion 55b. The slope 61d of the movable piece 61 constitutes the slope portion 55g of the cam member 55. (See FIG. 15).

  The cam member 55 is provided with an arc-shaped long hole 55d centered on the drive shaft 53. The long hole 55d is formed at a position and shape where the bolt 58 can be inserted into the mounting hole 54b. The cam member 55 is fixed to the arm member 54 by fastening a bolt 58 to the mounting hole 54b of the arm member 54 through the long hole 55d. As described above, the cam member 55 and the arm member 54 are integrally connected by the bolt 58, so that the cam member 55 is rotationally driven in the same direction as the arm member 54 with the drive shaft 53 as the rotation center. It is configured as follows. The details of the mounting structure of the cam member 55 to the arm member 54 will be described later (see FIG. 14).

  The engaging arm 57 is pivotally supported by a support shaft 50b whose lower end protrudes substantially horizontally from the lower portion of the vertical surface 50a of the main frame 50. The engagement arm 57 extends upward from the lower end portion, is located on the outer side of the machine body with respect to the arm member 54 and the cam member 55, and is disposed so as to be substantially parallel thereto. An engagement portion 62 protrudes from the substantially upper and lower middle portion of the engagement arm 57 toward the inside of the machine body, and the engagement portion 62 is in contact with the circumferential portion 55a of the cam member 55 at a substantially right angle. The engaging portion 62 can be constituted by a roller or the like to reduce the resistance.

  The engaging portion 57 is in sliding contact with the engaging portion 62 along the circumferential surface 55 a of the cam member 55 by the rotational drive of the cam member 55. The position of the engagement arm 57 is set as a position P4 (see FIG. 8). While the engagement arm 57 maintains the state at the position P4, when the engagement portion 62 eventually reaches the vertical portion 55f of the notch portion 55b, the engagement between the engagement portion 62 and the cam member 55 is temporarily released. As a result, the support shaft 50b is swung back (rightward in FIG. 10) about the swing center, and the engaging portion 62 is engaged with the slope portion 55g (see FIG. 12). As the cam member 55 is driven to rotate, the engaging portion 62 is slid along the inclined surface portion 55g, and the engaging arm 57 is gradually swung forward (leftward in FIG. 10). Return to P4 (see FIG. 13). In the cam member 55, when the engaging portion 62 of the engaging arm 57 reaches the vertical portion 55f, the engagement between the engaging portion 62 and the cam member 55 is not released, and the engaging portion 62 becomes the vertical portion. The vertical portion 55f may be formed so as to slide along the slope of 55f. However, it is also possible to dispose the engaging portion 62 on the side surface of the swing arm 56 on the base side, and to dispose the cam member 55 below and behind it.

  Returning to FIGS. 10 and 11, the link mechanism 36 is connected to the link rod 64 whose end is pivotally supported by the upper end of the engagement arm 57 and the other end of the link rod 64. The swing arm 56 that is swingably fixed to the main frame 50 and the swing arm 56 that is engaged with the swing arm 56 and that is swung upward and downward is biased downward. The urging arm 65 and the like are configured.

  The link rod 64 has an insertion hole 64 a formed at the upper end portion, and the pin shaft 66 communicates with the insertion hole 64 a and the attachment hole 57 a formed at the upper end portion of the engagement arm 57. In this way, the upper end portion of the link rod 64 is pivotally supported by the engagement arm 57 so as to be swingable in the vertical direction. Further, an insertion hole 64 b is formed in the lower end portion of the link rod 64, and the pin shaft 68 is communicated with the insertion hole 64 b and the attachment hole 67 a of the attachment stay 67 provided in the swing arm 56. In this way, the lower end portion of the link rod 64 is pivotally supported by the swing arm 56 so as to be swingable. That is, the engagement arm 57 and the swing arm 56 are connected by the link rod 64, and when the engagement arm 57 swings in the vertical direction, the swing arm 56 is interlocked via the link rod 64 to move up and down. Rocks in the direction.

