JP6930699B2 - Rice transplanter - Google Patents

Description

The present invention relates to a rice transplanter in which a seedling stand and a seedling planting device having a plurality of planting claws are attached to a traveling machine to continuously perform seedling planting work.

In a conventional rice transplanter, a seedling planting device having a seedling stand and a transplanting mechanism with a planting claw is attached to the rear part of the traveling machine. As a transplanting mechanism of the seedling planting device, 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 reversed with respect to the rotary case. Make one turn in the direction. That is, the planting claw revolves around the axis of the rotary case while rotating.

In the seedling planting work using this type of rice transplanter, the seedling pedestal on which the seedling mat is placed is intermittently fed laterally to the left and right at predetermined intervals, and the planting claws facing the front of the sapling pedestal are moved. By rotating around the axis of the rotary case while revolving, the planting claws are reciprocated between the seedling stand and the field scene, and the seedlings are scraped from the seedling mat one by one and planted in the field. The operation cycle (planting cycle) of the planting claws in the seedling planting device is linked to the traveling speed of the traveling machine, and the seedling planting interval (between stocks) is kept constant even if the traveling speed changes.

The number of seedlings to be planted per unit area (generally 3.3 square meters) is not always constant, and the number of plants to be planted per unit area, for example, varies depending on the area and the user. In this respect, the conventional rice transplanter is provided with an inter-stock transmission that adjusts the interlocking relationship between the traveling speed and the planting cycle. In this case, by changing the operating speed (planting speed) of the transplanting mechanism with respect to the traveling speed in the inter-strain transmission, the inter-strains are changed and the number of planted stocks per unit area changes.

In recent years, sparse planting has been carried out in which the distance between plants is longer than that of standard planting in consideration of the growth conditions of seedlings planted in the field, but it is necessary to slow down the planting speed as the distance between plants is increased. However, if the planting speed is simply slowed down by the inter-strain transmission, there is a problem that the tip of the planting claw is dragged in the field and the seedlings fall forward or float seedlings are generated.

In this regard, Patent Documents 1 and 2 describe a rice transplanter provided with an unequal velocity member that transmits unequal velocity rotational power to a transplantation mechanism in order to prevent the planting claws from being dragged in the field during sparse planting. The structure is disclosed. The non-constant velocity member is configured to change the angular velocity during one rotation of the rotary case constituting the transplanting mechanism (non-constant velocity rotation), and accelerates the speed at which the planting claws escape from the field even during sparse planting. There is. In the rice transplanter of Patent Document 1, a non-uniform speed member is incorporated in the inter-stock transmission in the mission case. In the rice transplanter of Patent Document 2, a non-uniform velocity member is provided on the downstream side of the power transmission with respect to the lateral feed drive mechanism of the seedling stand.

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

By the way, there are power switching structures of inter-stock transmissions, such as those that shift (switch) in stages and those that shift continuously, but all of them tend to have a large number of parts and a complicated structure. was there.

The present invention has been made in view of the above-mentioned current situation, and is intended to prevent the inconvenience while enjoying the advantages of the non-constant velocity member.

The rice planting machine according to the invention of claim 1 transmits power to a seedling planting device supported by a traveling unit and a seedling planting device, and changes the working speed of the seedling planting device with respect to the traveling speed of the traveling unit. The inter-strain transmission is provided with a possible inter-strain transmission, and the inter-strain transmission can switch the power transmitted to the seedling planting device in a plurality of stages, and the inter-strain transmission is input on the power transmission path to the seedling planting device. It is equipped with a first switching mechanism and a second switching mechanism that switch the generated power in a plurality of shift stages, and transmits the power to the seedling planting device by the combination of the respective shift stages selected by the first switching mechanism and the second switching mechanism. The power can be switched, and among the plurality of powers, the operating speed of the seedling planting device with respect to the traveling speed includes a dense planting power having a predetermined speed and a sparse planting power having a speed slower than the dense planting power, and the sparse planting power. Is configured to transmit to the seedling planting device by selecting a sparsely planted shift stage in the first switching mechanism and selecting a corresponding specific shift stage in the second switching mechanism, and a plurality of power sources. Of these, the power other than the sparse planting power is transmitted to the seedling planting device regardless of the combination of the shift stage different from the sparse planting shift stage in the first switching mechanism and the shift stage selectable in the second switching mechanism. It is configured to be possible.

In the rice transplanter of the present invention, the power other than the sparsely planted power among the plurality of powers can be selected by the second switching mechanism and the plurality of gears that can be selected by the first switching mechanism other than the sparsely planted gears. Any combination of gears may be configured to be transmittable to the seedling planting apparatus.
Further, in the rice transplanter of the present invention, the sparse planting power having the slowest operating speed of the seedling planting device with respect to the traveling speed among the plurality of powers selects the sparse planting shift stage in the first switching mechanism and is the first. 2 The switching mechanism may be configured to transmit to the seedling planting device by selecting the corresponding specific shift stage.

