JP7139501B2 - rice transplanter - Google Patents

Description

TECHNICAL FIELD The present invention relates to a rice transplanter for continuously planting seedlings by mounting a seedling planting device having a seedling platform and a plurality of planting claws on a traveling machine body.

In the conventional rice transplanter, a seedling planting device having a seedling platform and a transplanting mechanism with planting claws is attached to the rear part of the running body. As a transplanting mechanism of a seedling planting apparatus, a type in which two planting claws are provided in one rotary case is common, and when the rotary case rotates once, the two planting claws are opposite to each other with respect to the rotary case. Rotate one direction. That is, the planting claw rotates while revolving around the axis of the rotary case.

In a seedling planting operation using this type of rice transplanter, a seedling mounting table on which a seedling mat is placed is intermittently laterally fed at predetermined intervals, and the planting claws facing toward the front seedling mounting table are moved. By rotating the rotary case while revolving around its axis, the planting claws are reciprocated between the seedling mounting table and the field, and the seedlings are scraped off from the seedling mat one by one and planted in the field. The operating cycle (planting cycle) of the planting claws in the seedling planting device is interlocked with the running speed of the traveling machine body, and the seedling planting interval (between plants) is kept constant even if the running speed changes.

The number of seedlings to be planted per unit area (generally 3.3 square meters) is not always constant, and the desired number of seedlings to be planted per unit area varies, for example, depending on the region or user. In this regard, the conventional rice transplanter is provided with an inter-plant transmission that adjusts the interlocking relationship between the running speed and the planting cycle. In this case, by changing the operation speed (planting speed) of the transplanting mechanism with respect to the running speed by the inter-plant distance transmission, the inter-plant distance is changed, and the number of planted plants per unit area is changed.

In recent years, considering the growth conditions of seedlings planted in fields, sparse planting is practiced with longer spacing between plants than in standard planting. However, the longer the spacing between plants, the slower the planting speed. However, if the planting speed is simply slowed down by the inter-plant speed changer, the tips of the planting claws are dragged in the field, causing problems such as the seedlings falling forward or floating seedlings.

In this regard, Patent Documents 1 and 2 disclose a rice transplanter equipped with a non-uniform speed member for transmitting non-uniform rotational power to a transplanting mechanism in order to prevent the planting claws from being dragged in the field during sparse planting. A structure is disclosed. The non-uniform velocity member is configured to change the angular velocity during one rotation of the rotary case that constitutes the transplanting mechanism (non-uniform rotation). there is In the rice transplanter of Patent Literature 1, a non-uniform speed member is incorporated in the transmission between plants in the mission case. In the rice transplanter of Patent Literature 2, a non-uniform-speed member is provided on the downstream side of the power transmission from the lateral feed drive mechanism of the seedling mounting table.

Japanese Patent No. 4376154 Japanese Patent Application Laid-Open No. 2003-189712

Now, the power switching structure of the transmission between the stocks includes the one that shifts the speed in stages and the one that shifts the speed continuously. was there.

SUMMARY OF THE INVENTION The present invention has been made in view of the above-described current situation, and aims to prevent the drawbacks thereof while enjoying the advantages of the non-uniform velocity member.

A rice transplanter according to one aspect of the present invention includes a seedling planting device supported by a traveling portion, a power transmission to the seedling planting device, and operation of the seedling planting device with respect to a traveling speed of the traveling portion. and an inter-plant transmission capable of changing the speed, the inter-plant transmission can switch the power transmitted to the seedling planting device in a plurality of stages, and the inter-plant transmission is capable of transmitting power to the seedling planting device. A power transmission path includes a first switching mechanism and a second switching mechanism for switching input power between a plurality of gear stages, and each gear stage selected by the first switching mechanism and the second switching mechanism is provided. It is possible to switch the power transmitted to the seedling planting device in combination, and among the plurality of powers, the sparse planting power, which has the slowest operating speed of the seedling planting device with respect to at least the running speed, is selected by the first switching mechanism. By selecting a planting gear stage and selecting a corresponding specific gear stage in the second switching mechanism, it is configured to transmit to the seedling planting device.

The sparse planting gear stage of the first switching mechanism may be a non-uniform speed member that transmits power at a non-uniform speed.

The inter-plant transmission device has at least two sparse planting gear stages in the first switching mechanism, and the second switching mechanism has different specific gear stages respectively corresponding to the sparse planting gear stages of the first switching mechanism. It may be a configuration having a gear stage of .

The first switching mechanism has a plurality of transmission gears aligned axially with the shaft, the non-uniform speed member of the sparsely planted shift stage is a non-uniform gear, and the non-uniform gear comprises a plurality of transmission gears. It may be arranged in the axial end of the transmission gear.

The shaft includes an output shaft that transmits power to the seedling planting device, an input shaft arranged concentrically with the output shaft, and an intermediate shaft fitted to the input shaft while rotating together with the output shaft. , wherein, among the plurality of transmission gears, the non-uniform gear may be fitted to the intermediate shaft so as to be relatively rotatable, and the remaining transmission gears may be fitted to the intermediate shaft so as not to be relatively rotatable. .

A non-uniform gear is also arranged inside the rotary case that constitutes the transplanting mechanism, and this causes the planting claws to move so as to draw a non-circular motion locus that is long in the vertical direction. It is different from an unequal-speed member (that is, a member that imparts unequal-speed rotation (acceleration/deceleration) to a transmission element of a power transmission system).

ADVANTAGE OF THE INVENTION According to this invention, in the transmission between plants which can change the working speed of a seedling planting apparatus with respect to the driving|running|working speed of a driving|running|working part, the power switching structure which tends to become complicated can be simplified.

It is a top view of a rice transplanter concerning an embodiment. It is a side view of a rice transplanter. It is a perspective view which shows the framework of a rice transplanter. (A) is a perspective view showing the entire power transmission path, and (B) is a perspective view of the implantation mechanism. (A) is a side view of the power transmission path, (B) is a side view of the portion of the transplanting mechanism, and (C) is a diagram showing the trajectory of the planting nail. (A) is a plan view showing a power transmission path, (B) is an external perspective view of a device for changing the distance between plants, and (C) and (D) are external perspective views of a center case provided in a planting portion. (A) is an external perspective view of a spacing changing device and a group of gears in a center case, and (B) is a perspective view of a group of gears in the center case. It is a transmission system diagram. (A) is a plan view showing the power transmission path to the planting device, (B) is an isolated plan view of the terminal planting portion of the power transmission path, and (C) is a schematic diagram of the bevel gear. (A) and (B) are plan views showing meshing states of bevel gears, (C) and (D) are perspective views of bevel gears, and (E) is a comparison view in which a pair of bevel gears are arranged. It is a chart which shows the relationship between the combination of the gear in a transmission between plants, and the number of planted plants. It is a figure which shows the movement locus|trajectory of the planting nail|claw at the time of setting to 43 strains of non-uniform speed. It is a figure which shows the angular velocity change of the planting nail|claw at the time of setting to 43 strains of non-uniform velocity. FIG. 4 is a plan view showing the arrangement structure of the transplantation mechanism in the first embodiment; It is plane sectional drawing which shows the power transmission structure in a planted transmission case. It is an enlarged plan sectional view of the planted transmission case rear part. It is an expanded side sectional view of the planted transmission case rear part. FIG. 4 is a diagram showing the relationship between the rotational torque and antiphase torque of the implantation mechanism; It is a power transmission system diagram from a planted transmission case to a transplantation mechanism in the second embodiment. It is a power transmission system diagram from a planted transmission case to a transplantation mechanism in the 3rd embodiment. It is a power transmission system diagram from a planted transmission case to a transplantation mechanism in the 4th embodiment. FIG. 11 is an explanatory diagram schematically showing a non-uniform velocity member in a fourth embodiment; FIG. 11 is an explanatory diagram schematically showing a non-uniform velocity member in a fifth embodiment; FIG. 11 is an explanatory diagram schematically showing a non-uniform velocity member in a sixth embodiment; FIG. 11 is an explanatory diagram schematically showing a non-uniform velocity member in a seventh embodiment; FIG. 20 is an explanatory diagram schematically showing a non-uniform velocity member in an eighth embodiment; FIG. 21 is an explanatory diagram schematically showing a non-uniform velocity member in a ninth embodiment;

Next, embodiments of the present invention will be described based on the drawings. The embodiment is applied to a riding-type rice transplanter (hereinafter simply referred to as "rice transplanter"). In the following description, terms of front/rear and left/right are used to specify the direction, and the terms front/rear and left/right define the advancing direction of the rice transplanter as forward. The front view direction is the direction opposite to the advancing direction.

