KR102080358B1 - Transplanting machine - Google Patents

Abstract

An object of the present invention is to correct problems such as twisting of a transmission element due to the function of the inconstant speed member in an implanter having a rotary seedling planting device. Seedlings 48, 56, 121, 122, 98, 99 for transmitting the inconstant rotational power to the implant mechanism 8 are seeded with the upstream inconstant members 48, 56, 121, 122 on the main transmission 26 side. It is provided separately by the downstream inconstant velocity members 98 and 99 on a planting apparatus side. The upstream inconstant speed members 48, 56, 121, 122 are switchable in multiple stages, and the acceleration / deceleration ratios of the respective stages are different, and the downstream inconstant speed members 98, 99 are configured in one stage. At each end of the upstream inconstant speed members 48, 56, 121, 122, the maximum speed phase at which the operating speed of the planting reed 96 in the implantation mechanism 8 becomes the highest speed can be set and changed.

Description

Transplanter {TRANSPLANTING MACHINE}

The present invention relates to an implanter such as an electric machine for attaching a seedling planting apparatus having a seedling stand and a plurality of planting aids to a traveling body, and continuously performing seedling transplant work.

A conventional planting machine is equipped with the seedling planting apparatus which has a seeding stand and a transplantation mechanism with a planting aid attached to the rear part of a traveling body. As a transplant mechanism of a seedling planting apparatus, the type which provided two planting aids to one rotary case is common, and when a rotary case rotates once, two planting aids rotate 1 rotation in a reverse direction with respect to a rotary case, respectively. That is, the planting rotation rotates while revolving around the axis of the rotary case.

In seedling transplanting work using this kind of rice transplanter, planting aid is rotated while revolving the planting oriented in the direction of the seedling stand in front of the rotary case while intermittently feeding the seedling stand loaded with seedling mats at predetermined intervals. The seedlings are reciprocated between the seedling stand and the pavement surface, and the seedlings are scraped from the seedling mats for one week and then transplanted into the pavement. The operation cycle (planting cycle) of the planting aid in the seedling planting apparatus is linked to the traveling speed of the traveling body, and the planting interval (weekly) of the seedlings is kept constant even when the traveling speed is changed.

The number of weeks to plant seedlings per unit area (generally 3.3 m2) is not necessarily constant. For example, the number of planting shares per unit area desired depends on the region or the user. In this regard, the conventional electric machine is provided with a weekly transmission device for adjusting the interlocking relationship between the traveling speed and the planting period. In this case, the daytime is changed by changing the operating speed (grafting speed) of the implantation mechanism with respect to the traveling speed in the weekly transmission, so that the number of planting shares per unit area is changed.

In recent years, news has been made to take longer days compared to standard transplants in consideration of growth conditions of seedlings planted on the packaging, but it is necessary to slow down the planting speed as the day lengthens. However, by simply slowing down the planting speed by the weekly transmission device, there is a problem that seedlings are turned over or seedlings are generated because the planting tip is pulled from the pavement.

In this regard, Patent Literatures 1 and 2 disclose a structure of a transfer machine provided with an inconstant speed member that transmits an inconstant rotational power to an implantation mechanism in order to prevent the planting aid from being dragged from the packaging when it is notified. The inconstant speed member is configured to change the angular velocity (inconstant speed rotation) during one rotation of the rotary case constituting the implant mechanism, thereby speeding up the speed at which planting aids avoid from packing. In the transfer machine of patent document 1, the inconstant speed member is attached to the weekly transmission device in a mission case. In the transfer machine of patent document 2, the inconstant velocity member is provided in the power transmission downstream rather than the lateral feed drive mechanism of a seedling stand.

Japanese Patent No. 4376154 Japanese Patent Publication No. 2003-189712

By the way, the power transmission system from the weekly transmission to the implantation mechanism is composed of transmission elements such as gears and rotating shafts. A transmission element such as a rotating shaft is not a complete rigid body, but slightly deforms when a load (rotation torque) is applied, and returns to elastic restoring force when the load is released. That is, torsion and torsional release occur alternately with the rotation of the transmission element of the power transmission system, which appears as a vibration. On the other hand, the inconstant speed member accelerates and decelerates the angular velocity during one rotation of the transmission element, and the load variation acting on the transmission element is further increased by the acceleration and deceleration. For this reason, in the structure which functions the inconstant speed member at the time of a news like the said prior art, the vibration of a transmission element becomes remarkable, and the operation period of planting relief is shifted, and there existed a problem of planting failure. This tendency was remarkable as the traveling speed of the traveling gas became faster.

The present invention has been made in view of the present situation as described above, and the advantage of the inconstant member is that it is nostalgic and attempts to prevent the problem.

The present invention includes various configurations. The invention of claim 1 constitutes the highest concept, and the implanter according to the invention has a mission case for shifting power from an engine mounted on a traveling body, and a transplant mechanism with a planting aid for drawing a non-circular motion trajectory. The seedling planting apparatus and the weekly transmission device which changes a daytime by changing the operation speed of the said transplantation mechanism with respect to the travel speed of the said traveling body are provided. And the inconstant speed member which transmits the inconstant rotational power to the said implant mechanism is divided into the upstream inconstant speed member on the said main transmission side, and the downstream inconstant speed member on the said seedling planting side. The upstream inconstant speed member is switchable in a plurality of stages, and the acceleration / deceleration ratios of the respective stages are different, and the downstream inconstant speed member is configured in a single stage. Each stage of the upstream inconstant speed member is capable of setting and changing the highest speed phase at which the operating speed of the planting aid in the implantation mechanism becomes the highest speed.

In the invention of claim 2, the downstream inconstant speed member is capable of changing the setting in the direction further away from the front-back range or the bottom dead center with the highest speed phase interposed between the bottom dead center.

The invention of claim 3 suitably develops the invention of claim 1 or 2. In the above invention, the weekly speed shift device is provided on the traveling body side.