In the rice transplanter of the present invention, the sparsely planted speed change stage of the first switching mechanism may be a non-constant speed member that transmits power at a non-constant speed.
Further, in the rice transplanter of the present invention, the inter-stock transmission has at least two sparsely planted gears in the first switching mechanism, and the second switching mechanism corresponds to each of the sparsely planted gears of the first switching mechanism. It may have different specific gears.

An unequal velocity gear is also arranged inside the rotary case constituting the transplantation mechanism, which operates the planting claw so as to draw a long non-circular operation locus in the vertical direction, which is referred to in the present invention. It is different from a non-constant velocity member (that is, a member that imparts non-constant velocity rotation (acceleration / deceleration) to a transmission element of a power transmission system).

According to planting machine according to the present invention, in a changeable strains transmission the working speed of the seedling planting apparatus relative to the running speed of the run line portion, can be simplified complex tend power switching structure.

It is a top view of the rice transplanter which concerns on embodiment. It is a side view of a rice transplanter. It is a perspective view which shows the skeleton of a rice transplanter. (A) is a perspective view showing the entire power transmission path, and (B) is a perspective view of the transplantation 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 view showing the locus of the planted claw. (A) is a plan view showing a power transmission path, (B) is an external perspective view of an inter-stock changing device, and (C) and (D) are external perspective views of a center case provided in a planting portion. (A) is an external perspective view of the gear group in the inter-stock changing device and the center case, and (B) is a perspective view of the gear group in the center case. It is a transmission system diagram. (A) is a plan view showing a power transmission path to the planting device, (B) is a separation plan view of a terminal planting portion of the power transmission path, and (C) is a schematic view of a bevel gear. (A) and (B) are plan views showing the meshing state of the bevel gears, (C) and (D) are perspective views of the bevel gears, and (E) is a comparison view in which pairs of bevel gears are arranged side by side. It is a chart which shows the relationship between the combination of gears in an inter-stock transmission and the number of planted stocks. It is a figure which shows the operation locus of a planting claw when it is set to 43 strains of non-constant velocity. It is a figure which shows the angular velocity change of a planting nail when it is set to 43 strains of non-constant velocity. It is a top view which shows the arrangement structure of the transplantation mechanism in 1st Example. It is a plan sectional view which shows the power transmission structure in a planting transmission case. It is an enlarged plan sectional view of the rear part of a planting transmission case. It is an enlarged side sectional view of the rear part of a planting transmission case. It is a figure which shows the relationship between the rotational torque of a transplanting mechanism, and the antiphase torque. It is a power transmission system diagram from the planting transmission case to the transplantation mechanism in the second embodiment. It is a power transmission system diagram from the planting transmission case to the transplantation mechanism in the third embodiment. It is a power transmission system diagram from the planting transmission case to the transplantation mechanism in the fourth embodiment. It is explanatory drawing which shows typically the non-constant velocity member in 4th Example. It is explanatory drawing which shows typically the non-constant velocity member in 5th Example. It is explanatory drawing which shows typically the non-constant velocity member in 6th Example. It is explanatory drawing which shows typically the non-constant velocity member in 7th Example. It is explanatory drawing which shows typically the non-constant velocity member in 8th Example. It is explanatory drawing which shows typically the non-constant velocity member in 9th Example.

Next, an embodiment of the present invention will be described with reference to the drawings. The embodiment is applied to a passenger-type rice transplanter (hereinafter, simply referred to as "rice transplanter"). In the following explanation, the front-back and left-right words are used to specify the direction, but the front-back and left-right words define the forward direction of the rice transplanter as the front. The front view direction is the direction opposite to the forward direction.

(1). Outline of rice transplanter First, an outline of the rice transplanter will be described based on FIGS. 1 to 5. As shown in FIGS. 1 to 3, the rice transplanter has a traveling machine 1 and a seedling planting device 2 arranged behind the traveling machine 1. The traveling machine body 1 has front and rear wheels 3 and 4, a control seat 5, and a control handle 6, while the seedling planting device 2 has a seedling mounting table 7 on which a seedling mat is placed and a transplanting mechanism 8. The rice transplanter of the embodiment is an eight-row planting type. Therefore, eight seedling mat placement areas are formed on the seedling stand 7, and eight transplanting mechanisms are formed at the rear of the seedling planting device 2. 8 are arranged in a horizontal row.