  The swing arm 56 is pivotally supported by a support shaft 50c having one end projecting from the vertical surface 50a of the main frame 50 in a substantially horizontal direction, and from the cover body formed by the main frame 50 or the like to the rear of the machine body. It is extended toward the. The swing arm 56 is formed in a substantially crank shape in plan view, extends from the support shaft 50c along the longitudinal direction of the aircraft, and then bends toward the inside of the aircraft, and then bends toward the longitudinal axis of the aircraft again at the other end. It is bent along (see FIG. 9). A roller shaft 69 is disposed at the other end, and the pressing roller 34 is pivotally supported on the roller shaft 69. The pressing roller 34 is formed in a substantially cylindrical shape, is rotatably supported by a roller shaft 69, and is configured to be able to roll in accordance with the forward movement of the machine body while being in contact with the upper surface 18 ( (See FIG. 9).

  As shown in FIG. 9, the swing arm 56 is attached to only one end of the roller shaft 69, and the pressing roller 34 is supported on the roller shaft 69. A pair of swing arms 56 and 56 formed in substantially the same shape may be attached to both ends of the shaft 69, and the pressing roller 34 may be supported on the roller shaft 69. In such a case, one of the swing arms 56, 56 constitutes the pressing drive mechanism 35, and the other is pivotally supported by the handle frame 7 or the like.

  The swing arm 56 can swing up and down with the support shaft 50c as the center of swing, and the pressing roller 34 disposed at the tip is moved up and down. At this time, the swing arm 56 is linked to the engagement arm 57 by the link rod 64 as described above, and the lowest position and the highest position in the vertical direction are regulated by the link rod 64. Hereinafter, the state where the pressing roller 34 disposed on the swing arm 56 is at the lowest position is referred to as the lowest position P2 of the swing arm 56 (see FIG. 12), and the state where the pressure roller 34 is at the uppermost position is the swing arm. The uppermost position P3 is 56 (see FIG. 8).

  The lowest position P2 and the highest position P3 of the swing arm 56 are determined by changing the size and shape of each member such as the link rod 64 and the swing arm 56. In the pressing device 14, the lowest position P <b> 2 of the swing arm 56 is adjusted to a position where the lower surface of the pressure roller 34 attached to the swing arm 56 sinks from the upper surface 18 into the bag by the maximum depth L <b> 1. . The maximum depth L1 varies in size depending on the heel state. By adjusting the lowest position P2 so that the pressing roller 34 sinks into the cocoon, the pressing roller 34 that is dropped onto the cocoon upper surface 18 surely presses the cocoon after seedling transplantation by the planting claws 20L and 20R. Further, by interlocking the pressing roller 34 along the heel surface 18, the seedling transplanted in the cocoon can be reliably held and the root activity of the seedling can be improved. On the other hand, the uppermost position P3 of the swing arm 56 is adjusted so that the lower surface of the pressing roller 34 is higher than the vertical height of the seedling transplanted on the heel surface 18.

  As shown in FIGS. 8, 11, and 12, the urging arm 65 is formed in a substantially L shape in plan view, and one end thereof is pivotally supported on the vertical surface 50 a of the main frame 50 so as to be swingable in the vertical direction. The bent portion 65a is bent substantially perpendicularly to the rear of the machine body, and the other end extends from the cover body formed by the main frame 50 or the like to the rear of the machine body. The other end portion of the urging arm 65 is engaged with an engagement portion 70 formed at a substantially midway portion in the front and rear direction of the swing arm 56.

  The engaging portion 70 includes an attachment member 70a protruding upward from the swing arm 56, and a connection member 70b attached to protrude from the attachment member 70a toward the inside of the machine body. The connection member 70b is pivotally supported by the attachment member 70a so as to be able to rotate back and forth. A through hole 70c is formed in a protruding portion from the mounting member 70a so as to penetrate in the vertical direction, and the other end portion of the urging arm 65 is slidably inserted into the through hole 70c. When the swing arm 56 is moved up and down, the urging arm 65 is slid through the through hole 70c of the connection member 70b, and the connection member 70b is rotated in the front-rear direction. The urging arm 65 is oscillated in the vertical direction around the pivotal support portion with the vertical surface 50a in conjunction with the vertical movement of the oscillating arm 56.

  A stopper member 71 is attached to the protruding portion at the other end of the urging arm 65 penetrating the connecting member 70b. By providing the stopper member 71, in particular, even when the swing arm 56 is suddenly operated from the uppermost position P3 to the lowermost position P2, the stopper member 71 comes into contact with the connecting member 70b and the urging arm 65 is moved. Does not escape from the through hole 70c.