As a transmission element of a power transmission system, there exist various things, such as a gear, a rotating shaft, a clutch, a sprocket, and a chain. The gears include not only spur gears but also various gears such as bevel gears and planetary gears, but conventionally, spur gears are configured as inconstant speed members as inconstant speed members. On the other hand, in invention of Claim 4, the bevel gear pair is comprised by the inconstant speed bevel gear as a downstream inconstant speed member. That is, the power transmission system from the weekly transmission to the implantation mechanism of claim 4 has rotation axes intersected with each other, and is configured to transmit power to these crossed rotation axes through a bevel gear pair, and as the downstream inconstant speed member, The bevel gear pair consists of an inconstant bevel gear.

In addition, although the inconstant speed gear is arrange | positioned inside the rotary case which comprises an implantation mechanism, this is to operate a planting relief to draw the long non-circular operation trace of up and down, and the inconstant speed member (namely, the transmission of a power transmission system) mentioned in this invention. A member for imparting inconstant speed rotation (acceleration and deceleration) to the element.

According to a fifth aspect of the present invention, in the implanter according to claim 4, each of the inconstant bevel gears is one in which the pitch cone angle is continuously changed along the rotational direction.

According to a sixth aspect of the present invention, in the implanter according to claim 5, the pitch circle of each of the inconstant bevel gears is eccentric with respect to a round circle having a shape close to an ellipse and centered on a rotation axis. Is to form the outer diameter of the circle.

(Effects of the Invention)

According to the present invention, a seedling planting apparatus having a shunt case for shifting power from an engine mounted on a traveling body, an implantation mechanism with a planting aid for drawing a non-circular motion trajectory, and the above-described method for the traveling speed of the traveling gas. In the implanter provided with the weekly transmission device which changes a daytime by changing the operation speed of a transplantation mechanism, the inconstant speed member which transmits an inconstant rotational power to the said implantation mechanism is an upstream inconstant member on the said daytime transmission device side, and the said seedling planting device side Of the downstream inconstant speed member, the upstream inconstant speed member is switchable in a plurality of stages, and the acceleration / deceleration ratios of the respective stages are different. Concentration can be suppressed and the torsion of a power transmission system can be suppressed. As a result, planting defects can be prevented or suppressed.

Moreover, since the part which rotates at an inconstant speed largely becomes smaller than before, generation | occurrence | production of the excessive torque in a power transmission system can be suppressed, and the operation cycle shift of the said planting relief caused by the reaction of a power transmission system can be prevented or suppressed. As described above, it is generally necessary to rotate the power transmission system at an inconstant speed in the news. Therefore, it is preferable to make the intermittent rotation rotate in conjunction with the interstate transmission when switching to the news setting.

Further, at each end of the upstream inconstant speed member, the maximum speed phase at which the operating speed of the planting aid in the implantation mechanism becomes the highest speed can be set and changed. The maximum speed phase can be set and changed even when it is large and there is a concern about staggered operation cycles of the planting aid, or when the torsion of the power transmission system is small and the vibration of the power transmission system is to be minimized. That is, for example, it is possible to set and change the fastest phase in accordance with the relationship between the assembly accuracy and the like to draw the operation trajectory optimal for the planting aid.

According to the invention of claim 2, in the downstream inconstant speed member, the maximum speed phase can be changed in a forward and backward range with a bottom dead center or in a direction further away from the bottom dead center. The speed is increased near the bottom dead center to quickly and accurately avoid planting relief from the bottom dead center. As a result, seedlings can be transplanted to an appropriate planting posture.

Moreover, although it is theoretically possible to attach the said weekly transmission device to the said seedling planting apparatus, it is advantageous to make the seedling planting apparatus as light as possible. Therefore, it is preferable to install a weekly transmission device on the traveling body side as described in Claim 3. In recent years, many fertilizers are installed in the traveling body, but since the fertilizer must be linked to the movement of the planting device, in this case, a weekly change device is installed in the traveling body, and the fertilizer is applied from the weekly change device. And power to the implant. In either case, it is suitable to install the weekly transmission on the traveling body side.

According to the invention of claim 5, since each of the inconstant bevel gears is a pitch cone angle continuously changed along the rotational direction, the inconstant bevel gears generate and transmit inconstant rotation between, for example, rotation axes that cross each other. It becomes possible. Therefore, the number of parts and the structure can be simplified, and the structure for inconstant speed rotation can be made compact.

According to the sixth aspect of the present invention, the pitch circle of each of the inconstant bevel gears has a shape close to an ellipse and is eccentric with respect to a circle centered on a rotation axis. It becomes possible to form it about the size of a normal bevel gear, and can miniaturize and compact the assembly space of the said inconstant speed bevel gear mechanism in a power transmission system. In this case, as a way of thinking about the production of the inconstant bevel gear, the rotating shaft is cut into a common cylinder by deforming the conical shape formed by keeping the cone distance constant, so that the outer diameter shape is the origin.

1 is a plan view of a transfer machine according to an embodiment.
2 is a side view of the electric machine.
3 is a perspective view showing the skeleton of the electric table.
Fig. 4A is a perspective view showing the entire power transmission path, and Fig. 4B is a perspective view of a seedling planting apparatus.
FIG. 5 (A) is a side view of a power transmission path, FIG. 5 (B) is a side view of a location of a seedling planting apparatus, and FIG. 5 (C) is a diagram showing a trajectory of planting aid.
Fig. 6 (A) is a plan view showing a power transmission path, Fig. 6 (B) is an external perspective view of the weekly change device, and Fig. 6 (C) and Fig. 6 (D) are an external perspective view of the center case provided in the planting part.
Fig. 7A is an external perspective view of the gear group in the weekly change device and the center case, Fig. 7B is a perspective view of the gear group in the center case, and Fig. 7C is a gear group in the center case. Is the rear view of.
8 is an electric system diagram.
Fig. 9A is a plan view showing a power transmission path to a seedling planting apparatus, Fig. 9B is an exploded plan view of a terminal planting part of the power transmission path, and Fig. 9C is a schematic view of a bevel gear.
10 (A) and 10 (B) are plan views showing the bevel gear meshing state, FIGS. 10 (C) and 10 (D) are perspective views of the bevel gears, and FIG. 10 (E) shows a pair of bevel gears. It is a contrast chart.
11 is a chart showing the relationship between the gear combination and the planting number in the weekly transmission.
It is a figure which shows the operation | movement trace of the planting relief when it sets to 43 weeks of inconstant velocity.
It is a figure which shows the change of the angular velocity of planting relief when it sets to 43 weeks of inconstant velocity.