As shown in FIG. 3, the traveling machine body 1 has a skeleton 9 composed of a large number of frame materials, and the engine 10 is supported by the front portion of the skeleton 9. A mission case 11 is arranged behind the engine 10. As shown in FIG. 4A, a hydrostatic continuously variable transmission (HST) 12 is mounted on the left side surface of the mission case 11, and the power of the engine 10 is a hydrostatic continuously variable transmission (HST) by a belt 13. It is transmitted to the machine (HST) 12. The engine 10 is covered with a bonnet 14. Further, the portion of the traveling machine body 1 excluding the bonnet 14 is covered with the vehicle body cover 15.

Front axle devices 17 are attached to the left and right side surfaces of the mission case 11, and front wheels 3 are attached to the front axle devices 17. A rear axle case 18 is arranged behind the mission case 11, and a rear wheel 4 is attached to a rear axle projecting laterally from the rear axle case 18. The mission case 11 and the rear axle case 18 are connected by a front-rear longitudinal joint material 19. Two left and right rear columns 20 are attached to the rear axle case 18, and the upper ends of the rear columns 20 are fixed to the left and right horizontally long rear frames 9a (see FIG. 3) constituting the rear end of the frame 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 columns 20, and a 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 material 19. Therefore, by expanding and contracting the hydraulic cylinder 22, the seedling planting device 2 moves up and down.

As can be easily understood from FIG. 4, power is transmitted from the inside of the mission case 11 to the inside of the rear axle case 18 by the rear wheel drive shaft 23. The rotation of the rear wheel drive shaft 23 is transmitted to the rear wheels 4 via 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 ground leveling rotor 24, and power is transmitted to the ground leveling rotor 24 by a rotor drive shaft 25 projecting rearward from the rear axle case 18.

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

The seedling planting device 2 has a horizontally long main frame 28, a center case 30 is fixed to a substantially left and right middle portion of the main frame 28, and the power of the PTO shaft 29 is a gear built in the center case 30. It is transmitted to the group. Four planting transmission cases 31 extending rearward are fixed to the rear surface of the main frame 28, and a pair of left and right transplanting mechanisms 8 are rotatably attached to the rear side of the planting transmission case 31.

A horizontally long planting drive shaft 32 penetrates the front side (base end side) of the planting transmission case 31, and the transplantation mechanism 8 is driven by the rotation of the planting drive shaft 32 (details will be described later). do). Further, power is transmitted to the planted drive shaft 32 from the PTO shaft 29 via a gear group built in the center case 30. A horizontally long horizontal feed shaft 33 is also attached to the center case 30, and the seedling stand 7 is laterally moved by one pitch by the rotation of the horizontal feed shaft 33.

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 support shafts 35. When the seedling stand 7 moves completely to the left or right, the vertical feed support shaft 35 rotates and the seedling mat moves down 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, and the rotary case 36 rotates 1/2. Each time the seedlings are scraped and planted by the planting claw member 37. Further, the rotary case 36 is set to rotate 1/2 when the PTO shaft 29 makes one rotation. The rotation speed of the PTO shaft 29 is basically proportional to the traveling speed of the traveling machine body 1, but the seedlings are planted by changing the relationship between the traveling speed and the rotation speed of the PTO shaft 29 by the inter-stock transmission device 26. The interval (between shares) can be changed.

(2). Interstock transmission structure / power transmission structure (upstream non-constant velocity member)
Hereinafter, the details of the power transmission system from the inter-stock transmission 26 to the transplant mechanism 8 will be described. First, the structure of the inter-stock transmission 26 and the power transmission structure for the structure will be described mainly with reference to FIGS. 6 to 8. The inter-stock transmission 26 has a front-rear split type inter-stock case 40 shown in FIG. 6 (B), and gear groups as shown in FIGS. 6 (A) and 6 (C) are arranged therein. ..

An input shaft 41 and an output shaft 42 are arranged inside the inter-stock case 40, 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. Although both gears 43 and 44 have the same diameter, 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 tubular intermediate shaft 45 is fitted in the input shaft 41 so as to be relatively rotatable, and the intermediate shaft 45 is fitted in a state of rotating together with the output shaft 42 (a state in which relative rotation is not possible). The third gear 46 and the fourth gear 47 are fitted to the intermediate shaft 45 so as to be slidable and unable to rotate relative to each other by spline fitting or the like. Further, the upstream non-constant speed first gear 48 and the upstream non-uniform speed third gear 121 are fitted in the intermediate shaft 45 so as to be relatively rotatable.

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

Inside the inter-stock case 40, an idle shaft 51 extending in parallel with the input shaft 41 and the output shaft 42 is rotatably supported on the idle shaft 51, and the idle shaft 51 is connected to the first gear 43 or the second gear 44. The meshable fifth gear 52 is fitted so as to be slidable and unable to rotate relative to each other due to spline fitting or the like. The fifth gear 52 has about twice the number of teeth as the first gear 43 or the second gear 44, and the first position meshed with the first gear 43 and the second position meshed with the second gear 44 can be selected. ..