  In the urging arm 65, an urging spring 72 is interposed between the bent portion 65 a and the engaging portion 70. The upper end of the biasing spring 72 is in contact with a stop member 73 fixed to the biasing arm 65, and the lower end of the biasing spring 72 is in contact with a stop member 74 that is slidably fitted along the biasing arm 65. (See FIG. 10). The urging spring 65 is in the most extended state when the swing arm 56 is in the lowest position P2. (See FIG. 12). On the other hand, in the state where the swing arm 56 is at the uppermost position P3, the stop member 74 abuts on the engaging portion 70 and is pressed upward, that is, the swing arm 56 is biased downward by the biasing spring 72. (See FIG. 8).

  As described above, the biasing arm 65 with the biasing spring 72 interposed therebetween biases the swing arm 56 downward, so that the pressing roller 34 not only falls by its own weight, but also the swing arm 56. Can be reliably swung downward, and the pressure roller 34 can be reliably crushed by the pressing roller 34. The arrangement of the urging spring 62 is not limited to the above-described configuration. For example, even when the swing arm 56 is in the lowest position P2, the stop member 74 is in contact with the engaging portion 70. The swing arm 56 may be always biased downward by the biasing spring 62 regardless of its vertical position. Further, the structure for attaching the urging spring 72 to the urging arm 65 is not limited to the above-described structure.

  In the pressing device 14 configured as described above, a pressure reducing operation of the upper surface 18 by the pressing roller 34 will be described. The nail reciprocating mechanism 24 causes the planting claws 20L and 20R to pinch and grab the seedling at the delivery position 21d, release the seedling at the lowest position of the reciprocating motion in the cage, retreat upward, and place the seedling into the cage. It is reciprocated to transplant. Therefore, the pressure roller 34 falls from above so that the planting claws 20L and 20R strike the upper surface 18 immediately after transplanting the seedlings into the cage and suppresses the pressure, and interlocks with the reciprocation of the planting claws 20L and 20R. It is swung up and down.

  In the state of the pressing device 14 shown in FIG. 8, the cam member 55 is continuously rotated in a fixed direction by the arm member 54 in the pressing drive mechanism 35. The engagement portion 70 of the engagement arm 57 is slidably contacted along the circumferential portion 55a of the cam member 55, and the engagement arm 57 is stopped in a state at the position P4. The swing arm 56 is held at the uppermost position P <b> 3 pulled upward by a link rod 64 pivotally supported by the upper end portion of the engagement arm 57. Further, in a state where the swing arm 56 is at the uppermost position P3, the swing arm 56 is biased downward by a biasing spring 72 interposed in the biasing arm 65.

  As shown in FIG. 12, when the cam member 55 is rotated and the engaging portion 70 reaches the notch 55b of the cam member 55, the engaging arm 57 is disengaged from the cam member 55, Swing is performed so as to tilt rightward (downward) from the position P4, and the engaging portion 70 is engaged with the end portion of the inclined surface portion 55g from the vertical portion 55f to stop the swinging. When the engagement between the engagement arm 57 and the cam member 55 is released, the swing arm 56 swings downward by the weight of the pressing roller 34 attached to the tip and the biasing force of the biasing spring 72. . The downward swing of the swing arm 56 is restricted by the link rod 64, the swing arm 56 is stopped at the lowest position P2, and the upper surface 18 is pressed down by the pressing roller 34. The timing at which the pressing roller 34 falls and suppresses the pressure on the upper surface 18 is adjusted to be immediately after the planting claws 20L and 20R are pulled out of the cage.

  Then, as shown in FIG. 13, the cam member 55 is continuously rotated, and the engaging portion 62 of the engaging arm 57 is slid along the shape of the slope portion 55g of the notch portion 55b. 57 is gradually swung leftward (upward). In conjunction with the swinging operation of the engagement arm 57, the swinging arm 56 is swung upward via the link rod 64. The engagement arm 57 and the swing arm 56 are swung upward until the engagement portion 62 of the engagement arm 57 reaches the circumferential portion 55a from the inclined surface portion 55g. The arm 57 returns to the position P4 again and is stopped, and the swing arm 56 is also stopped in the state where it is raised to the uppermost position P3.