Next, embodiment of this invention is described based on drawing. Embodiment is applied to the riding type transfer machine (henceforth a "transplanter") as an implanter. In the following description, the words in front, back, left, and right are used to specify the direction, but the words in the front, back, left, and right directions define the forward direction of the electric machine in the future. From the front, the direction is the direction opposite to the forward direction.

(One). Summary of electric machine

First, the outline of the electric machine will be described based on FIGS. 1 to 5. As shown in FIGS. 1-3, the electric heater has the traveling body 1 and the seedling planting apparatus 2 arrange | positioned behind it. The traveling body 1 has the front and rear wheels 3 and 4, a steering seat 5, and a steering wheel 6, while the seedling planting apparatus 2 has a seedling stand 7 or a seedling mat on which a seedling mat is loaded. It has a mechanism (8). The electric table of the embodiment is an 8 tank type, and therefore, the seedling stage 7 is provided with eight seedling mat loading areas, and eight transplant mechanisms 8 are transverse to the rear part of the seedling planting apparatus 2. It is arranged in a line.

As shown in FIG. 3, the traveling body 1 has a frame 9 made of a plurality of frame members, and the engine 10 is supported at the front of the frame 9. The mission case 11 is arranged behind the engine 10. As shown in FIG. 4 (A), a hydrostatic continuously variable transmission (HST) 12 is mounted on the left side of the mission case 11, and the power of the engine 10 is controlled by the hydrostatic stepless belt 13. Is transmitted to a transmission (HST) 12. The engine 10 is covered with a bonnet 14. In addition, the part except the bonnet 14 of the traveling body 1 is covered with the vehicle body cover 15.

The front axle device 17 is attached to the left and right side surfaces of the mission case 11, and the front wheel 3 is attached to the front axle device 17. The rear axle case 18 is arrange | positioned behind the mission case 11, and the rear wheel 4 is attached to the axle after protruding laterally from the rear axle case 18. As shown in FIG. The mission case 11 and the rear axle case 18 are connected by a joint material 19 of front and rear lengths. The left and right rear supporters 20 are attached to the rear axle case 18, and the upper end of the rear supporters 20 has a left and right horizontally long rear frame 9a constituting the rear end of the frame 9 (Fig. 3).

Link apparatus 21 which consists of upper and lower link bodies (top link and lower link) is rotatably connected to the left and right rear supporters 20, and the seedling planting apparatus 2 is attached to the rear end of the link apparatus 21. It is. The linkage device 21 can be rotated by a hydraulic cylinder (elevating cylinder) 22 connected to the joint material 19. Therefore, the seedling planting apparatus 2 raises and lowers by expanding and contracting the hydraulic cylinder 22.

As can be easily understood from FIG. 4, power is transmitted from the inside of the mission case 11 to the rear axle case 18 to the inside of the rear axle case 18. Rotation of the rear wheel drive shaft 23 is transmitted to the rear wheel 4 via a gear group provided in the rear axle case 18. The transfer machine of the embodiment is provided with the stationary rotor 24 in the seedling planting apparatus 2, and is transmitted to the stationary rotor 24 by the rotor drive shaft 25 which protruded back from the rear axle case 18. .

In the embodiment, the weekly transmission 26 is attached to the right side of the rear axle case 18, and the power is transmitted from the mission case 11 to the weekly transmission 26 via the planting power transmission shaft 27. . The rotation of the planting power transmission shaft 27 is shifted by the gear group incorporated in the weekly transmission 26, and is transmitted to the seedling planting apparatus 2 by the PTO shaft 29.

The seedling planting apparatus 2 has the main frame 28 long left and right horizontally, the center case 30 is fixed to the substantially left and right middle part of the main frame 28, and the power of the PTO shaft 29 is centered. It is transmitted to the gear group built in the case 30. Four support arms 31 extending backward are fixed to the rear surface of the main frame 28, and a pair of left and right implantation mechanisms 8 are rotatably attached to the rear end of the support arm 31.

A planting drive shaft 32 that extends from side to side and horizontally penetrates the base end portion (near the front end portion) of the support arm 31, and the implant mechanism 8 is driven by the rotation of the planting drive shaft 32 (details will be described later). ). In addition, power is transmitted to the planting drive shaft 32 from the PTO shaft 29 through a gear group built into the center case 30. The center case 30 is also provided with a horizontal feed shaft 33 that is long horizontally and horizontally, and the seedling stand 7 moves horizontally by one pitch by the rotation of the horizontal feed shaft 33.

The seedling planting apparatus 2 has a belt 34 group in which a seedling mat is mounted, and the belt 34 is wound up by a pair of vertical conveyance support shafts 35 up and down. When the seedling stand 7 is all moved to either of the left and right, the longitudinal feed support shaft 35 is rotated so that the seedling mat moves downward by one pitch.

As shown in FIG. 4B, each implant mechanism 8 has one rotary case 36 and a planting member 37 rotatably provided at both ends thereof, and the rotary case 36 has one-half. Each time rotation, seedling scraping and planting by the planting member 37 are performed. In addition, when the PTO shaft 29 rotates once, the rotary case 36 is set to rotate 1/2. And although the rotational speed of the PTO shaft 29 is basically proportional to the traveling speed of the traveling body 1, by changing the relationship between the traveling speed and the rotational speed of the PTO shaft 29 by the weekly transmission 26, You can change the transplant interval (weekly).

(2). Structure, power transmission structure (upstream inconstant member) of the weekly transmission

Hereinafter, the power transmission system from the weekly transmission 26 to the implant mechanism 8 will be described in detail. First, the structure of the weekly transmission 26 and the power transmission structure therefor will be mainly described based on FIGS. 6 to 8. The weekly transmission 26 has the weekly case 40 of the front-back dividing system shown in FIG. 4 (B), and the gear group shown in FIG. 6 (A) and FIG. 6 (C) is arrange | positioned inside it. .

The input shaft 41 and the output shaft 42 are arrange | positioned inside the main case 40, and the rear end of the planting power transmission shaft 27 is connected via the universal joint to the input shaft 41. As shown in FIG. The first gear 43 and the second gear 44 having the same diameter are fixed to the input shaft 41. Both gears 43 and 44 have the same diameter but the number of teeth is slightly smaller than that of the first gear 43.