(1). Overview of Rice Transplanter First, an overview of the rice transplanter will be described with reference to FIGS. 1 to 5. FIG. As shown in FIGS. 1 to 3, the rice transplanter has a traveling body 1 and a seedling planting device 2 arranged behind it. The traveling body 1 has front and rear wheels 3, 4, an operating seat 5, and an operating handle 6, while the seedling planting device 2 has a seedling mounting base 7 on which a seedling mat is placed and a transplanting mechanism 8. - 特許庁The rice transplanter of the embodiment is of the 8-row planting type, and for this reason, the seedling mounting table 7 is formed with 8 seedling mat mounting areas, and the rear part of the seedling planting device 2 is equipped with 8 transplanting mechanisms. 8 are arranged in a row.

As shown in FIG. 3, the traveling machine body 1 has a framework 9 made up of a large number of frame members, and an engine 10 is supported on the front part of the framework 9 . A transmission case 11 is arranged behind the engine 10 . As clearly shown in FIG. 4A, a hydrostatic continuously variable transmission (HST) 12 is attached to the left side of the mission case 11, and the power of the engine 10 is hydrostatically continuously variable by a belt 13. is transmitted to the machine (HST) 12 . Engine 10 is covered with bonnet 14 . A vehicle body cover 15 covers the traveling body 1 except for the bonnet 14 .

A front axle device 17 is attached to the left and right side surfaces of the transmission case 11 , and the front wheel 3 is attached to the front axle device 17 . A rear axle case 18 is arranged behind the transmission case 11, and a rear wheel 4 is attached to a rear axle projecting laterally from the rear axle case 18. - 特許庁The transmission case 11 and the rear axle case 18 are connected by a longitudinal joint member 19 . Two left and right rear struts 20 are attached to the rear axle case 18, and the upper ends of the rear struts 20 are fixed to the left and right horizontally elongated rear frames 9a (see FIG. 3) forming the rear ends of the framework 9. .

A link device 21 composed of upper and lower link bodies (top link and lower link) is rotatably connected to the left and right rear struts 20, and the seedling planting device 2 is attached to the rear end of the link device 21. . The link device 21 can be rotated by a hydraulic cylinder (elevating cylinder) 22 connected to the joint member 19 . Therefore, the seedling planting device 2 moves up and down by extending and retracting the hydraulic cylinder 22 .

As can be easily understood from FIG. 4, power is transmitted from the inside of the transmission case 11 to the inside of the rear axle case 18 via the rear wheel drive shaft 23 . Rotation of the rear wheel drive shaft 23 is transmitted to the rear wheels 4 through a gear group provided on the rear axle case 18 . In the rice transplanter of the embodiment, the seedling planting device 2 is provided with a leveling rotor 24 , and power is transmitted to the leveling rotor 24 by a rotor drive shaft 25 projecting backward from the rear axle case 18 .

In the embodiment, a plant-to-plant transmission 26 is attached to the right side of the rear axle case 18 , and power is transmitted from the transmission case 11 to the plant-to-plant transmission 26 via a planting power transmission shaft 27 . The rotation of the planting power transmission shaft 27 is changed in speed by a group of gears built in the interplant transmission 26 and transmitted to the seedling planting device 2 by the PTO shaft 29 .

The seedling planting device 2 has a horizontally elongated main frame 28. A center case 30 is fixed to substantially the left and right intermediate portions of the main frame 28, and the power of the PTO shaft 29 is a gear built in the center case 30. transmitted to the flock. Four planted transmission cases 31 extending rearward are fixed to the rear surface of the main frame 28, and a pair of right and left transplanting mechanisms 8 are rotatably attached to the rear side of the planted transmission cases 31.例文帳に追加

A laterally long planting drive shaft 32 passes through the front side (base end side) of the planting transmission case 31, and the rotation of this planting drive shaft 32 drives the transplanting mechanism 8 (details will be described later). do). Further, power is transmitted from the PTO shaft 29 to the planted drive shaft 32 via a gear group built in the center case 30 . A horizontally elongated lateral feed shaft 33 is also attached to the center case 30, and the rotation of the lateral feed shaft 33 causes the seedling mounting table 7 to laterally move one pitch at a time.

The seedling planting device 2 has a group of belts 34 on which seedling mats are placed, and the belts 34 are wound around a pair of upper and lower vertical feed spindles 35 . When the seedling mounting table 7 is completely moved to either the left or right, the vertical feed spindle 35 rotates and the seedling mat moves downward by one pitch.

As shown in FIG. 4B, each transplanting mechanism 8 has one rotary case 36 and planting claw members 37 rotatably provided at both ends thereof. The seedlings are scraped and planted by the planting claw member 37 each time. Further, the rotary case 36 is set to rotate 1/2 when the PTO shaft 29 makes one rotation. The number of revolutions of the PTO shaft 29 is basically proportional to the running speed of the traveling machine body 1, but by changing the relationship between the running speed and the number of revolutions of the PTO shaft 29 with the transmission between plants 26, seedlings can be planted. Spacing (between plants) can be changed.

(2). Structure and power transmission structure of inter-stall transmission (upstream inconstant speed member)
The details of the power transmission system from the inter-row transmission 26 to the transplanting mechanism 8 will be described below. First, the structure of the inter-stall transmission 26 and the power transmission structure therefor will be described mainly with reference to FIGS. The inter-row transmission 26 has an inter-row case 40 split into front and rear halves as shown in FIG. .

An input shaft 41 and an output shaft 42 are arranged inside the case 40 between plants, and the rear end of the planting power transmission shaft 27 is connected to the input shaft 41 via a universal joint. A first gear 43 and a 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 of the second gear 44 is slightly smaller than that of the first gear 43 .

The input shaft 41 and the output shaft 42 are arranged concentrically. A cylindrical intermediate shaft 45 is fitted to the input shaft 41 so as to be relatively rotatable, and the intermediate shaft 45 is fitted so as to be rotatable together with the output shaft 42 (not relatively rotatable). A third gear 46 and a fourth gear 47 are fitted to the intermediate shaft 45 by spline fitting or the like so as to be slidable and non-rotatable relative to each other. Further, the intermediate shaft 45 is fitted with an upstream non-uniform first gear 48 and an upstream non-uniform third gear 121 so as to be relatively rotatable.

A cam-type main clutch 49 is provided on the output shaft 42 . The main clutch 49 consists of a fixed part 49a and a slide part 49b, and the slide part 49b is biased toward the fixed part 49a by a clutch spring 49c (see FIG. 7(C)). When the slide part 49b separates from the fixed part 49a against the clutch spring 49c, power transmission from the input shaft 41 to the output shaft 42 is interrupted. The main clutch 49 is disengaged when the seedling planting device 2 is raised, such as when traveling on the road or turning. Disengaging operation of the main clutch 49 is performed by lowering the main clutch operating shaft 50 .

An idle shaft 51 extending parallel to the input shaft 41 and the output shaft 42 in a side view is rotatably supported inside the case 40 between plants. A meshable fifth gear 52 is fitted by spline fitting or the like so as to be slidable and non-rotatable relative to each other. The fifth gear 52 has about twice the number of teeth of the first gear 43 or the second gear 44, and can select a first position meshed with the first gear 43 or a second position meshed with the second gear 44. .

The idle shaft 51 is provided with an upstream inconstant-speed fourth gear 122 that is always meshed with an upstream inconstant-speed third gear 121, a sixth gear 54 that meshes with and disengages from the third gear 46, and a fourth gear 47. - A seventh gear 55 that separates and a second upstream non-uniform-speed gear 56 that is always meshed with the first upstream non-uniform-speed gear 48 are fixed. The ratio of the number of teeth of the seventh gear 55 to the fourth gear 47 is set to be smaller than the ratio of the number of teeth of the seventh gear 54 to the third gear 46 . Therefore, the rotation speed of the intermediate shaft 45 (and the output shaft 42) is higher when the fourth gear 47 and the seventh gear 55 are engaged than when the third gear 46 and the sixth gear 54 are engaged. is lower.