  As described above, the pressing device 14 is configured to repeatedly perform the operation of moving the swing arm 56 up and down by the pressing drive mechanism 35 and dropping the pressing roller 34 onto the upper surface 18. The pressure roller 34 is struck against the upper surface 18 by its own weight and the urging force of the urging spring 72, so that the upper surface 18 is crushed and the opening of the planting claws 20L and 20R formed in the heel is closed. Roots can be activated. Furthermore, since the pressing roller 34 is intermittently swung in the vertical direction, the planted seedling is not crushed by the pressing roller 34, and the working efficiency can be improved.

  The pressing device 14 in the sweet potato seedling machine 1 includes a first adjusting mechanism 46 and a second adjusting mechanism 47 that adjust the timing of the vertical movement of the pressing roller 34, as will be described below. -ing

<First adjusting mechanism 46>
As shown in FIGS. 11 and 14, the first adjustment mechanism 46 changes the attachment position by rotating the cam member 55 in the circumferential direction with respect to the arm member 54, and the downward movement of the pressing roller 34. It is configured to adjust timing. As described above, the cam member 55 and the arm member 54 are fixed by inserting the bolt 58 into the mounting hole 54b of the arm member 54 through the long hole 55d and fastening the bolt 58 with the nut 59 (see FIG. 10). The long hole 55d is formed in an arc shape along the turning locus of the mounting hole 54b formed in the arm member 54 in a side view. By loosening the nut 59, the cam member 55 can be rotated relative to the arm member 54 in the circumferential direction with the drive shaft 53 as a rotation center, and the fixing position relative to the arm member 54 is relatively changed. Thus, it can be positioned and fixed at a predetermined position within the drilling range of the long hole 55d.

  As shown in FIGS. 14A to 14C, when the cam member 55 is fixed, the arm member 54 is fixed at a substantially middle portion of the long hole 55d at the position P5 and both end portions of the long hole 55d. In the case where the inner cam member 55 is fixed to the notch 55b at the far end, it is fixed at the position P6, and at the end near the notch 55b of the inner cam member 55 at both ends of the long hole 55d. The case is designated as position P7. When the cam member 55 is fixed at the position P5 with respect to the arm member 54, it is fixed so that the timing of the vertical movement of the pressing roller 34 with respect to the vertical movement of the planting claws 20L and 20R substantially coincides. In addition, when the vertical movement timing of the pressing roller 34 with respect to the vertical movement of the planting claws 20L and 20R substantially coincides, the pressing roller 34 moves down immediately after the planting claws 20L and 20R transplant the seedlings into the cage, It means that it is adjusted so as to strike the upper surface 18.

  When the timing of the downward movement of the pressure roller 34 with respect to the planting claws 20L and 20R becomes earlier, that is, when the planting claws 20L and 20R have not yet been sufficiently pulled out of the cage, the pressure roller 34 swings downward. When moved, the cam member 55 is rotated so that the fixing position of the cam member 55 with respect to the arm member 54 is changed from the position P5 to the position P6, and the timing of the vertical movement of the pressing roller 34 is adjusted. (See FIG. 14B). When the fixing position of the cam member 55 is changed from the position P5 to the position P6, the timing at which the engaging portion 62 of the engaging arm 57 reaches the notch portion 55b as compared with the case where the fixing position of the cam member 55 is at the position P5. Can be changed to be slower. In the pressing drive mechanism 35, the swinging of the pressing roller 34 can be delayed via the engagement arm 57, so that the timing of the vertical movement of the pressing roller 34 with respect to the planting claws 20L and 20R can be substantially matched.

  On the other hand, when the timing of the downward movement of the pressure roller 34 with respect to the planting claws 20L and 20R is delayed, that is, not immediately after the planting claws 20L and 20R are pulled out of the cage, the pressure roller 34 is lowered after a predetermined time has elapsed. When the cam member 55 is swung in the direction, the cam member 55 is rotated so that the fixing position of the cam member 55 with respect to the arm member 54 is changed from the position P5 to the position P7 (see FIG. 14C). When the fixing position of the cam member 55 is changed from the position P5 to the position P7, the timing at which the engaging portion 62 of the engaging arm 57 reaches the notch portion 55b as compared with the case where the fixing position of the cam member 55 is at the position P5. Can be expedited. Therefore, the timing of the vertical movement of the pressing roller 34 with respect to the planting claws 20L and 20R can be substantially matched.