The input shaft 41 and the output shaft 42 are arranged concentrically. The cylindrical intermediate shaft 45 is fitted to the input shaft 41 so as to be relatively rotatable, and the intermediate shaft 45 is fitted in a state in which it rotates together with the output shaft 42 (the state in which the relative rotation is impossible). The third gear 46 and the fourth gear 47 are fitted to the intermediate shaft 45 so as not to rotate relative to each other by spline fitting or the like. In addition, an upstream inconstant speed first gear 48 and an upstream inconstant speed third gear 121 are fitted to the intermediate shaft 45 so as to be relatively rotatable.

The output shaft 42 is provided with a cam main clutch 49. The main clutch 49 consists of the fixing part 49a and the sliding part 49b, and the sliding part 49b is a via which is biased toward the fixing part 49a by the clutch spring 49c (refer FIG. 7 (C)). It is fresh. When the sliding component 49b resists the clutch spring 49c and is separated from the fixed component 49a, power transmission from the input shaft 41 to the output shaft 42 is interrupted. The main clutch 49 is turned off in the state which raises the seedling planting apparatus 2 like the case of road-floor running and turning. The blocking operation of the main clutch 49 is performed by lowering the main clutch operation shaft 50.

In the interior of the main case 40, an idle shaft 51 extending in parallel with the input shaft 41 and the output shaft 42 when viewed from the side is rotatably supported, and the first gear is supported by the idle shaft 51. The fifth gear 52 that can be engaged with the 43 or the second gear 44 is fitted in a slidable and non-rotating manner by spline fitting or the like. The fifth gear 52 is about twice the number of teeth of the first gear 43 or the second gear 44, and the first position engaged with the first gear 43 and the second gear 44 are engaged. The second position can be selected.

The sixth gear 54 and the fourth gear engaged with and separated from the upstream inconstant speed fourth gear 122 and the third gear 46 are always engaged with the upstream inconstant third gear 121 on the idle shaft 51. The seventh gear 55 meshing with the 47 and the upstream inconstant second gear 56 that are always in engagement with the upstream inconstant first gear 48 are fixed. The ratio of the number of teeth of the seventh gear 55 to the fourth gear 47 is set smaller than the ratio of the sixth gear 54 to the third gear 46. Therefore, the rotation speed of the intermediate shaft 45 (and the output shaft 42) is higher than the state in which the third gear 46 and the sixth gear 54 are engaged with the fourth gear 47 and the seventh gear 55. The side which is in an engaged state becomes low.

The upstream inconstant first gear 48 and the upstream inconstant second gear 56 are non-circular profiles, such as ellipses, and the number of teeth is set the same. Therefore, in the state where the rotation of the idle shaft 51 is transmitted to the intermediate shaft 45 and the output shaft 42 through both inconstant speed gears 48 and 56, the rotation speed of the idle shaft 51 and the output shaft 42 are the same. In addition, the output shaft 42 rotates in the state which changed the angular velocity periodically among the 1 rotation. Both inconstant gears 48 and 56 are non-circular and are always held in engagement from the particularity that the phase of engagement is always fixed. Similarly, the upstream inconstant third gear 121 and the upstream inconstant fourth gear 122 also have a non-circular profile like an ellipse, and the number of teeth is set the same. Therefore, in the state where the rotation of the idle shaft 51 is transmitted to the intermediate shaft 45 and the output shaft 42 through both inconstant speed gears 48 and 56, the rotation speed of the idle shaft 51 and the output shaft 42 are the same. In addition, the output shaft 42 rotates in the state which changed the angular velocity periodically among the 1 rotation. That is, the upstream inconstant speed first gear 48 and the upstream inconstant speed second gear 56 are non-circular gear pairs, such as an eccentric gear, and are large acceleration / deceleration ratio (inconstant speed ratio). The upstream inconstant speed third gear 121 and the upstream inconstant speed fourth gear 122 are also non-circular gear pairs such as eccentric gears, but are small in acceleration / deceleration ratio (inconstant speed ratio).

Here, in the rotary case 36, for example, at the news of 37 shares / m 2, the highest speed phase of each planting 96 in the planting member 37 (the operating speed of the planting 96 is Acceleration and deceleration are given so that the phase becoming the highest speed is near the bottom dead center, but in the embodiment, the upstream inconstant first gear 48 and the upstream inconstant second gear 56 provided in the weekly transmission 26 are provided. A rather large acceleration / deceleration is given to the rotational power from the weekly case 40 to output the inconstant rotational power. Therefore, since the acceleration / deceleration ratio (inconstant speed ratio) is larger than the combination of the upstream inconstant third gear 121 and the upstream inconstant fourth gear 122, the operation speed near the bottom dead center of the operation trajectory of the planting 96 is greatly increased. Let's do it. In addition, the upstream inconstant speed third gear 121 and the upstream inconstant speed fourth gear 122 impart rather small acceleration / deceleration to the rotational power from the main case 40 to output the inconstant rotational power. Therefore, since the acceleration / deceleration ratio (inconstant speed ratio) is smaller than the combination of the upstream inconstant first gear 48 and the upstream inconstant second gear 56, the operation speed in the vicinity of the bottom dead center of the operation trajectory of the planting 96 is increased slowly. Let's do it. The upstream inconstant first to fourth gears 48, 56, 121, 122 correspond to the upstream inconstant member on the side of the main transmission 26 that transmits the inconstant rotational power to the implant mechanism 8.

The 1st intermediate | middle clutch 57 which can be engaged and separated is provided in the 4th gear 47 and the upstream inconstant speed 1st gear 48. As shown in FIG. The first intermediate clutch 57 is engaged when the fourth gear 47 slides further to the right through the state in which the fourth gear 47 is engaged with the seventh gear 55 once. In the state where the first intermediate clutch 57 is engaged, the power of the idle shaft 51 is transmitted to the output shaft 42 via the upstream inconstant speed second gear 56 and the upstream inconstant speed first gear 48. In a state where the first intermediate clutch 57 is engaged, the third gear 46 and the fourth gear 47 are idle. Therefore, the 1st intermediate | middle clutch 57 has the function of relaying and interrupting | connecting the intermediate shaft 45 and the upstream inconstant speed 1st gear 48. As shown in FIG.