The idle shaft 51 meshes with the sixth gear 54 and the fourth gear 47 that mesh with and separate from the upstream non-uniform speed fourth gear 122 and the third gear 46 that are always meshed with the upstream non-uniform speed third gear 121. -The 7th gear 55 that separates and the upstream non-uniform speed 2nd gear 56 that is always in mesh with the upstream non-uniform speed 1st gear 48 are fixed. The ratio of the number of teeth of the 7th gear 55 to the 4th gear 47 is set to be smaller than the ratio of the 6th gear 54 to the 3rd gear 46. Therefore, the rotation speed of the intermediate shaft 45 (and the output shaft 42) is such that the fourth gear 47 and the seventh gear 55 are meshed with each other rather than the state in which the third gear 46 and the sixth gear 54 are meshed with each other. Is lower.

The upstream non-constant speed first gear 48 and the upstream non-uniform speed second gear 56 have a non-circular profile such as an ellipse, and the number of teeth is set to be the same. Therefore, in a state where the rotation of the idle shaft 51 is transmitted to the intermediate shaft 45 and the output shaft 42 via the two non-uniform speed gears 48 and 56, the rotation speeds of the idle shaft 51 and the output shaft 42 are the same, and the rotation speed is the same. , The output shaft 42 rotates in a state where the angular velocity is periodically changed during one rotation thereof. Both non-constant speed gears 48 and 56 are always maintained in the meshed state due to the peculiarity that the meshing phases are always fixed because they are non-circular. 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 the number of teeth is set to be the same. Therefore, in a state where the rotation of the idle shaft 51 is transmitted to the intermediate shaft 45 and the output shaft 42 via the two non-uniform speed gears 48 and 56, the rotation speeds of the idle shaft 51 and the output shaft 42 are the same, and the rotation speed is the same. , The output shaft 42 rotates in a state where the angular velocity is periodically changed during one rotation thereof. That is, the upstream non-uniform speed first gear 48 and the upstream non-uniform speed second gear 56 are non-circular gear pairs such as eccentric gears and have a large acceleration / reduction ratio (non-constant speed ratio). The upstream non-constant 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 / reduction ratio (non-constant speed ratio).

Here, in the rotary case 36, for example, at the time of sparse planting of 37 strains / square m, the maximum speed phase of each planted claw 96 in the planted claw member 37 (the phase at which the operating speed of the planted claw 96 becomes the maximum speed) is set. Acceleration / deceleration is provided so as to be near the bottom dead center, and in the embodiment, the upstream non-uniform speed first gear 48 and the upstream non-uniform speed second gear 56 provided in the inter-stock transmission 26 are used. A slightly larger acceleration / deceleration is applied to the rotational power from the inter-stock case 40 to output non-constant velocity rotational power. Therefore, since the acceleration / reduction ratio (non-constant velocity ratio) is larger than the combination of the upstream non-constant speed 3rd gear 121 and the upstream non-uniform speed 4th gear 122, the operation locus of the planting claw 96 is near the bottom dead center. Greatly increases the operating speed of. Further, the upstream non-uniform speed 3rd gear 121 and the upstream non-uniform speed 4th gear 122 impart a slightly smaller acceleration / deceleration to the rotational power from the inter-stock case 40 to output the non-constant speed rotational power. Therefore, since the acceleration / reduction ratio (non-constant speed ratio) is smaller than the combination of the upstream non-constant speed 1st gear 48 and the upstream non-uniform speed 4th gear 56, the operation locus of the planting claw 96 is near the bottom dead center. Increase the operating speed of. The upstream non-constant speed first to fourth gears 48, 56, 121, 122 correspond to the upstream non-uniform speed member on the interstock transmission 26 side that transmits the non-constant speed rotational power to the transplant mechanism 8.

The fourth gear 47 and the upstream non-uniform velocity first gear 48 are provided with a first intermediate clutch 57 that can be meshed with and separated from each other. When the fourth gear 47 slides further to the right after being engaged with the seventh gear 55 from the state shown in FIG. 8, 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 speed second gear 56 and the upstream non-uniform speed 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 upstream non-uniform velocity first 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 meshed with and separated from each other. When the third gear 46 slides further to the left from the state shown in FIG. 8 after once meshing with the sixth gear 54, the second intermediate clutch 123 meshes 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 speed fourth gear 122 and the upstream non-uniform speed 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 velocity third gear 121.