  By providing the first adjustment mechanism 46 in this way, it is easy to adjust the timing of the vertical movement of the planting claws 20L and 20R and the downward movement of the pressing roller 34, and these timings can be substantially matched. Therefore, by appropriately increasing or decreasing the timing of repression by the pressure roller 34, the transplanted seedling is not damaged, and the repression timing is delayed so that the vicinity of the root of the seedling in the reed cannot be relieved. Inability to hold seedlings can be prevented. The reason why the planting claws 20L and 20R and the pressing roller 34 are moved up and down is because the kind and size of the seedlings to be transplanted, the state of the field and cocoons, the moving speed of the machine body, etc. are different. It is possible to sufficiently cope with changes and workability is improved.

  Further, since the first adjustment mechanism 46 is provided in the pressing drive mechanism 35 configured in the pressing device 14, the cam member 55 also serves as a constituent member of the pressing drive mechanism 35 that moves the pressing roller 34 up and down. The accuracy of the adjustment is high, and the number of parts can be reduced and compactly formed. Further, the pressing drive mechanism 35 is surrounded by the cover body disposed on the handle frame 7 on the left side of the machine body, and the cover body can be opened and closed toward the outside of the machine body. Can be operated easily. The operation of the first adjusting mechanism 46 only needs to change the fixing position of the cam member 55 fixed to the arm member 54. If the cam member 55 is rotated by tightening or loosening the bolt 58, the first adjusting mechanism 46 is operated. Therefore, the operation can be performed quickly and accurately, and the workability in the field is improved.

<Second adjusting mechanism 47>
As shown in FIGS. 11 and 15, the second adjustment mechanism 47 includes a movable piece 61 that is swingably attached to the cam member 55, and changes the attachment position of the movable piece 61 with respect to the cam member 55. Thus, the cutout shape of the cutout portion 55b can be changed, and the upward movement timing of the pressing roller 34 is adjusted. The movable piece 61 is disposed closer to the cam body 55 than the cam member 55 and close to the cam member 55, and is disposed substantially parallel to the cam member 55, the arm member 54, the engagement arm 57, and the like. The movable piece 61 and the arm member 54 are arranged on the left and right opposite sides with respect to the cam member 55 so as not to interfere with the rotation. Further, the movable piece 61 has an insertion hole 61a formed at an end thereof, and the drive shaft 53 is inserted into the insertion hole 54a so that the movable piece 61 is loosely fitted to the arm member 54 so as to be relatively rotatable.

  The movable piece 61 is formed with an arc-shaped long hole 61b with the drive shaft 53 as the center, and the long hole 55d is disposed vertically opposite to the drive shaft 53 so as to be compactly disposed. Yes. On the other hand, a mounting hole 55 h is formed in the cam member 55, a bolt 75 is inserted into the mounting hole 55 h through the long hole 61 b, and the bolt 75 is fastened by a nut 76. The long hole 61b is formed in a position and shape that allows the bolt 75 to be inserted into the attachment hole 55h, that is, formed in an arc shape along the rotation locus of the attachment hole 55h in a side view. In this way, the movable piece 61 is relatively rotated in the circumferential direction with respect to the cam member 55 around the drive shaft 53 by loosening the nut 76, so that the fixed position relative to the cam member 55 is relatively set. It is configured so that it can be changed. In addition, the movable piece 61 is positioned and fixed at a predetermined position within the drilling range of the long hole 61b.

  The movable piece 61 has a circumferential surface 61c formed so as to have substantially the same curvature as the circumferential portion 55a of the cam member 55, and a slope 61d that forms a slope portion 55g in the notch 55b. The circumferential surface 61 c is formed to coincide with the circumferential portion 55 a of the cam member 55 in a state where the movable piece 61 is positioned and fixed to the cam member 55. Therefore, the engaging portion 62 of the engaging arm 57 that contacts the cam member 55 is in sliding contact with the circumferential portion 55a or the circumferential portion 55a along the circumferential surface 61c. The slope 61d is projected in a convex shape at the notch 55b of the cam member 55, and the engaging portion 62 is slid along the slope 61d.