Moreover, the 2nd intermediate | middle clutch 123 which can be engaged and separated also is provided also in the 3rd gear 46 and the upstream inconstant 3rd gear 121. As shown in FIG. The second intermediate clutch 123 is engaged with the intermediate shaft 45 when the third gear 46 slides further to the left once through the state in which the third gear 46 is engaged with the sixth gear 54. In the state where the second intermediate clutch 123 is engaged, the power of the idle shaft 51 is transmitted to the output shaft 42 through the upstream inconstant fourth gear 122 and the upstream inconstant third gear 121. Also in this case, when the second intermediate clutch 123 is engaged, the third gear 46 and the fourth gear 47 are idle. Therefore, the 2nd intermediate | middle clutch 123 has a function which relays and interrupts the connection of the intermediate shaft 45 and the upstream inconstant 3rd gear 121. As shown in FIG.

Two stages of switching are performed by the fifth gear 52 sliding, and four stages of switching are performed by the sliding of the intermediate shaft 45. Therefore, there are eight stages of combinations (speed switching) in total. For example, the number of weeks per 3.3 m2 can be changed to the number of weeks, such as 37 to 85 shares, and covers most of the news and the total area of the news. 11 shows the relationship between the gear combination and the planting number in the embodiment. In the case where the first gear 43 and the fifth gear 52 are engaged with each other, when the fourth gear 47 and the seventh gear 55 are engaged with each other, the planting number is set to the d-week with constant velocity, and the third gear 46 ) And the sixth gear 54 are set to the f strain at the constant velocity. When the second intermediate clutch 123 is engaged, the number of planting strains is set to b strains which are inequality. In the case where the second gear 44 and the fifth gear 52 are engaged with each other, when the fourth gear 47 and the seventh gear 55 are engaged with each other, the number of planting shares is set to c shares with constant velocity, and the third gear 46 ) And the sixth gear 54 are set to the number e of planting liquor at constant velocity. When the first intermediate clutch 57 is engaged, the number of planting strains is set to a strain at an inconstant speed. In this case, the number of weeks represented by the alphabet has many relationships in alphabetical order.

Here, the upstream inconstant first to fourth gears 48, 56, 121, 122 are assembled to the intermediate shaft 45 or the idle shaft 51 by adjusting the attachment phase so that the planting aid in the implantation mechanism 8 can be adjusted. It is possible to set and change the maximum speed phase at which the operating speed of 96 becomes the highest speed within the front and rear ranges with a bottom dead center. FIG. 12 shows an operation trajectory of the planting relief 96 when it is set to 43 weeks of inequality as an example. The symbol MS1 of FIG. 12 is the highest when assembling the upstream inconstant third gear 121 and the upstream inconstant fourth gear 122 so that the operating speed of the planting 96 is the highest at the front side (upstream side) of the bottom dead center. It is a high speed phase, and MS2 is a highest speed phase when the upstream inconstant speed 3rd gear 121 and the upstream inconstant speed 4th gear 122 are assembled so that the operation speed of the planting part 96 may become the highest speed near bottom dead center. Reference sign MS3 is the highest phase in the case of assembling the upstream inconstant third gear 121 and the upstream inconstant fourth gear 122 such that the operating speed of the planting 96 is the highest speed at the rear side (downstream side) from the bottom dead center. .

For example, the upstream inconstant third gear 121 and the upstream inconstant fourth gear 122 may be assembled or inferior so that the front side (upstream side) of the bottom dead center is the highest speed phase MS1, for example, in accordance with the relationship with the assembly accuracy. The upstream inconstant third gear 121 and the upstream inconstant fourth gear 122 are assembled so as to have the highest speed phase MS2 in the vicinity of the point, or the rear side (downstream) is set to the fastest speed MS3 behind the bottom dead center. It is possible to assemble the upstream inconstant third gear 121 and the upstream inconstant fourth gear 122. That is, for example, when the torque of the power transmission system is large and the operation cycle of the planting 96 is worrisome in relation to the assembly accuracy, or when the movement of the power transmission system is small and the distortion of the power transmission system is small and the vibration of the power transmission system is desired to be suppressed as much as possible. You can change the speed phase before and after bottom dead center. By doing so, it is possible to suppress jerking of the planting vessel 96 or to suppress vibration of the power transmission system. It goes without saying that the upstream inconstant first gear 48 and the upstream inconstant second gear 56 may be assembled to the intermediate shaft 45 or the idle shaft 51 by adjusting the attachment phase.

At the upper part of the weekly case 40, a fertilizer rotating shaft 58 extending in parallel with the input shaft 41 and the output shaft 42 is rotatably disposed, and the first gear 43 is disposed on the fertilizing shaft 58. And the eighth gear 59 engaged with each other are rotatably fitted. The fertilizing drive shaft 58 is powered by the bevel gear 61 to the fertilizing drive shaft 62.

As shown to FIG. 7 (A), the weekly transmission 26 has two operation shafts, the 1st operation shaft 63 and the 2nd operation shaft 64. As shown in FIG. These operation shafts 63 and 64 are in the posture of the front-back length, and are exposed in front of the daytime case 40. As shown in FIG. As can be understood from FIG. 6B, the first operating shaft 63 can be slid back and forth by the first lever 65, and the second operating shaft 64 is driven by the second lever 66. Sliding back and forth can be operated. The 1st operation shaft 63 is for sliding operation of the 5th gear 52, and has the shifter which slides the 5th gear 52. As shown in FIG. The second operation shaft 64 is for sliding the intermediate shaft 45 and includes a shifter engaged with the intermediate shaft 45.

(3). Internal structure of the center case

6 to 8, the internal structure of the center case 30 (that is, the planting transmission device) will be described. The center case 30 is composed of a shell body of two left and right dividing methods, and the input shaft 69 of the front and rear lengths is rotatably held. The front end of the input shaft 69 and the rear end of the PTO shaft 29 are connected via a universal joint.

Inside the center case 30, the left and right intermediate shafts 70 are disposed, and the rotation of the input shaft 69 is transmitted to the intermediate shaft 70 by a pair of first bevel gears 71a and 71b. The horizontal feed drive shaft 72 is arrange | positioned at the left and right horizontally long posture inside the center case 30, and the horizontal feed shaft 33 is connected to the horizontal feed drive shaft 72. As shown in FIG.