The sliding of the fifth gear 52 causes a two-step switching, and the sliding of the intermediate shaft 45 causes a four-step switching. Therefore, there are eight stages of combinations (speed switching) as a whole. For example, the number of plants per 3.3 square meters can be changed to 37 to 85, which covers almost all areas of sparse planting and dense planting. FIG. 11 shows the relationship between the combination of gears and the number of planted stocks in the embodiment. When the 1st gear 43 and the 5th gear 52 are meshed, if the 4th gear 47 and the 7th gear 55 are meshed, the number of planted stocks is set to the constant velocity d stock, and the 3rd gear 46 and the 6th gear are engaged. When the gear 54 is engaged, the number of planted plants is set to the constant velocity f plant. When the second intermediate clutch 123 is engaged, the number of planted shares is set to the non-constant velocity b share. When the 2nd gear 44 and the 5th gear 52 are meshed, if the 4th gear 47 and the 7th gear 55 are meshed, the number of planted stocks is set to the constant velocity c stock, and the 3rd gear 46 and the 6th gear are engaged. When the gear 54 is engaged, the number of planted plants is set to the constant velocity e-strain. When the first intermediate clutch 57 is engaged, the number of planted shares is set to the a-share having a non-constant velocity. In this case, the number of shares indicated by the alphabet is in a relationship of increasing in alphabetical order.

Here, the upstream non-constant velocity 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, so that the planting claw 96 in the transplanting mechanism 8 operates. The maximum speed phase at which the speed becomes the maximum speed can be changed in the front-back range with the bottom dead center in between. As an example, FIG. 12 shows the operation locus of the planting claw 96 when the planting claw 96 is set to 43 strains having a non-constant velocity. Reference numeral MS1 in FIG. 12 refers to the upstream non-uniform speed third gear 121 and the upstream non-uniform speed fourth gear 122 so that the operating speed of the planting claw 96 becomes the highest on the front side (upstream side) of the bottom dead center. This is the maximum speed phase when assembled, and the MS2 has an upstream non-uniform speed 3rd gear 121 and an upstream non-uniform speed 4th gear 122 so that the operating speed of the planting claw 96 becomes the maximum speed near the bottom dead center. It is the maximum speed phase when is assembled. Reference numeral MS3 is assembled with the upstream non-uniform speed 3rd gear 121 and the upstream non-uniform speed 4th gear 122 so that the operating speed of the planting claw 96 becomes the highest on the rear side (downstream side) from the bottom dead center. The fastest phase of the case.

Depending on the relationship with the assembly accuracy, for example, the upstream non-uniform speed 3rd gear 121 and the upstream non-uniform speed 4th gear 122 may be assembled so that the front side (upstream side) from the bottom dead center is set to the maximum speed phase MS1. Assemble the upstream non-constant speed 3rd gear 121 and the upstream non-uniform speed 4th gear 122 so that the maximum speed phase MS2 is set near the bottom dead center, and further, the maximum speed on the rear side (downstream side) from the bottom dead center. It is possible to assemble the upstream non-constant speed third gear 121 and the upstream non-uniform speed fourth gear 122 so as to have the phase MS3. That is, for example, when the twist of the power transmission system is large and there is a concern that the operation cycle of the planting claw 96 may deviate due to the relationship with the assembly accuracy, or when the twist of the power transmission system is small and the vibration of the power transmission system is minimized. Even if you want to suppress it, you can change the setting of the maximum speed phase before and after the bottom dead center. Then, the so-called "hiccups" of the planting claw 96 can be suppressed and the vibration of the power transmission system can be suppressed. Needless to say, the upstream non-uniform speed first gear 48 and the upstream non-uniform speed second gear 56 may be assembled to the intermediate shaft 45 or the idle shaft 51 by adjusting the mounting phase.

A fertilizer-applying rotary shaft 58 extending in parallel with the input shaft 41 and the output shaft 42 is rotatably arranged on the upper portion of the inter-stock case 40, and the fertilizer-applying rotary shaft 58 meshes with the first gear 43. The gear 59 is fitted so as to be relatively rotatable. Power is transmitted from the fertilizer application rotating shaft 58 to the fertilizer application drive shaft 62 via the bevel gear 61.

As shown in FIG. 7A, the interstock 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 front-rear and longitudinal posture, and are exposed in front of the inter-stock case 40. As can be understood from FIG. 6B, the first operating shaft 63 can be slid back and forth with the first lever 65, and the second operating shaft 64 can be slid back and forth with the second lever 66. 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 includes 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 section transmission) will be described with reference to FIGS. 6 to 8. The center case 30 is formed of a shell body divided into two left and right, and a front-rear and 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. Inside the center case 30, the lateral feed drive shaft 72 is arranged in a horizontally long posture, and the lateral feed shaft 33 is connected to the lateral feed drive shaft 72.

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

The ratio of the number of teeth is different between the pairs of the lateral feed amount adjusting gears 73 and 74, and when the combination of the lateral feed amount adjusting gears 73 and 74 is changed, the rotation ratio of the lateral feed drive shaft 72 with respect to the PTO shaft 29 changes. .. As a result, the lateral feed pitch of the seedling mounting table 7 changes, and the amount of scraped seedlings changes.