The upstream non-uniform first gear 48 and the upstream non-uniform second gear 56 have a non-circular profile such as an ellipse, and have the same number of teeth. Therefore, in a state in which the rotation of the idle shaft 51 is transmitted to the intermediate shaft 45 and the output shaft 42 via the non-uniform gears 48 and 56, the rotation speeds of the idle shaft 51 and the output shaft 42 are the same, and , the output shaft 42 rotates with the angular velocity periodically changed during one rotation. Both of the non-uniform gears 48 and 56 are non-circular and are always maintained in a meshing state due to the peculiarity that the meshing phase is always determined. Similarly, the upstream non-uniform speed third gear 121 and the upstream non-uniform speed fourth gear 122 also have a non-circular profile such as an ellipse, and have the same number of teeth. Therefore, in a state in which the rotation of the idle shaft 51 is transmitted to the intermediate shaft 45 and the output shaft 42 via the non-uniform gears 48 and 56, the rotation speeds of the idle shaft 51 and the output shaft 42 are the same, and , the output shaft 42 rotates with the angular velocity periodically changed during one rotation. That is, the upstream non-uniform first gear 48 and the upstream non-uniform second gear 56 are non-circular gear pairs such as eccentric gears, and have a large acceleration/deceleration ratio (non-uniform speed ratio). The upstream non-uniform speed third gear 121 and the upstream non-uniform speed fourth gear 122 are also non-circular gear pairs such as eccentric gears, but have a small acceleration/deceleration ratio (non-uniform speed ratio).

Here, in the rotary case 36, the maximum speed phase of each planting claw 96 in the planting claw member 37 (the phase at which the operation speed of the planting claw 96 becomes the maximum speed) is set when, for example, 37 plants/m2 are sparsely planted. Acceleration and deceleration are applied to the vicinity of the bottom dead center, but in addition, in the embodiment, the upstream inconstant speed first gear 48 and the upstream inconstant speed second gear 56 provided in the inter-plant transmission 26 A slightly large acceleration/deceleration is applied to the rotational power from the inter-plant case 40 to output non-uniform rotational power. Therefore, since the acceleration/deceleration ratio (non-uniform speed ratio) is larger than the combination of the upstream non-uniform speed third gear 121 and the upstream non-uniform speed fourth gear 122, near the bottom dead center of the operation locus of the planting claw 96, greatly increases the operating speed of In addition, the upstream non-uniform speed third gear 121 and the upstream non-uniform speed fourth gear 122 impart a slightly smaller acceleration or deceleration to the rotational power from the case between plants 40 to output the non-uniform rotational power. Therefore, since the acceleration/deceleration ratio (non-uniform speed ratio) is smaller than the combination of the upstream non-uniform speed first gear 48 and the upstream non-uniform speed fourth gear 56, the operation locus of the planting claw 96 near the bottom dead center to increase the operating speed of The upstream inconstant-speed first to fourth gears 48 , 56 , 121 , 122 correspond to upstream inconstant-speed members on the inter-stock transmission 26 side that transmit the inconstant-speed rotational power to the transplanting mechanism 8 .

The fourth gear 47 and the upstream non-uniform first gear 48 are provided with a first intermediate clutch 57 that can be engaged and disengaged. When the fourth gear 47 is once engaged with the seventh gear 55 from the state shown in FIG. 8 and further slides rightward, the first intermediate clutch 57 is engaged. When the first intermediate clutch 57 is engaged, the power of the idle shaft 51 is transmitted to the output shaft 42 via the upstream non-uniform second gear 56 and the upstream non-uniform first gear 48 . When the first intermediate clutch 57 is engaged, the third gear 46 and the fourth gear 47 are idling. Therefore, the first intermediate clutch 57 functions to connect and disconnect the intermediate shaft 45 and the first upstream non-uniform speed gear 48 .

Further, the third gear 46 and the upstream non-uniform-speed third gear 121 are also provided with a second intermediate clutch 123 that can be freely engaged and disengaged. When the third gear 46 is once engaged with the sixth gear 54 from the state shown in FIG. 8 and further slides leftward, the second intermediate clutch 123 is engaged with the intermediate shaft 45 . When the second intermediate clutch 123 is engaged, the power of the idle shaft 51 is transmitted to the output shaft 42 via the upstream non-uniform fourth gear 122 and the upstream non-uniform third gear 121 . Also in this case, if the second intermediate clutch 123 is engaged, the third gear 46 and the fourth gear 47 idle. Therefore, the second intermediate clutch 123 functions to connect and disconnect the intermediate shaft 45 and the upstream non-uniform speed third gear 121 .

By sliding the fifth gear 52, two-stage switching is performed, and by sliding the intermediate shaft 45, four-stage switching is performed. Therefore, there are eight combinations (speed switching) in total. For example, the number of stocks per 3.3 square meters can be changed to 37 to 85, and almost all areas of sparse planting and dense planting are covered. FIG. 11 shows the relationship between the gear combination and the number of planted strains in the embodiment. When the first gear 43 and the fifth gear 52 are meshed, if the fourth gear 47 and the seventh gear 55 are meshed, the number of planted stocks is set to the constant speed d stock, and the third gear 46 and the sixth gear are engaged. When the gear 54 is meshed, the number of plants to be planted is set to f plants at a constant speed. If the second intermediate clutch 123 is engaged, the number of planted stocks is set to b stocks with non-uniform speed. When the second gear 44 and the fifth gear 52 are meshed, if the fourth gear 47 and the seventh gear 55 are meshed, the number of plants to be planted is set to a constant speed c strain, and the third gear 46 and the sixth gear are engaged. If the gear 54 is meshed, the number of plants to be planted is set to the constant speed e strain. If the first intermediate clutch 57 is engaged, the number of plants to be planted is set to the non-uniform speed a strain. In this case, the number of stocks shown in alphabetical order is large in alphabetical order.

Here, the upstream non-uniform first to fourth gears 48, 56, 121, 122 are assembled to the intermediate shaft 45 and the idle shaft 51 by adjusting the mounting phase, thereby controlling the operation of the planting claw 96 in the transplanting mechanism 8. The maximum speed phase at which the speed reaches the maximum speed can be changed in the range before and after the bottom dead center. FIG. 12 shows, as an example, the motion locus of the planting claw 96 when the speed is set to 43 stocks at a non-uniform speed. Reference numeral MS1 in FIG. 12 designates the upstream non-uniform speed third gear 121 and the upstream non-uniform speed fourth gear 122 so that the operation speed of the planting claw 96 reaches the highest speed on the front side (upstream side) of the bottom dead center. MS2 is the maximum speed phase when assembled, and MS2 is the upstream non-uniform speed third gear 121 and the upstream non-uniform speed fourth gear 122 so that the planting claw 96 operates at the maximum speed near the bottom dead center. This is the highest speed phase when the Reference numeral MS3 indicates that the upstream inconstant-speed third gear 121 and the upstream inconstant-speed fourth gear 122 are assembled so that the operating speed of the planting claw 96 becomes the highest on the rear side (downstream side) of the bottom dead center. is the fastest phase in the case.

Depending on the relationship with assembly accuracy, for example, the upstream inconstant speed third gear 121 and the upstream inconstant speed fourth gear 122 may be assembled so that the front side (upstream side) from the bottom dead center is the maximum speed phase MS1. , the upstream inconstant speed third gear 121 and the upstream inconstant speed fourth gear 122 are assembled so that the vicinity of the bottom dead center is the highest speed phase MS2, and furthermore, the rear side (downstream side) of the bottom dead center is the highest speed It is possible to assemble the upstream non-uniform third gear 121 and the upstream non-uniform fourth gear 122 so that the phase is MS3. That is, for example, when the torsion of the power transmission system is large and there is a concern that the operation cycle deviation of the planting claw 96 may occur due to the relationship with the assembly accuracy, or when the torsion of the power transmission system is small and the vibration of the power transmission system is minimized. If you want to suppress it, you can change the setting of the maximum speed phase to around the bottom dead center. By doing so, it is possible to suppress the so-called "jerking" of the planting claw 96 and suppress the vibration of the power transmission system. Needless to say, the upstream non-uniform first gear 48 and the upstream non-uniform second gear 56 may be assembled to the intermediate shaft 45 and the idle shaft 51 by adjusting the mounting phase.