  When the fixed position of the movable piece 61 with respect to the cam member 55 is changed, the slope 61d protruding to the notch 55b of the cam member 55 is changed, and the notch shape of the slope 55g of the notch 55b is changed. Here, when the protrusion of the inclined surface 61d to the notch 55b is maximum at the fixed position of the movable piece 61, in other words, the position P8 is a case where the inclined surface 55g is greatly protruded in the notch shape of the notch 55b. (See FIG. 15A). On the other hand, when the protrusion of the inclined surface 61d is minimized, in other words, the case where the inclined surface portion 55g protrudes gently is set as the position P9 (see FIG. 15B).

  When the movable piece 61 is at the position P8, the engagement arm 57 starts to swing leftward substantially simultaneously with the engagement portion 62 starting to slide along the slope 61d of the movable piece 61. For this reason, the pressing roller 34 is swung downward and squeezed the upper surface 18, and then immediately swung upward so that the pressing roller 34 and the upper surface 18 are separated from each other. That is, in such a case, the length (time) during which the pressing roller 34 is grounded to the heel surface 18 is short. Note that the pressing device 14 is configured such that the lower surface of the pressing roller 34 sinks by a predetermined depth L1 from the upper surface 18 to the lowermost position P2 of the swing arm 56 (see FIG. 12). ) Even if the pressing roller 34 is swung upward from a state where it is in contact with the upper surface 18, the pressing roller 34 and the upper surface 18 are not immediately separated.

  On the other hand, when the movable piece 61 is at the position P9, even if the engaging portion 62 starts to slide along the inclined surface 61d of the movable piece 61, the convex shape of the inclined surface 61d is gentle. Even if the movable piece 61 is not swung (leftward) or is swung, its size (swinging angle) is smaller than that in the case where the movable piece 61 is at the position P8. For this reason, the pressure roller 34 is rolled for a while while the heel surface 18 is crushed after the heel surface 18 is crushed. That is, in such a case, the length (time) for which the pressing roller 34 is grounded to the heel surface 18 is configured to be longer than that described above.

  As described above, the second adjustment mechanism 47 changes the cutout shape of the cutout portion 55b, thereby adjusting the length of contact of the pressure roller 34 with the upper surface 18 and the upward movement of the pressure roller 34. It is configured to adjust timing. Specifically, the movable piece 61 is rotated relative to the cam member 55 within the perforation range of the long hole 61b to change the cutout shape of the cutout portion 55b, and the inclined surface 61d to the cutout portion 55b. The protrusion is changed. Therefore, it is possible to easily adjust the pressure reducing operation by the pressing roller 34 by changing the length of the pressing roller 34 that is grounded to the upper surface 18. In particular, by changing the timing of the upward movement of the pressure roller 34 according to the state of the cocoon, the planting distance between the seedlings, the type and size of the seedling, etc., the effect of suppressing the pressure on the cocoon can be improved. Even if the second adjusting mechanism 47 is provided, the timing of the downward movement of the planting claws 20L and 20R and the pressing roller 34 is not changed, so that the workability of the pressing drive mechanism 35 is not impaired.

  Further, by providing the second adjustment mechanism 47 in the press drive mechanism 35, the cam member 55 also serves as a constituent member of the press drive mechanism 35 that moves the press roller 34 up and down. The number of points can be reduced and compactly formed. Furthermore, since the pressing drive mechanism 35 is disposed on the handle frame 7 on the left side of the machine body, it can be easily attached and changed by an operator. Then, the operation of the second adjustment mechanism 47 only needs to change the fixed position of the movable piece 61 fixed to the cam member 55, and the movable piece 61 is rotated by tightening or loosening the bolt 75. Therefore, the operation can be performed quickly and accurately, and the workability on the field is improved.