Three lateral feed amount adjustment driven gears 73 are fixed to the lateral feed drive shaft 72, while three lateral feed amount adjustment main gears 74 correspond to the lateral feed amount adjustment driven gears 73 on the intermediate shaft 70. Is loosely fitted. It is selectively powered from the intermediate shaft 70 by a sliding key 76 (see FIG. 8) to any one of the three lateral feed amount adjusting cogwheels 74. The sliding key 76 is slid by the sliding lever 77 shown in FIG. 6 (C), FIG. 6 (D), FIG. 7 (A), and FIG. 7 (B).

The ratio of the number of teeth of the lateral feed adjustment gears 73 and 74 pairs differs, respectively, and when the combination of the lateral feed adjustment gears 73 and 74 is changed, the rotation ratio of the lateral feed drive shaft 72 with respect to the PTO shaft 29 is changed. This changes. As a result, the lateral feed pitch of the seedling stage 7 changes, and the amount of scraping of seedlings changes.

The center case 30 has a projection 30a extending downward from the rear side, and the planting output shaft 78 that is horizontally long and horizontally held on the projection 30a is rotatably held, and the planting output shaft 78 has an intermediate shaft. The first relay gear 79 fixed to 70, the second relay gear 80 fitted to the lateral feed drive shaft 72 so as to be relatively rotatable, and the center case 30 are rotatably held by the idle shaft 81. Is transmitted through the third relay gear 82 and the fourth relay gear 84. The fourth relay gear 84 is attached to the planting output shaft 78 via the sleeve 83.

The ratio of the number of teeth of the first bevel gears 71a and 71b is in a 1: 1 relationship, and also the teeth of the first relay gear 79, the second relay gear 80, and the fourth relay gear 84. The numbers are in a 1: 1: 1 relationship. Therefore, the rotation speed of the PTO shaft 29 and the planting output shaft 78 has a 1: 1 relationship. In addition, since the third relay gear 82 is a simple idle gear, the number of teeth does not affect the rotation speed of the fourth relay gear 84.

The planting output shaft 78 and the planting drive shaft 32 located in the neighborhood thereof are connected by a coupling (sleeve) 86. Moreover, the relay shaft 85 is arrange | positioned between the planting drive shaft 32 adjacent to right and left, and the drive shaft 32 and the relay shaft 85 are also connected by the coupling 86. As shown in FIG. Therefore, each planting drive shaft 32 rotates integrally. The planting drive shaft 32 is segmented at each location of each transplantation mechanism 8, and the adjacent planting drive shaft 32 is connected by the coupling 86. In addition, it is also possible to make the planting output shaft 78, each planting drive shaft 32, and the relay shaft 85 into a single structure made of one bar.

(4). Structure and Power Transmission Structure of Implant Mechanism

Next, the structure of the implant mechanism 8 and the power transmission structure thereof will be described. These form the main part of the embodiment, and are mainly shown in Figs. 8 to 10 (see also Fig. 6 (A)). The support arm 31 has a hollow structure, and as shown in FIG. 8, the planting transmission shaft 87 of the front and rear lengths is rotatably held therein.

The planting transmission shaft 87 is powered by the planting drive shaft 32 by the second bevel gear pairs 88a and 88b. Among the second bevel gear pairs 88a and 88b, the bevel gear 88b which rotates concentrically with the planting transmission shaft 87 is attached to the torque limiter 89 fitted to the planting transmission shaft 87. The torque limiter 89 has a spring 90. If the planting transmission shaft 87 is subjected to a predetermined load or more, the engagement is separated and power transmission is interrupted.

The planting central axis 91 long horizontally and horizontally is hold | maintained rotatably at the rear end part (tip part) of the support arm 31 via a pair of left and right bearings 104. The planting central axis 91 protrudes to the left and right outer side of the support arm 31, and the sun gear 92 incorporated in the rotary case 36 is fixed to the protruding end. Although the details are omitted, the rotary case 36 is rotatably held at the rear end of the support arm 31.

The rotary case 36 has a hollow structure in which two left and right shell bodies are enclosed, the sun gear 92 described above is disposed in the middle of the length thereof, and the intermediate gear 93 is disposed outside thereof, and the planetary body is disposed outside thereof. Gear 94 is arranged. Each gear 92, 93, 94 is eccentrically eccentric. The planting member 37 is fixed to the unit shaft 95 fixed to the planetary gear 94.

As shown in FIG. 5, the planting aid member 37 includes a planting aid 96 and a protruding rod 97. As shown in FIG. 5C, a planting aid 96 is used to plant seedlings from a seedling mat. The seedlings are planted on the pavement by cutting off only one week and transferring to the pavement, and the protruding rod 97 moves relatively to the planting ridge 96 near the bottom dead center.

As shown in FIG. 9, power is transmitted from the planting transmission shaft 87 to the planting central shaft 91 by the downstream inconstant speed bevel gear pairs 98 and 99. That is, the downstream inconstant speed driving bevel gear 98 is fixed to the planting transmission shaft 87 via the coupling 100, while the downstream inconstant speed driven bevel gear 99 is fitted to the planting central shaft 91. Inconstant speed rotation is always transmitted from the planting transmission shaft 87 to the planting central axis 91 by the inconstant bevel gear pairs 98 and 99.

The downstream inconstant speed bevel gear 98 has the boss body 98a of the shape different in height, and the coupling 100 is fitted in the small diameter part of the boss body 98a. The bearing 101 is fitted in the boss body 98a. On the other hand, the coupling 100 is welded and fixed to the planting transmission shaft 87 and is maintained so that relative rotation is impossible. The downstream inconstant speed driven bevel gear 99 is fitted to the planting central shaft 91 so as to be relatively rotatable, and has a cam portion 103 engaged with the jaw stop clutch 102. The operation ring 105 is integrally welded to the jaw stop clutch 102.