A fertilizing rotary shaft 58 extending parallel to the input shaft 41 and the output shaft 42 is rotatably arranged in the upper portion of the case 40 between plants. A gear 59 is fitted so as to be relatively rotatable. Power is transmitted from the fertilizing rotary shaft 58 to the fertilizing driving shaft 62 via the bevel gear 61 .

As shown in FIG. 7(A), the inter-share transmission 26 has two operating shafts, a first operating shaft 63 and a second operating shaft 64 . These operating shafts 63 and 64 are in a longitudinally long position and are exposed in front of the interplant case 40 . 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 can be slid back and forth by the second lever 66. As shown in FIG. The first operating shaft 63 is for sliding the fifth gear 52 and has a shifter for sliding the fifth gear 52 . The second operating shaft 64 is for sliding the intermediate shaft 45 and has a shifter that engages with the intermediate shaft 45 .

(3). Internal Structure of Center Case Next, the internal structure of the center case 30 (that is, the planting portion transmission) will be described with reference to FIGS. 6 to 8. FIG. The center case 30 consists of a left and right divided shell body, and a longitudinal input shaft 69 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.

A left-right longitudinal intermediate shaft 70 is arranged inside the center case 30, 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. A lateral feed drive shaft 72 is arranged in the interior of the center case 30 so as to extend horizontally, and the lateral feed shaft 33 is connected to the lateral feed drive shaft 72 .

Three traverse amount adjusting driven gears 73 are fixed to the traverse driving shaft 72, while three traverse amount adjusting main drive gears are attached to the intermediate shaft 70 corresponding to the traverse amount adjusting driven gears 73. 74 is loosely fitted. Power is selectively transmitted from the intermediate shaft 70 by a slide key 76 (see FIG. 8) to only one of the three transverse feed amount adjusting main driving gears 74 . The slide key 76 is slidably operated by a slide lever 77 shown in FIGS. 6(C), 6(D), 7(A), and 7(B).

The pair of traversing amount adjusting gears 73 and 74 have different tooth ratios, and changing the combination of the traversing amount adjusting gears 73 and 74 changes the rotation ratio of the traversing drive shaft 72 with respect to the PTO shaft 29. . As a result, the lateral feeding pitch of the seedling mounting table 7 changes, and the scraping amount of seedlings changes.

The center case 30 has an overhanging portion 30a that extends rearward and downward. a first intermediate gear 79 fixed to the , a second intermediate gear 80 fitted to the transverse drive shaft 72 in a relatively rotatable manner, a third intermediate gear 82 rotatably held in the center case 30 via an idle shaft 81, and the fourth relay gear 84 to transmit power. The fourth relay gear 84 is attached to the planting output shaft 78 via a sleeve 83 .

The ratio of the number of teeth of the first bevel gears 71a and 71b is 1:1, and the number of teeth of the first relay gear 79, the second relay gear 80 and the fourth relay gear 84 is 1:1:1. in a relationship. Therefore, the rotational speeds of the PTO shaft 29 and the planting output shaft 78 are in a 1:1 relationship. Since the third intermediate gear 82 is a mere idle gear, the number of teeth thereof does not affect the rotational speed of the fourth intermediate gear 84 .

The planting output shaft 78 and the adjacent planting drive shaft 32 are connected by a coupling (sleeve) 86 . A relay shaft 85 is arranged between the planting drive shafts 32 adjacent to each other on the left and right, and the drive shaft 32 and the relay shaft 85 are also connected by a coupling 86 . Therefore, each planting drive shaft 32 rotates together. The planting drive shaft 32 is divided for each planting mechanism 8 , and adjacent planting drive shafts 32 are connected by springs 86 . The planting output shaft 78, each planting drive shaft 32, and the relay shaft 85 may be formed into a single structure made of one bar.

(4). Structure and Power Transmission Structure of the Implantation Mechanism Next, the structure of the transplantation mechanism 8 and the power transmission structure therefor will be described. These constitute the main part of the embodiment, and are mainly shown in FIGS. 8 to 10 (see also FIG. 6(A)). The planted transmission case 31 has a hollow structure, and as shown in FIG. 8, a planted transmission shaft 87 extending in the front-rear direction is rotatably held therein.

Power is transmitted from the planted drive shaft 32 to the planted transmission shaft 87 through a second bevel gear pair 88a, 88b. A bevel gear 88b of the second bevel gear pair 88a, 88b, which rotates concentrically with the transmission shaft 87 with planting, is attached to a torque limiter 89 fitted on the transmission shaft 87 with planting. The torque limiter 89 has a spring 90, and when a load exceeding a predetermined level is applied to the transmission shaft 87 with plants, the mesh is disengaged and power transmission is cut off.

On the rear side (front end side) of the planting transmission case 31, a laterally long planting center shaft 91 is rotatably held via a pair of left and right bearings 104. As shown in FIG. The planting center shaft 91 protrudes to the left and right outside of the planting transmission case 31, and the sun gear 92 incorporated in the rotary case 36 is fixed to the protruding end. Although details are omitted, the rotary case 36 is rotatably held at the rear end portion of the planting transmission case 31 .

The rotary case 36 has a hollow structure in which two left and right shell bodies are superimposed on each other. A gear 94 is arranged. Each gear 92, 93, 94 is non-circular and eccentric. A planting claw member 37 is fixed to a unit shaft 95 fixed to a planetary gear 94 .

As clearly shown in FIG. 5, the planting claw member 37 has a planting claw 96 and a projecting rod 97. As shown in FIG. The seedlings are planted in the field by cutting off the seedlings only by the amount and transferring to the field, and moving the protruding rod 97 forward relative to the planting claws 96 in the vicinity of the bottom dead center.

As shown in FIG. 9 , power is transmitted from a planting transmission shaft 87 to the planting center shaft 91 by a downstream non-uniform bevel gear pair 98 , 99 . That is, while a downstream inconstant velocity driving bevel gear 98 is fixed to the planting transmission shaft 87 via a coupling 100, a downstream inconstant velocity driven bevel gear 99 is fitted to the planting center shaft 91. Non-uniform rotation is transmitted from the planting transmission shaft 87 to the planting center shaft 91 by the non-uniform bevel gear pair 98 and 99 .

The downstream non-constant velocity driving bevel gear 98 has a stepped boss body 98a, and the coupling 100 is fitted to the small diameter portion of the boss body 98a. A bearing 101 is fitted in the boss body 98a. The coupling 100 is fixed by welding to the planted transmission shaft 87 and is held so as not to be relatively rotatable. The downstream non-uniform-velocity driven bevel gear 99 is fitted to the planting center shaft 91 so as to be relatively rotatable, and has a cam portion 103 that meshes with a row-stopping clutch 102 . An operation ring 105 is integrally welded to the row-stopping clutch 102 .

The row stopping clutch 102 is slidably held on the planting center shaft 91 and is relatively non-rotatable. The row-stopping clutch 102 is normally pushed by a spring 106 into mesh with the downstream non-uniform-velocity driven bevel gear 99 . When the operating rod 129 is operated, the row stopping clutch 102 is separated from the downstream non-uniform-velocity driven bevel gear 99 along the axis of the planting center shaft 91, and the power to the planting center shaft 91 is cut off.

For example, in the planting work at the edge of a furrow, there are cases where some of the four pairs of transplanting mechanisms 8 do not want to operate. can stop functioning. In other words, a row-stopping function that reduces the number of planted rows is exhibited.

(5). Downstream Inconsistent Velocity Member In the embodiment, the downstream inconstant velocity bevel gear pair 98, 99 is provided with a function of inconstant rotation (acceleration/deceleration) (the downstream inconstant velocity bevel gear pair 98, 99 are employed). This point will be explained mainly based on FIG. 10 and FIG. 9(C). As shown in FIG. 10(E), in forming a large number of teeth 107 on the downstream non-uniform main bevel gear 98, the distance from the tip of each tooth 107 to the axis O1 is set to widen and narrow again. is doing. That is, each tooth 107 has a minimum pitch cone angle portion 108 with the shortest distance from the axis O1 to the tip and a maximum pitch cone angle portion 109 with the widest distance from the axis O1 to the tip, The interval between them gradually changes.