The center case 30 has an overhanging portion 30a extending downward from the rear, and the left and right horizontally long planting output shafts 78 are rotatably held by the overhanging portion 30a, and the planting output shaft 78 has an intermediate shaft 70. The first relay gear 79 fixed to, the second relay gear 80 rotatably fitted to the lateral feed drive shaft 72, and the third relay gear 82 rotatably held by the center case 30 via the idle shaft 81. And power is transmitted via 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 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. There is a relationship. Therefore, the rotation speeds of the PTO shaft 29 and the planting output shaft 78 have a 1: 1 relationship. Since the third relay gear 82 is a mere 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 next to the planting output shaft 78 are connected by a coupling (sleeve) 86. Further, 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 integrally. The planting drive shaft 32 is divided at each position of the transplanting mechanism 8, and the adjacent planting drive shafts 32 are connected by a pulling 86. It is also possible to form a single structure in which the planting output shaft 78, each planting drive shaft 32, and the relay shaft 85 are made of one rod material.

(4). Structure of transplant mechanism / power transmission structure Next, the structure of the transplant mechanism 8 and the power transmission structure for the transplant mechanism 8 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 planting transmission case 31 has a hollow structure, and as shown in FIG. 8, a front-rear and longitudinal planting transmission shaft 87 is rotatably held inside the planting transmission case 31.

Power is transmitted to the planting transmission shaft 87 from the planting drive shaft 32 by the second bevel gear pairs 88a and 88b. Of the second bevel gear pairs 88a and 88b, the bevel gear 88b that rotates concentrically with the planting transmission shaft 87 is attached to a torque limiter 89 fitted to the planting transmission shaft 87. The torque limiter 89 has a spring 90, and when a load of a predetermined value or more is applied to the planting transmission shaft 87, the engagement is disengaged and power transmission is cut off.

On the rear side (tip side) of the planting transmission case 31, a horizontally long planting center shaft 91 is rotatably held via a pair of left and right bearings 104. The planting center shaft 91 projects to the left and right outside of the planting transmission case 31, and a sun gear 92 built in the rotary case 36 is fixed to the projecting end. Although details are omitted, the rotary case 36 is rotatably held at the rear end of the planting transmission case 31.

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

As is clearly shown in FIG. 5, the planting claw member 37 includes a planting claw 96 and a protruding rod 97, and as shown in FIG. 5 (C), the planting claw 96 provides one seedling from the seedling mat. The seedlings are planted in the field by cutting out only the seedlings and transferring them to the field, and by projecting the rod 97 in the vicinity of the bottom dead center and advancing relative to the planting claw 96.

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

The downstream non-constant velocity main driving bevel gear 98 has a stepped boss body 98a, and the coupling 100 is fitted in a small diameter portion of the boss body 98a. A bearing 101 is fitted in the boss body 98a. The coupling 100 is welded and fixed to the planting transmission shaft 87 and is held so as not to rotate relative to each other. The downstream non-constant 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 the strip stop clutch 102. An operation ring 105 is integrally welded to the streak clutch 102.

The streak clutch 102 is slidable on the planting center shaft 91 and is held so as not to rotate relative to each other. Then, the streak clutch 102 is normally pushed by the spring 106 so as to mesh with the downstream non-constant velocity driven bevel gear 99. When the operation rod 129 is operated, the strip stop clutch 102 is separated from the downstream non-constant 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 ridge, a part of the four pairs of transplanting mechanisms 8 may not be operated. In such a case, the strip stop clutch 102 is operated to operate some of the transplanting mechanisms 8. The function can be stopped. In other words, the bar-stopping function that reduces the number of planted rows is demonstrated.

(5). Downstream non-constant velocity member In the embodiment, the downstream non-constant velocity bevel gear pair 98,99 is provided with a function of causing non-constant velocity rotation (acceleration / deceleration) (downstream non-uniform velocity bevel gear pair 98, 99 as a downstream non-constant velocity member). Is adopted). This point will be described mainly with reference to FIGS. 10 and 9 (C). As shown in FIG. 10 (E), when forming a large number of teeth 107 on the downstream non-uniform velocity driven bevel gear 98, the distance from the tip of each tooth 107 to the axial center O1 is set to gradually widen and narrow again. doing. That is, each tooth 107 has a pitch cone angle minimum portion 108 having the narrowest distance from the axial center O1 to the tip, and a pitch cone angle maximum portion 109 having the widest distance from the axial center O1 to the tip. The interval between the two is gradually changing.