The jaw stop clutch 102 is slidably held relative to the planting central axis 91 so as not to rotate relatively. The stopping clutch 102 is normally pressed in the state of being engaged with the downstream inconstant speed driven bevel gear 99 by the spring 106. When the rotary operation rod (not shown) is operated, the jaw stop clutch 102 is separated from the downstream inconstant speed driven bevel gear 99 along the axis of the planting central shaft 91 to cut off power to the planting central shaft 91. .

For example, some of the four transplant mechanisms 8 may not be operated in the planting operation at the head edge, but in this case, the function of the some implant mechanisms 8 is operated by operating the stopping clutch 102. Can be stopped. That is, the stop function for reducing the number of planting aids is exerted.

(5). Downstream inconstant

In the embodiment, the downstream inconstant bevel gear pairs 98 and 99 have a function of inconstant rotation (acceleration and deceleration) (the downstream inconstant speed bevel gear pairs 98 and 99 are employed). This point will be mainly described based on Figs. 10 and 9C. As shown in FIG. 10 (E), in forming a plurality of teeth 107 in the downstream inconstant speed bevel gear 98, the distance from the tip of each tooth 107 to the shaft center O1 is slightly widened and again. It is set to be narrower. That is, each tooth 107 is the pitch cone angle minimum portion 108 with the narrowest distance from the shaft center O1 to the tip, and the pitch cone angle maximum portion 109 with the largest distance from the shaft center O1 to the tip. The gap is gradually changed between the two.

In other words, as shown in Fig. 9C, the pitch circle 110 of each tooth 107 has a shape close to an ellipse or is eccentric with respect to the circle (indicated by 110 ', the pitch circle in the case of a circle is indicated by have). In the opposite view, the conventional bevel gear is inclined at the same angle with respect to the axial center at any portion of the virtual cone, but in the downstream inconstant speed bevel gear 98 of the embodiment, the outer circumferential surface of the virtual cone shifts in the circumferential direction. Accordingly, the inclination angle θ1 (see FIGS. 10A and 10C) of the outer circumferential surface is gradually changed.

The downstream inconstant speed driven bevel gear 99 has the teeth 112 of twice the number of teeth of the downstream inconstant speed bevel gear 98. And as can be clearly seen from FIG. 10 (A) and FIG. 10 (B), the position of each tooth 112 in the axial direction is shifted little by little. In other words, also in the downstream inconstant speed driven bevel gear 99 of the embodiment, the inclination angle θ2 of the outer circumferential surface as the outer circumferential surface of the virtual cone shifts in the circumferential direction similarly to the downstream inconstant speed bevel gear 98 (Fig. 10 (A) ) Is slowly changing.

Since the downstream inconstant speed bevel gear 99 is twice the number of teeth of the downstream inconstant speed bevel gear 98, the downstream inconstant speed bevel gear 98 is divided into two pitch cone angle maximums 113 and pitch cones. Each minimum part 114 has it. Therefore, as shown in FIG. 9 (C), the pitch circle 115 of the downstream inconstant speed driven bevel gear 99 is substantially elliptical, and is symmetrical with the shaft center O2 interposed therebetween (FIG. 9C). In the case of a round circle, the pitch circle is indicated by reference numeral 115 '). That is, the downstream inconstant bevel gear pairs 98 and 99 are continuously changing the pitch cone angles θ1 and θ2 along the rotational direction while keeping the cone distance Y (see FIG. 10 (C)) constant. will be. As can be seen from the above description, the downstream inconstant bevel gear pairs 98 and 99 as downstream inconstant speed members are single-stage, and the same as the upstream inconstant first to fourth gears 48, 56, 121 and 122 as the upstream inconstant speed member. No action (no speed switching).

In this manner, the pitch circles 110 and 115 of the downstream inconstant bevel gears 98 and 99 have a shape that is close to an ellipse or eccentrically with respect to a circle centered on the rotational axes (axial centers) O1 and O2, and then the outer diameter shape thereof is changed. By making the respective roundness, the pair of downstream inconstant bevel gears 98 and 99 can be formed in the size of a normal bevel gear, respectively, and the assembly space of the pair of downstream inconstant bevel gears 98 and 99 in the power transmission system can be reduced in size. · Compactness can be achieved. In this case, as a way of thinking of manufacturing the downstream inconstant bevel gears 99 and 99, the rotating shafts O1 and O2 are cut into a common cylinder so that the deformed cone shape formed by keeping the cone distance constant makes the outer diameter shape the origin.

Here, the downstream inconstant bevel gear pairs 98 and 99 also adjust the attachment phase similarly to the upstream inconstant first to fourth gears 48, 56, 121, and 122 so that the above-described highest speed phase is further away from the bottom dead center. The setting can be changed. FIG. 13 shows a change in the angular velocity of the planting relief 96 when it is set to 43 weeks of inequality as an example. The thick one-dot chain line in Fig. 13A shows the bottom dead center after assembling the upstream inconstant third gear 121 and the upstream inconstant fourth gear 122 so that the front side (upstream side) is the highest speed phase MS1 before the bottom dead center. It is a case where further downstream inconstant bevel gear pairs 98 and 99 are further assembled so that the front side becomes the highest speed phase MS1 '(refer FIG. 12). The thick solid line in FIG. 13 (B) assembles the upstream inconstant third gear 121 and the upstream inconstant fourth gear 122 so that the bottom dead center is at the highest speed phase MS2, and the downstream inconstant bevel gear pair 98 , 99). The thick dashed-dotted line of FIG. 13 (C) shows the bottom dead center after assembling the upstream inconstant third gear 121 and the upstream inconstant fourth gear 122 so that the rear side (downstream side) is the highest speed phase MS3 than the bottom dead center. It is a case where the downstream inconstant bevel gear pairs 98 and 99 are further assembled so that the rear side becomes the highest speed phase MS3 '(see FIG. 12). In such a configuration, the operation speed of the planting edible 96 is increased near the bottom dead center, thereby further enhancing the effect that the planting edible 96 can be quickly and accurately avoided from the bottom dead center.

(6). theorem

In FIG. 5C, the relationship between the number of planting shares per 3.3 m 2 and the operation trajectory of the planting relief 96 is shown. As can be understood from this figure, it can be understood that when the planting aid 96 rises directly from the bottom dead center, the evacuation of the planting aid 96 deteriorates and causes seedlings to fall when the news is reached.