In other words, as shown in FIG. 9C, the pitch circle 110 of each tooth 107 has a shape close to an ellipse and is eccentric with respect to the perfect circle (reference numeral 110' indicates the pitch circle in the case of a perfect circle. ing). Stated from the opposite point of view, in a normal bevel gear, the outer peripheral surface of the virtual cone is inclined at the same angle with respect to the axis at any part. As the outer peripheral surface of the cone shifts in the circumferential direction, the inclination angle θ1 (see FIGS. 10A and 10C) of the outer peripheral surface is gradually changed.

The downstream inconstant velocity driven bevel gear 99 has teeth 112 twice the number of teeth of the downstream inconstant velocity driving bevel gear 98 . As can be clearly understood from FIGS. 10A and 10B, the axial position of each tooth 112 is shifted little by little. In other words, in the downstream inconstant-velocity driven bevel gear 99 of the embodiment, as in the downstream inconstant-velocity driving bevel gear 98, the inclination angle θ2 of the outer peripheral surface (Fig. 10 (A)) is gradually changed.

Since the downstream inconstant velocity driven bevel gear 99 has twice the number of teeth of the downstream inconstant velocity main bevel gear 98, the downstream inconstant velocity driven bevel gear 99 has two maximum pitch cone angle portions 113 and two minimum pitch cone angle portions. It has a part 114 . Therefore, as shown in FIG. 9(C), the pitch circle 115 of the downstream non-uniform-velocity driven bevel gear 99 has a substantially elliptical shape and is symmetrical with respect to the axis O2 (FIG. 9(C) ), the pitch circle in the case of a perfect circle is indicated by reference numeral 115'). That is, the downstream non-uniform bevel gear pair 98, 99 continuously changes the pitch cone angles θ1, θ2 along the rotation direction while keeping the cone distance γ (see FIG. 10(C)) constant. of. As can be seen from the above description, the downstream inconstant-velocity bevel gear pair 98, 99 as the downstream inconstant-velocity member is a single stage, and the upstream inconstant-velocity first to fourth gears 48, 56 as the upstream inconstant-velocity member. , 121 and 122 do not perform speed change operation (there is no speed change).

In this way, the pitch circles 110 and 115 of the downstream non-uniform bevel gears 98 and 99 are made eccentric with respect to the perfect circles centered on the rotation axes O1 and O2, which are nearly elliptical. By forming the respective circles, the pair of downstream non-uniform bevel gears 98 and 99 can be formed to the same size as normal bevel gears, and the assembly space for the pair of downstream non-uniform bevel gears 98 and 99 in the power transmission system is reduced. can be made smaller and more compact. In this case, the concept of manufacturing the downstream non-uniform bevel gears 98 and 99 is to cut the distorted conical shape formed with a constant conical distance by a cylinder having a common rotation axis O1 and O2 to make the outer diameter shape true. It means making a circle.

Here, the downstream inconstant-velocity bevel gear pair 98, 99 also adjusts the mounting phase in the same manner as the upstream inconstant-velocity first to fourth gears 48, 56, 121, 122 so that the above-described highest speed phase is at the bottom dead center. It is possible to change the setting in the direction further away from. FIG. 13 shows, as an example, changes in the angular velocity of the planting claw 96 when 43 strains are set at a non-uniform speed. The thick one-dot chain line in FIG. 13(A) shows the top of the upstream inconstant speed third gear 121 and the upstream inconstant speed fourth gear 122 assembled so that the front side (upstream side) of the bottom dead center is the maximum speed phase MS1. In this case, the downstream inconstant velocity bevel gear pair 98, 99 is assembled so that the front side of the bottom dead center is the maximum velocity phase MS1' (see FIG. 12). The thick solid line in FIG. 13B indicates that the upstream inconstant-speed third gear 121 and the upstream inconstant-speed fourth gear 122 are assembled and the downstream inconstant-speed bevel gear pair is assembled so that the vicinity of the bottom dead center is the maximum speed phase MS2. This is the case where 98 and 99 are assembled. The thick two-dot chain line in FIG. 13(C) indicates that the upstream inconstant-speed third gear 121 and the upstream inconstant-speed fourth gear 122 are assembled so that the rear side (downstream side) of the bottom dead center is the maximum speed phase MS3. In addition, the downstream inconstant velocity bevel gear pair 98, 99 is assembled so that the rear side of the bottom dead center is the maximum velocity phase MS3' (see FIG. 12). With this configuration, the operating speed of the planting claw 96 increases near the bottom dead center, and the effect of allowing the planting claw 96 to escape from the bottom dead center accurately and quickly can be further enhanced.

(6). Summary FIG. 5(C) shows the relationship between the number of plants planted per 3.3 square meters and the movement trajectory of the planting claw 96 . As can be understood from this figure, even if the planting claw 96 rises straight up from the bottom dead center during dense planting, the planting claw 96 does not easily escape during sparse planting, causing a phenomenon in which the seedlings fall forward. It can be understood.

In the embodiment, the interplant transmission device 26 is provided with the upstream inconstant speed first to fourth gears 48, 56, 121, 122, and the seedling planting device 2 is provided with the downstream inconstant speed bevel gear pairs 98, 99. Due to the provision, the planting claw member 37 is accelerated and rotationally driven so that the operating speed increases near the planting claw 96 positioned at the bottom dead center. Therefore, the planting claw 96 quickly escapes from the bottom dead center, and as a result, it is possible to prevent the planting claw 96 from tipping the seedling forward.

In addition, in the embodiment, since the non-uniform speed member is arranged separately between the inter-plant transmission device 26 and the seedling planting device 2, the distance from the inter-plant transmission device 26 to the downstream inconsistent speed bevel gear pair 98, 99 is The ratio of non-uniform rotation is small. As a result, torsion generated in the transmission elements (PTO shaft 29, planting drive shaft 32, planting transmission shaft 87, etc.) constituting the power transmission system is remarkably suppressed, and smooth movement of the transplantation mechanism 8 can be ensured. In addition, since the backlash that occurs in the power transmission system can be suppressed, it is possible to prevent problems such as the planting posture of the seedlings being disturbed due to the timing of the uneven speed being shifted.

Since the transplanting mechanism 8 is configured such that the planting claw members 37 are swingably attached to both ends of the elongated rotary case 36, the planting claw members 37 themselves act as weights and generate a large inertial force. Moreover, a large load is generated when the seedling is scraped, and a negative load is generated thereafter. That is, due to the rocking motion of the planting claw member 37 , a large torque fluctuation occurs in a cycle of overload→no load→negative load with respect to the rotation of the transplanting mechanism 8 . Such torque fluctuations are conspicuous when the resonance rotation speed is exceeded even when the plants are rotating at a constant speed during dense planting (because the transplanting mechanism 8 rotates at a higher speed during dense planting than during sparse planting).

More specifically, even if the transplanting mechanism 8 rotates at a constant speed, when one planting claw member 37 escapes from the field, the other planting claw member 37 shifts to scraping the seedlings. It can be said that the planting claw members 37 act to cancel each other's load fluctuations. However, since a large torque is required to scrape the seedlings, the movement of the two planting claw members 37 alone is weak in the function of leveling torque fluctuations. For this reason, the transplantation mechanism 8 does not rotate smoothly, and a phenomenon called "jerking" tends to occur.

On the other hand, if the transplanting mechanism 8 is given a slight non-uniform rotation by the downstream non-uniform bevel gear pair 98, 99 even in a densely planted state as in the embodiment, the planting claw member 37 scrapes the seedlings due to the inertia force. , and the transplanting mechanism 8 decelerates after the seedling is scraped, so that a large inertial force acting on the transplanting mechanism 8 can be suppressed. Therefore, the load fluctuation (or torque fluctuation) acting on the transplantation mechanism 8 can be leveled to ensure smooth rotation.