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). From the opposite point of view, in the 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, but in the downstream non-uniform velocity driving bevel gear 98 of the embodiment, the virtual weight is virtual. 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 non-constant velocity driven bevel gear 99 has teeth 112 that are twice the number of teeth of the downstream non-constant velocity driven bevel gear 98. Then, as can be clearly grasped from FIGS. 10A and 10B, the axial positions of the teeth 112 are slightly deviated. In other words, even in the downstream non-constant velocity driven bevel gear 99 of the embodiment, as in the case of the downstream non-constant velocity driven bevel gear 98, as the outer peripheral surface of the virtual weight shifts in the circumferential direction, the inclination angle θ2 of the outer peripheral surface is θ2 (FIG. 10). (See (A)) is gradually changed.

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

In this way, the pitch circles 110 and 115 of the downstream non-uniform velocity bevel gears 98 and 99 have a shape close to an ellipse and are eccentric with respect to a perfect circle centered on the rotation axes O1 and O2, and then the outer diameter shape thereof. By making each a perfect circle, the pairs of downstream non-uniform velocity bevel gears 98 and 99 can be formed to the same size as the normal bevel gears, respectively, and the assembly space for the downstream non-uniform velocity bevel gears 98 and 99 pairs in the power transmission system. Can be made smaller and more compact. In this case, the idea of manufacturing the downstream non-uniform velocity bevel gears 98 and 99 is to cut the distorted conical shape formed by keeping the conical distance constant with a cylinder having common rotation axes O1 and O2, and make the outer diameter shape true. It will be made into a circle.

Here, the downstream non-constant velocity bevel gear pairs 98, 99 also adjust the mounting phase in the same manner as the upstream non-uniform velocity first to fourth gears 48, 56, 121, 122, and set the above-mentioned maximum speed phase to the bottom dead center. The setting can be changed in the direction further away from. FIG. 13 shows, as an example, the change in the angular velocity of the planted claw 96 when the strain is set to 43 strains having a non-constant velocity. The thick alternate long and short dash line in FIG. 13A shows the upstream non-uniform speed 3rd gear 121 and the upstream non-uniform speed 4th gear 122 assembled so that the front side (upstream side) from the bottom dead center has the maximum speed phase MS1. In this case, the downstream non-uniform velocity bevel gear pairs 98 and 99 are assembled so that the maximum speed phase MS1'(see FIG. 12) is further set on the front side of the bottom dead center. The thick solid line in FIG. 13B shows the upstream non-uniform speed 3rd gear 121 and the upstream non-uniform speed 4th gear 122 assembled and the downstream non-uniform speed bevel gear pair so that the maximum speed phase MS2 is set near the bottom dead center. This is the case when 98 and 99 are assembled. In the thick two-dot chain line of FIG. 13C, the upstream non-uniform speed third gear 121 and the upstream non-uniform speed fourth gear 122 are assembled so that the rear side (downstream side) from the bottom dead center is the maximum speed phase MS3. This is a case where the downstream non-uniform velocity bevel gear pairs 98 and 99 are assembled so that the maximum speed phase MS3'(see FIG. 12) is further rearward from the bottom dead center. With such a 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 promoted.

(6). Summary FIG. 5 (C) shows the relationship between the number of planted stocks per 3.3 square meters and the operation locus of the planted claw 96. As can be seen from this figure, even if the planting claw 96 rises directly above the bottom dead center during dense planting, the planting claw 96 may not escape easily during sparse planting, causing a phenomenon in which the seedlings are moved forward. Understandable.

In the embodiment, the inter-stock transmission 26 is provided with the upstream non-constant speed first to fourth gears 48, 56, 121, 122, and the seedling planting device 2 is provided with the downstream non-uniform 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 becomes high in the vicinity of the planting claw 96 located at the bottom dead center. Therefore, the planting claw 96 quickly escapes from the bottom dead center, and as a result, the phenomenon that the planting claw 96 moves the seedling forward can be prevented.

In the embodiment, since the non-uniform speed member is separately arranged in the inter-stock transmission device 26 and the seedling planting device 2, the range from the inter-stock transmission device 26 to the downstream non-uniform speed bevel gear pairs 98 and 99 is compared with the conventional case. The ratio of non-constant speed rotation is small. As a result, the twist generated in the transmission elements (PTO shaft 29, the planting drive shaft 32, the planting transmission shaft 87, etc.) constituting the power transmission system is remarkably suppressed, and the smooth movement of the transplant mechanism 8 can be ensured. In addition, since the backlash generated in the power transmission system can be suppressed, it is possible to prevent problems such as the timing of non-constant velocity shifting and the planting posture of seedlings being disturbed.

Since the transplanting mechanism 8 has a form in which the planting claw members 37 are swingably attached to both ends of the elongated rotary case 36, the planting claw member 37 itself plays the role of a weight and a large inertial force is generated. Moreover, a large load is generated when the seedlings are scraped, and then a negative load is generated. That is, due to the swing 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 noticeable when the resonance rotation speed is exceeded even if the torque is rotated at a constant speed during dense planting (because the transplantation mechanism 8 rotates at a higher speed during dense planting than during sparse planting).