  In addition, the shape of the cam member 55 etc. which comprise the 1st adjustment mechanism 46 and the 2nd adjustment mechanism 47 which were mentioned above is not limited to this, The shape and structure which show | plays the same function can be used. For example, in the first adjustment mechanism 46, instead of the long hole 55d drilled in the cam member 55, a plurality of holes may be drilled and positioned at a predetermined position with respect to the arm member 54. In addition, the member and position for forming the hole may be appropriately changed. Similarly, in the second adjustment mechanism 47, a plurality of holes may be formed instead of the long hole 61b formed in the movable piece 61.

  As described above, the first adjustment mechanism 46 and the second adjustment mechanism 47 are provided in the pressing device 14 of the sweet potato seedling machine 1 so that the seedlings are planted, the type of seedlings, and the like. The timing of vertical movement between the planting claws 20L and 20R and the pressing roller 34 can be easily fine-tuned during the operation, and the pressure reduction effect is improved, so that the seedling can be placed in the cage without damaging the seedling by the pressing roller 34. It can be held sufficiently. In particular, the sweet potato seedling machine 1 is provided with a nail reciprocating mechanism 24 configured to change the planting posture of the seedlings with the planting claws 20L and 20R, so that the planting posture of the planting claws 20L and 20R can be changed. Therefore, even if the vertical movement timing of the planting claws 20L and 20R and the pressing roller 34 fluctuates, fine adjustment can be easily performed. Further, the first adjusting mechanism 46 and the second adjusting mechanism 47 are arranged in a compact manner so as to be adjusted with respect to the same cam member 55, the number of parts is reduced, and both are arranged in close proximity. Thus, the members to be adjusted are concentrated and arranged so that the location can be easily understood.

The side view which showed the whole structure of the sweet potato seedling machine provided with the press apparatus which concerns on one Example of this invention. The top view of the sweet potato seedling machine of FIG. 1 similarly. The side view of a planting apparatus. The side view which shows the movement path | route of the planting nail | claw at the time of ship bottom planting. The side view which shows the nail reciprocation mechanism at the time of ship bottom planting. The side view which shows the nail | claw reciprocation mechanism at the time of diagonal planting. The side view which shows the movement path | route of the planting nail | claw at the time of diagonal planting. The side view of a press apparatus. FIG. 9 is a plan view of the pressing device in FIG. 8. The side view of a press drive mechanism. The top view of the press drive mechanism of FIG. 10 similarly. The side view which shows the state in which a press roller presses the upper surface of a collar. The side view which shows the state by which a press roller is rock | fluctuated upwards. The side view which shows the attachment state of the arm member and cam member in a 1st adjustment mechanism. The side view which shows the attachment state of the cam member and movable piece in a 2nd adjustment mechanism. The top view which shows another Example of the support structure of a press roller.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Sweet potato seedling machine 14 Pressing device 20L / 20R Planting nail 34 Pressing roller (pressing body)
35 Press drive mechanism 36 Link mechanism 46 First adjustment mechanism (adjustment means)
47 Second adjustment mechanism (adjustment means)
54 Arm member 55 Cam member 55a Peripheral surface portion 57 Engaging arm 64 Link rod (link arm)

Claims (4)

  A pressing device of a transplanter provided with a pressing drive mechanism that swings the pressing body in the vertical direction in conjunction with the planting operation of the planting claw, wherein the pressing drive mechanism is an arm that is continuously rotated in one direction. A member, a cam member connected and fixed to the arm member, and having a notch formed in a part of the circumferential surface thereof, an engagement arm that abuts and swings along the circumferential surface of the cam member, A transplant mechanism comprising: a link mechanism that couples an engagement arm and a pressing body via a link arm; and an adjusting unit that adjusts the timing of the vertical movement of the pressing body with respect to the vertical movement of the planting claw. Pressing device.   The said adjustment means rotates the said cam member to the circumferential direction, and changes the fixing position with the said arm member relatively, The press apparatus of the transplanter of Claim 1 characterized by the above-mentioned.   The adjusting means includes a movable piece that changes a notch shape of the notch portion by changing a mounting position with respect to the cam member, and adjusts a length by which the pressing body is grounded to the upper surface of the collar. The pressing device for a transplanter according to claim 1 or 2.   The pressing device for a transplanter according to any one of claims 1 to 3 is arranged in a transplanter including a planting device capable of changing a planting posture of a seedling by the planting claws. A pressing device for a transplanter.

Images