(7). First Embodiment of Anti-Phase Torque Generating Member Next, a first embodiment of the anti-phase torque generating member 130 will be described with reference to FIGS. 8 and 14 to 18. FIG. In the rice transplanter of the embodiment, the rotation torque T of the transplanting mechanism 8 based on the inconstant rotational power of the upstream inconstant speed and the downstream inconstant speed bevel gear pair 98, 99 is inversely phased with the rotational torque T. An anti-phase torque generating member 130 is provided for applying a phase torque Tan. In the first embodiment, each of the plurality (four) of planted transmission cases 31 is provided with the opposite phase torque generating member 130 . Since each planted transmission case 31 is provided with a row stopping clutch 102 , a reverse phase torque generating member 130 exists for each combination of a total of four planted transmission cases 31 and row stopping clutches 102 .

As shown in FIGS. 14 to 17, an end case 131 having a hollow structure is integrally provided on the rear end side of the planted transmission case 31. As shown in FIGS. The end case 131 may be a separate structure that is detachably attached to the rear end side of the planted transmission case 31 . The inside of the planted transmission case 31 and the inside of the end case 131 communicate with each other. A planted branch shaft 132 extending in the front-rear direction is rotatably supported via a bearing at a communicating portion between the planted transmission case 31 and the end case 131 . A leveling bevel gear 133 that constantly meshes with the downstream non-uniform-speed driven bevel gear 99 is provided on the front end side of the planting branch shaft 132 . The leveling bevel gear 133 and the downstream inconstant velocity driving bevel gear 98 have a positional relationship in which they face each other (oppose) in front and behind with the planting central axis 91 interposed therebetween.

The leveling bevel gear 133 is formed in the same shape as the downstream inconstant velocity driving bevel gear 98 . That is, the leveling bevel gear 133 has the same number of teeth as the downstream non-uniform main drive bevel gear 98, and similarly to the downstream non-uniform main drive bevel gear 98, the pitch cone angle is changed in the rotational direction while the cone distance is kept constant. It is formed into a shape that changes continuously along the length of the line. Therefore, the leveling bevel gear 133 and the planting branch shaft 132 rotate in the opposite direction at the same speed as the downstream non-uniform speed driving bevel gear 98 (twice as fast as the downstream non-uniform driven bevel gear 99). .

The rear end side of the planting branch shaft 132 protrudes to the upper-lower middle part in the end case 131 . An eccentric shaft 134 extending parallel to the planting branch shaft 132 is fixed to the protruding portion on the rear end side. The axis of the eccentric shaft 134 is eccentric with respect to the center of rotation of the planting branch shaft 132 . For this reason, the planting branch shaft 132 and the eccentric shaft 134 are in the shape of a crankshaft (exhibiting the function of a crankshaft). A locking pin 135 is attached to the lower side in the end case 131 . A tension spring 136 is mounted on the eccentric shaft 134 and the locking pin 135 as means for generating antiphase torque. The tension spring 136 always urges the eccentric shaft 134 in a direction to move it to the lower side of the planting branch shaft 132 . When the eccentric shaft 134 passes right above the planting branch shaft 132, the tension spring 136 is set to cross the fulcrum. In the first embodiment, the planted branch shaft 132, the eccentric shaft 134 and the tension spring 136 constitute the antiphase torque generating member 130. FIG.

A driving spur gear 137 is fixed to the protruding portion on the rear end side of the planting branch shaft 132 . A power take-off shaft 138 extending in parallel with the planted branch shaft 132 is rotatably supported on the upper side in the end case 131 . A driven spur gear 139 is fixed to the front side of the power take-off shaft 138 . The driving spur gear 137 and the driven spur gear 139 are always in mesh. The rear end side of the power take-off shaft 138 protrudes rearward from the rear surface of the end case 131 . The rotational power of the planted transmission shaft 87 is transmitted to the power take-off shaft 138 via the downstream non-uniform bevel gear pair 98, 99, the leveling bevel gear 133, the planted branch shaft 132, the drive spur gear 137 and the driven spur gear 139. be done. When an optional device such as a chemical sprayer is attached to the seedling planting device 2, the rotational power of the power take-off shaft 138 is transmitted to the optional device.

Here, FIG. 18 shows, as an example, the relationship between the rotational torque T (fluctuation torque) of the planting center shaft 91 in the transplantation mechanism 8, the antiphase torque Tan, and the combined torque Tco obtained by synthesizing these torques. 18 represents the rotational torque T (fluctuating torque) of the central planting shaft 91. Near the bottom dead center where each planting claw 96 of the planting claw member 37 plants seedlings, the rotational torque T is become the largest. 18 represents the anti-phase torque Tan generated by the anti-phase torque generating member 130 (planting branch shaft 132, eccentric shaft 134 and tension spring 136). In the vicinity of the bottom dead center where 96 plant the seedlings, the anti-phase torque Tan becomes the smallest.

The elastic restoring force of the tension spring 136 is transmitted from the leveling bevel gear 133 provided on the planting branch shaft 132 to the planting center shaft 91 via the downstream non-uniform driven bevel gear 99 . As a result, as indicated by the solid line in FIG. 18 , the rotational torque T and the antiphase torque Tan are combined, and the combined torque Tco is transmitted to the implantation mechanism 8 . That is, the rotation torque T leveled (canceled) by combining the anti-phase torques Tan is transmitted to the implantation mechanism 8 . Therefore, load fluctuations (which may be called torque fluctuations) acting on the transplantation mechanism 8 are leveled, and smooth rotation of the transplantation mechanism 8 can be ensured. Therefore, the occurrence of a phenomenon called "jerking" can be suppressed, and seedlings can be planted in an appropriate planting posture.

As is clear from the above description and FIGS. 8 and 14 to 18, the transmission case 11 for shifting the power of the engine 10 mounted on the traveling body 1 and the planting claw 96 that draws a non-circular motion locus are provided. a seedling planting device 2 having a transplanting mechanism 8, a plant interval transmission device 26 for changing the plant interval by changing the operation speed of the plant planting mechanism 8 with respect to the running speed of the traveling body 1, and the plant planting mechanism 8 at a non-uniform speed In a rice transplanter provided with non-uniform speed members 98 and 99 for transmitting rotational power, the rotational torque T of the transplanting mechanism 8 based on the non-uniform rotational power is in opposite phase to the rotational torque T. Since the anti-phase torque generating member 130 for applying the anti-phase torque Tan is further provided, the anti-phase torque Tan from the anti-phase torque generating member 130 is the rotational torque of the transplantation mechanism 8 due to the non-uniform rotational power. T is offset, and load fluctuations (which may be called torque fluctuations) acting on the transplantation mechanism 8 are leveled, and smooth rotation of the transplantation mechanism 8 is ensured. Therefore, the occurrence of a phenomenon called "jerking" can be suppressed, and seedlings can be planted in an appropriate planting posture.

In particular, the power transmission system from the transmission between the stocks 26 to the transplantation mechanism 8 has rotating shafts 87 and 91 that intersect with each other, and these intersecting rotating shafts 87 and 91 are configured to transmit power via a pair of bevel gears. , the pair of bevel gears is configured as a pair of unequal speed gears 98 and 99 as the unequal speed members, and the opposite phase torque generating member 130 is provided to the unequal speed gear 99 on the downstream side of the pair of unequal speed gears 98 and 99. are connected, the existing members of the non-uniform gear pair 98, 99 can be utilized, which is advantageous in terms of cost.

(8). Second and Third Embodiments of Anti-Phase Torque Generating Member Next, a second embodiment of the anti-phase torque generating member 130 will be described with reference to FIG. In the second embodiment, the end case 131 is removed from the rear end side of the planted transmission case 31, and the opposite phase torque generating member 130 is arranged on the rear side in the planted transmission case 31, which is the first embodiment. It is different from the example.

In this case, external teeth 141 are formed on the outer peripheral side of the operating ring 105 of the row-stopping clutch 102 . The external teeth 142 of the operating ring 105 mesh with a leveling spur gear 143 rotatably supported on the rear side of the planted transmission case 31 . A rotation center axis 144 of the leveling spur gear 143 extends parallel to the planting center axis 91 . A locking pin 145 is erected on one side surface of the leveling spur gear 143 .