In the embodiment, the upstream inconstant first to fourth gears 48, 56, 121, and 122 are provided in the weekly transmission device 26, and the downstream inconstant bevel gear pairs 98, 99 in the seedling planting device 2. By installing this, the planting aid member 37 accelerates and rotates so that the operation speed may become high in the vicinity of the planting aid 96 located in the bottom dead center. For this reason, the planting claw 96 is quickly avoided from the bottom dead center, and as a result, the phenomenon which makes a seedling fall to the planting claw 96 can be prevented.

In the embodiment, since the inconstant speed member is disposed separately from the weekly transmission 26 and the seedling planting device 2, the interval between the daytime transmission 26 and the downstream inconstant bevel gear pairs 98 and 99 is lower than that in the prior art. The rate of inconstant rotation is small. As a result, the torsion generated in the transmission elements constituting the power transmission system (PTO shaft 29, planting drive shaft 32, planting transmission shaft 87, etc.) is remarkably suppressed to ensure smooth movement of the transplant mechanism 8 Can be. In addition, recoil generated in the power transmission system can also be suppressed, thereby preventing the problem that the timing of the inconstant speed is shifted and the planting posture of the seedling is disturbed.

By the way, since the implantation mechanism 8 is a form in which the planting member 37 is swingably attached to both ends of the elongate rotary case 36, the planting member 37 itself acts as a weight and a large inertial force is generated. . In addition, a large load is generated when scraping seedlings, and a negative load is generated after that. That is, a large torque fluctuation occurs in the cycle of overload → no load → negative load with respect to the rotation of the implantation mechanism 8 due to the swing of the planting member 37. Such torque fluctuations are remarkable when the resonant rotation speed is exceeded even when the constant speed is rotated during the close type (because the implant mechanism 8 rotates at a higher speed than the news when the close type is closed).

To explain further, when one planting member 37 avoids from packing even when the implant mechanism 8 is rotated at constant speed, the other planting member 37 is shifted to some sort of scraping, and thus two planting aids It can be said that the member 37 acts so that the load variation of each other may be eliminated. However, since some types of scraping require a large torque, the function of leveling the torque fluctuation is weak only by the movement of the two planting members 37. For this reason, the implantation mechanism 8 does not rotate smoothly, and the phenomenon called "jerking" also becomes easy to occur.

On the other hand, when some inconstant rotation is given to the implantation mechanism 8 by the downstream inconstant bevel gear pairs 98 and 99 also in the closed state like embodiment, scraping of the seedling by the planting member 37 is inertial force. Since the implantation mechanism 8 is decelerated after the acceleration is performed while some kinds of scraping are performed, the large inertial force acting on the implantation mechanism 8 can be suppressed. For this reason, the load fluctuation (or torque fluctuation) acting on the implantation mechanism 8 can be leveled, and smooth rotation can be ensured.

(7). Other

The present invention can be variously embodied in addition to the above embodiments. For example, when the bevel gear is a downstream inconstant speed member, the first bevel gear pair 71a, 71b may be a downstream inconstant speed member, or the second bevel gear pair 88a, 88b may be a downstream inconstant speed member. Moreover, it is also possible to provide the inconstant speed member in three or more places of a power transmission system. In addition, the seedling planting apparatus 2 may be provided with a plurality of inconstant speed members on the traveling body without providing the inconstant speed members.

In addition, the weekly transmission 26 can also be incorporated in the mission case 11, and in this case, one upstream inconstant speed member is incorporated in the mission case 11. When the inconstant speed member is provided in each of the traveling body 1 and the seedling planting apparatus 2, the acceleration / deceleration ratio (inconstant speed ratio) may be set as necessary. Therefore, in some cases, it is also possible to make the acceleration / deceleration ratio (inconstant speed ratio) at the traveling body 1 side smaller than the inconstant speed conversion ratio in the seedling planting apparatus 2. In addition, the downstream inconstant bevel gear pairs 98 and 99, which are inconstant speed bevel gear mechanisms, are not limited to those applied to electric machines, and can be applied to all structures in order to generate and transmit inconstant rotation between rotation axes whose postures are crossed. .

1: traveling body 2: seedling planting device
8 implantation mechanism 10 engine
11: Mission Case 26: Weekly Transmission
36: rotary case 37: planting relief member
40: weekly case 41: input shaft
42: output shaft 45: intermediate shaft
48: upstream inconstant first gear 49: main clutch
51: idle shaft 56: upstream inconstant second gear
57: first intermediate clutch 87: planting transmission shaft
91: central axis of planting 96: planting aid
98: downstream inconstant speed bevel gear 99: downstream inconstant speed bevel gear
121: upstream inconstant third gear 122: upstream inconstant third gear
123: second intermediate clutch

Claims (6)

A seedling planting apparatus having a mission case for shifting power from an engine mounted on a traveling body, an implantation mechanism with a planting aid for drawing a non-circular motion trajectory, and operation of the transplantation mechanism with respect to the traveling speed of the traveling body In an implanter having a weekly transmission for changing the day by shifting speed,
The inconstant speed member which transmits the inconstant rotational power to the implantation mechanism is divided into an upstream inconstant member on the side of the main transmission device and a downstream inconstant member on the seedling planting device side, and the upstream inconstant speed member is switchable in multiple stages, The acceleration / deceleration ratios of the respective stages are different, and the downstream inconstant speed member is composed of a single stage,
In each of the stages of the upstream inconstant speed member, the highest speed phase at which the operation speed of the planting aid in the implantation mechanism becomes the highest speed can be set and changed.
The power transmission system from the daytime transmission to the implantation mechanism has rotation axes that cross each other, and is configured to transmit power via these bevel gear pairs via the bevel gear pairs. Composed of gears,
Each of the inconstant speed bevel gears is characterized in that the pitch cone angle is continuously changed along the rotational direction,
The pitch circle of each said inconstant bevel gear is a shape close to an ellipse, it is eccentric with respect to the circle centered on a rotating shaft, and the outer diameter of each said inconstant bevel gear is formed in a round shape. The method of claim 1,
And the downstream inconstant speed member can be set and changed in a direction further deviating from the front-back range or the bottom dead center with the bottom dead center interposed therebetween. The method according to claim 1 or 2,
And the weekly transmission device is provided on the traveling body side. delete delete delete

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