A tension spring 146 is mounted on the locking pin 145 and the inner peripheral wall of the planted transmission case 31 as means for generating reverse phase torque. A tension spring 146 always biases the locking pin 145 away from the operation ring 105 . The tension spring 146 expands and contracts due to the rotation of the leveling spur gear 143 . The leveling spur gear 143 and the tension spring 146 form a kind of crank structure. In the second embodiment, the operation ring 105 of the row stop clutch 102, the leveling spur gear 143, the locking pin 145 and the tension spring 146 constitute the antiphase torque generating member . In other words, the opposite phase torque generating member 130 is positioned downstream of the row stop clutch 102 in the planted transmission case 31 . Also in the second embodiment, as in the case of the first embodiment, the anti-phase torque generating member 130 exists for each combination of the planted transmission case 31 and the row-stopping clutch 102 in total four sets.

In the above configuration, the elastic restoring force of the tension spring 146 is transmitted from the leveling spur gear 143 to the planting center shaft 91 via the operation ring 105 of the row stop clutch 102 . As a result, as in the case of the first embodiment (as indicated by the solid line in FIG. 18), the rotation torque T and the antiphase torque Tan are synthesized, and the synthesized torque Tco is transmitted to the implantation mechanism 8, 8 can ensure smooth rotation. Therefore, as in the case of the first embodiment, the occurrence of a phenomenon called "jerking" can be suppressed, and the seedlings can be planted in an appropriate planting attitude.

In addition, since the anti-phase torque generating member 130 is arranged downstream of the row stop clutch 102 in the planting transmission case 31, the anti-phase torque generating member 130 is located near the transplanting mechanism 8 which is the source of the load fluctuation. will be positioned. Therefore, the effect of offsetting the rotation torque T of the transplantation mechanism 8 with the anti-phase torque Tan, that is, the effect of leveling the load fluctuation is high. In addition, when the row-stopping clutch 102 is in the power cutoff state, the anti-phase torque Tan is not generated, so there is no danger of transmitting unnecessary torque around the transplanting mechanism 8 .

FIG. 20 shows a third embodiment of the antiphase torque generating member 130. As shown in FIG. The third embodiment shown in FIG. 20 is a modification of the second embodiment described above. The third embodiment is similar to the second embodiment in that the anti-phase torque generating member 130 is arranged on the rear side in the planted transmission case 31 and downstream of the row stop clutch 102. , and in that a reverse phase torque generating member 130 is provided independently of the row stop clutch 102, which is different from that of the second embodiment.

In this case, a first leveling spur gear 152 is fixed on the planting center shaft 91 on the opposite side of the row stop clutch 102 across the downstream non-uniform driven bevel gear 99 . The first leveling spur gear 152 is meshed with a second leveling spur gear 153 rotatably supported on the rear side of the planted transmission case 31 . A rotation center axis 154 of the second leveling spur gear 153 extends parallel to the planting center axis 91 . A locking pin 155 is erected on one side surface of the second flat gear 153 for leveling.

A tension spring 156 is mounted on the locking pin 155 and the inner peripheral wall of the planted transmission case 31 as means for generating reverse phase torque. The tension spring 156 always urges the locking pin 155 away from the first leveling spur gear 152 . The rotation of the second flat gear 153 for leveling expands and contracts the tension spring 156 . The second flat gear 153 for leveling and the tension spring 156 have a kind of crank structure. In the third embodiment, the first and second leveling spur gears 152, 153, locking pin 155 and tension spring 156 constitute the antiphase torque generating member 130. FIG. Also in the third embodiment, the reverse phase torque generating member 130 exists for each combination of the planted transmission case 31 and the row-stopping clutch 102, which are four sets in total. Even when configured as described above, the same effects as those of the second embodiment can be obtained.

As is clear from the above embodiment and FIGS. 19 and 20, the transmission case 11 for shifting the power of the engine 10 mounted on the traveling body 1 and the planting claw 96 that draws a non-circular motion trajectory. A seedling planting device 2 having a mechanism 8, a plant interval speed change device 26 for changing the plant interval by changing the operation speed of the plant planting mechanism 8 with respect to the running speed of the traveling machine body 1, and the plant planting mechanism 8 with a non-uniform rotational power. In a rice transplanter equipped with non-uniform velocity members 98 and 99 that transmit the non-uniform rotational power, the rotational torque T is opposite in phase to the rotational torque T of the transplanting mechanism 8 based on the non-uniform rotational power. Since the anti-phase torque generating member 130 for applying the phase torque Tan is further provided, the anti-phase torque Tan from the anti-phase torque generating member 130 reduces the rotation torque T of the transplantation mechanism 8 due to the non-uniform rotational power. This balances out the load fluctuations (which may also be called torque fluctuations) acting on the implantation mechanism 8, thereby ensuring smooth rotation of the implantation mechanism 8. FIG. Therefore, the occurrence of a phenomenon called "jerking" can be suppressed, and seedlings can be planted in an appropriate planting posture.

Further, when the row-stopping clutch 102 is put in the power cutoff state, the anti-phase torque Tan is not generated, and there is no danger of transmitting unnecessary torque around the transplanting mechanism 8 . Moreover, a row stopping clutch 102 for connecting and disconnecting power transmission from the inter-plant transmission 26 to the transplanting mechanism 8 is provided in the planting transmission case 31 of the seedling planting device 2, which is longitudinally elongated. 31, the anti-phase torque generating member 130 is arranged downstream of the row stop clutch 102, so that the anti-phase torque generating member 130 is positioned near the transplanting mechanism 8, which is the source of load fluctuation. Therefore, the effect of canceling the rotation torque T of the transplantation mechanism 8 with the anti-phase torque Tan, that is, the effect of leveling the load fluctuation is high.

(9). Fourth to Ninth Embodiments of Anti-Phase Torque Generating Member Next, a fourth embodiment of the anti-phase torque generating member 130 will be described with reference to FIGS. 21 and 22. FIG. In the fourth embodiment, the opposite phase torque generating member 130 is applied to the structure in which the rotation of the planting drive shaft 32 is transmitted to the planting center shaft 91 by the chain 163 . In this case, the planting drive shaft 32 in the planting transmission case 31 rotatably supports the driving sprocket 161 , while the planting center shaft 91 rotatably supports the driven sprocket 162 . A power transmission chain 163 is wound around a driving sprocket 161 and a driven sprocket 162 in the planted transmission case 31 . A torque limiter 164 is slidably mounted on the planting drive shaft 32 so as not to be relatively rotatable. When a predetermined load or more is applied to the planted drive shaft 32, the engagement of the torque limiter 164 is disengaged and power transmission from the planted drive shaft 32 to the driving sprocket 161 is interrupted. The planting center shaft 91 is slidably fitted with a row-stopping clutch 102 that connects and disconnects power transmission from the driven sprocket 162 to the planting center shaft 91 so as not to be relatively rotatable. As shown in FIG. 22, the driving sprocket 161 and the driven sprocket 162 are configured as elliptical or other (non-circular) non-uniform velocity sprockets. An idle roller 163 ′ is brought into contact with the chain 163 . With such a configuration, non-uniform rotation is imparted to the central shaft 91 for planting. In the fourth embodiment, the reduction ratio in chain 163 transmission is an average of 1/2.

A power take-off shaft 165 extending in parallel with the planting center shaft 91 is rotatably supported in the planting transmission case 31 further to the rear end side than the planting center shaft 91 . One end side (the right end side in the embodiment) of the power take-off shaft 165 is projected outward from the transmission case 31 with planting. A driving sprocket 166 for leveling is fixed on the opposite side of the row stop clutch 102 across the driven sprocket 162 on the center shaft 91 for planting, while a driven sprocket 167 for leveling is fixed on the power take-off shaft 165 . ing. A chain 168 for power transmission is wound around the driving sprocket 166 for leveling and the driven sprocket 167 for leveling. The rotational power of the planting central shaft 91 is branched and transmitted to the power take-off shaft 165 via the sprocket and chain transmission systems 166-168. When an optional device such as a chemical sprayer is attached to the seedling planting device 2, the rotational power of the power take-off shaft 165 is transmitted to the optional device.

The other end side of the power take-off shaft 165 is bent in a crank shape. A tension spring 169 is mounted on the crank tip side of the power take-off shaft 165 and the inner peripheral wall of the planted transmission case 31 as a means for generating reverse phase torque. The tension spring 169 always urges the power take-off shaft 165 to move the crank tip side of the power take-off shaft 165 to the lower side of the rotation center of the power take-off shaft 165 . Rotation of the power takeoff shaft 165 via the leveling driven sprocket 167 causes the extension spring 169 to expand and contract. In the fourth embodiment, the power takeoff shaft 165, leveling driving and driven sprockets 166, 167, chain 168 and tension spring 169 constitute the antiphase torque generating member 130. FIG. That is, the power take-off shaft 165 is one of the constituent elements of the anti-phase torque generating member 130 . Also in the fourth embodiment, the anti-phase torque generating member 130 exists for each combination of the planted transmission case 31 and the row-stopping clutch 102, which are four sets in total. Even when constructed as described above, the same effects as those of the second and third embodiments can be obtained.

In all of the fifth and subsequent embodiments shown in FIG. 23, as in the fourth embodiment, the rotation of the planting drive shaft 32 is transmitted to the planting center shaft 91 by a chain 163, and the reverse phase torque generating member 130 is applied. In the fifth embodiment, both the driving sprocket 161 provided on the planting drive shaft 32 and the driven sprocket 162 provided on the idle shaft 170 are circular but eccentric non-uniform sprockets. A main drive gear 171 is fixed to the idle shaft 170 , and a driven gear 172 is fixed to the central planting shaft 91 . By meshing the main drive gear 171 and the driven gear 172, non-uniform rotation is imparted to the planting center shaft 91. As shown in FIG. The reduction ratio in chain 163 transmission is 1 on average, but the reduction ratio in gear transmission from main drive gear 171 to driven gear 172 is 1/2. An idle roller 163 ′ is brought into contact with the chain 163 . Only one of the sprockets 161 and 162 may be eccentric and the other may not be eccentric.

A sixth embodiment shown in FIG. 24 and a seventh embodiment shown in FIG. 25 are modifications of the fourth embodiment shown in FIGS. In the sixth embodiment shown in FIG. 24, the drive sprocket 161 provided on the planting drive shaft 32 is configured as a circular constant velocity sprocket. In the seventh embodiment shown in FIG. 25, the drive sprocket 161 provided on the planting drive shaft 32 is configured as a circular but eccentric non-uniform sprocket. In the sixth and seventh embodiments, the reduction ratio in chain 163 transmission is 1/2 on average.

In the eighth embodiment shown in FIG. 26, the driving sprocket 161 provided on the planting drive shaft 32 is a circular but eccentric non-uniform sprocket, and the driven sprocket 162 provided on the planting central shaft 91 is a circular constant velocity sprocket. Sprocket. In this case, the reduction ratio in chain 163 transmission is also an average of 1/2.

In the ninth embodiment shown in FIG. 27, the driving sprocket 161 provided on the planting drive shaft 32 is configured as an elliptical (non-circular) non-uniform sprocket, and the driven sprocket 162 provided on the planting center shaft 91 is used. , polygonal (non-circular) non-uniform sprockets. In this case, the reduction ratio in chain 163 transmission is also an average of 1/2. Since the driven sprocket 162 is formed in a substantially square shape, acceleration and deceleration occur four times in one rotation of the planting center shaft 91 .

As is clear from the above embodiment and FIGS. 21 to 27, the transmission case 11 for shifting the power of the engine 10 mounted on the traveling body 1, and the planting claw 96 that draws a non-circular motion trajectory. A seedling planting device 2 having a mechanism 8, a plant interval speed change device 26 for changing the plant interval by changing the operation speed of the plant planting mechanism 8 with respect to the running speed of the traveling machine body 1, and the plant planting mechanism 8 with a non-uniform rotational power. In a rice transplanter provided with non-uniform velocity members 161 and 162 that transmit the non-uniform rotational power, the rotational torque T is in the opposite phase with respect to the rotational torque T of the transplanting mechanism 8 based on the non-uniform rotational power. A reverse phase torque generating member 130 for applying a phase torque Tan is further provided, and power can be transmitted to an optional device attached to the seedling planting device 2 to the planting transmission case 31 longitudinally in the seedling planting device 2. Since the power take-off shaft 165 is provided and the power take-off shaft 165 is used as a constituent element of the anti-phase torque generating member 130, the load fluctuation (torque fluctuation) acting on the transplanting mechanism 8 is leveled, and the transplanting mechanism 8 is stabilized. While ensuring smooth rotation of the power take-off shaft 165, the power take-off shaft 165 can also be used as the reverse phase torque generating member 130, simplifying the power transmission structure to the seedling planting device 2 and reducing the weight. can contribute to

(10). Others The present invention can be embodied in various ways other than the above embodiments. For example, the inter-stock transmission 26 can be built in the mission case 11, and in this case, one upstream non-uniform-speed member is built in the mission case 11. When a non-uniform speed member is provided for each of the traveling body 1 and the seedling planting device 2, the acceleration/deceleration ratio (non-uniform speed ratio) may be set as necessary. Therefore, depending on the case, it is possible to make the acceleration/deceleration ratio (non-uniform speed ratio) on the traveling body 1 side smaller than the non-uniform speed conversion ratio on the seedling planting device 2 . A belt transmission (preferably a timing belt) may be employed in place of the chain transmission. In any of the first to ninth embodiments, it is possible to dispose the crank structure and the tension spring of the anti-phase torque generating member 130 outside the planted transmission case 31 .

1 Traveling body 2 Seedling planting device 8 Transplanting mechanism 10 Engine 11 Mission case 26 Inter-plant transmission 36 Rotary case 37 Planting claw member 40 Inter-plant case 87 Planting transmission shaft 91 Planting center shaft 96 Planting claw 98 Downstream inconstant speed Main drive bevel gear 99 Downstream non-uniform speed driven bevel gear 102 Row stop clutch 105 Operation ring 130 Reverse phase torque generating member 131 End case 132 Planting branch shaft 133 Leveling bevel gear 134 Eccentric shaft 136 Tension spring 142 External tooth 143 Leveling flat Gears 145, 155 Locking pins 146, 156, 169 Tension spring 152 First leveling flat gear 153 Second leveling flat gear 161 Main drive sprocket 162 Driven sprockets 163, 168 Chain 164 Torque limiter 165 Power take-off shaft 166 Leveling driving sprocket 167 for leveling driven sprocket 169 tension spring

Claims (5)

a seedling planting device supported by a running portion;
a transmission between plants that transmits power to the seedling planting device and can change the working speed of the seedling planting device with respect to the traveling speed of the traveling unit;
The transmission between plants can switch the power transmitted to the seedling planting device in a plurality of stages,
The transmission between plants includes a first switching mechanism and a second switching mechanism for switching input power in a plurality of gear stages on a power transmission path to the seedling planting device,
The power transmitted to the seedling planting device can be switched by a combination of gear stages selected by the first switching mechanism and the second switching mechanism,
The sparse planting power with which the operation speed of the seedling planting device with respect to the running speed is the slowest among the plurality of powers selects the sparse planting gear stage in the first switching mechanism, and A rice transplanter configured to transmit to the seedling planting device by selecting a corresponding specific gear stage. The rice transplanter according to claim 1, wherein the sparse planting gear stage of the first switching mechanism is a variable speed member that transmits power at a variable speed. The inter-plant transmission has at least two transmission stages for sparse planting in the first switching mechanism,
The rice transplanter according to claim 1 or 2, wherein said second switching mechanism has different specific gear stages respectively corresponding to said sparse planting gear stages of said first switching mechanism. The first switching mechanism has a shaft and a plurality of transmission gears arranged in the axial direction,
the non-uniform speed member of the sparsely planted gear stage is a non-uniform gear;
The rice transplanter according to claim 2, wherein the non-uniform speed gear is arranged at an axial end of the plurality of transmission gears. The shaft includes an output shaft that transmits power to the seedling planting device, an input shaft arranged concentrically with the output shaft, and an intermediate shaft fitted to the input shaft while rotating together with the output shaft. , including
5. The method according to claim 4, wherein, among the plurality of transmission gears, the non-uniform gear is fitted on the intermediate shaft so as to be relatively rotatable, and the remaining transmission gears are fitted to the intermediate shaft so as not to be relatively rotatable. rice transplanter.

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