Furthermore, even if the transplanting mechanism 8 rotates at a constant velocity, when one planting claw member 37 escapes from the field, the other planting claw member 37 shifts to scraping seedlings, and therefore two. It can be said that the planted claw members 37 act to cancel each other's load fluctuations. However, since a large torque is required for scraping the seedlings, the function of leveling the torque fluctuation is weak only by the movement of the two planting claw members 37. Therefore, the transplant mechanism 8 does not rotate smoothly, and a phenomenon called "hiccups" is likely to occur.

On the other hand, when the transplanting mechanism 8 is given a slight non-constant velocity rotation by the downstream non-uniform velocity bevel gear pairs 98 and 99 even in the densely planted state as in the embodiment, the seedlings are scraped by the planting claw member 37 due to inertial force. In addition, since the transplantation mechanism 8 decelerates after the seedlings are scraped, it is possible to suppress the action of a large inertial force on the transplantation mechanism 8. Therefore, the load fluctuation (or torque fluctuation) acting on the transplant mechanism 8 can be leveled to ensure smooth rotation.

(7). First Example 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. In the rice planting machine of the embodiment, the rotational torque T of the transplantation mechanism 8 based on the non-constant velocity rotational power of the upstream non-constant velocity and the downstream non-constant velocity bevel gear pairs 98 and 99 is opposite to the rotational torque T. The anti-phase torque generating member 130 for adding the phase torque Tan is provided. In the first embodiment, the anti-phase torque generating member 130 is provided in each of the plurality of (4) planting transmission cases 31. Since each planting transmission case 31 is provided with a strip stop clutch 102, a counterphase torque generating member 130 is present for each combination of a total of four sets of the planting transmission case 31 and the strip stop clutch 102.

As shown in FIGS. 14 to 17, a hollow end case 131 is integrally provided on the rear end side of the planting transmission case 31. The end case 131 may have a separate structure that is detachably attached to the rear end side of the planting transmission case 31. The inside of the planting transmission case 31 and the inside of the end case 131 communicate with each other. A front-rear longitudinal planting branch shaft 132 is rotatably supported at a communication point between the inside of the planting transmission case 31 and the inside of the end case 131 via a bearing. A leveling bevel gear 133 that constantly meshes with the downstream non-uniform velocity 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 non-uniform speed main driving bevel gear 98 are in a positional relationship of facing (opposing) each other in front of and behind the planting center shaft 91.

The leveling bevel gear 133 is formed in the same shape as the downstream non-constant velocity main driving bevel gear 98. That is, the leveling bevel gear 133 has the same number of teeth as the downstream non-uniform speed driving bevel gear 98, and like the downstream non-uniform speed driving bevel gear 98, the pitch cone angle is rotated in the rotation direction while the cone distance is constant. It is formed into a shape that is continuously changed along the line. Therefore, the leveling bevel gear 133, and thus the planted branch shaft 132, rotates in the opposite direction at the same speed as the downstream non-uniform speed main driving bevel gear 98 (it rotates twice as fast as the downstream non-uniform speed driven bevel gear 99). ..

The rear end side of the planting branch shaft 132 projects in the middle of the upper and lower parts of 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. Therefore, the planting branch shaft 132 and the eccentric shaft 134 have a crankshaft shape (exhibiting the function of the crankshaft). A locking pin 135 is attached to the lower side of the end case 131. A tension spring 136 is mounted on the eccentric shaft 134 and the locking pin 135 as a means for generating anti-phase torque. The tension spring 136 is constantly urged in the direction of moving the eccentric shaft 134 to the lower side of the planting branch shaft 132. When the eccentric shaft 134 passes directly above the planting branch shaft 132, the tension spring 136 is set to cross the fulcrum. In the first embodiment, the planting branch shaft 132, the eccentric shaft 134, and the tension spring 136 constitute the anti-phase torque generating member 130.

A drive spur gear 137 is fixed to a protruding portion on the rear end side of the planted branch shaft 132. A power take-out shaft 138 extending parallel to the planting branch shaft 132 is rotatably supported on the upper side in the end case 131. The driven spur gear 139 is fixed on the front side of the power take-out shaft 138. The drive spur gear 137 and the driven spur gear 139 are always meshed with each other. The rear end side of the power take-out shaft 138 projects 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-out shaft 138 via the downstream non-uniform velocity 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. Will 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 extraction 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 central shaft 91 in the transplantation mechanism 8, the antiphase torque Tan, and the combined torque Tco obtained by synthesizing them. The alternate long and short dash line in FIG. 18 represents the rotational torque T (variable torque) of the planting central shaft 91, and the rotational torque T is near the bottom dead center where each planting claw 96 of the planting claw member 37 plants seedlings. It will be the largest. The alternate long and short dash line in FIG. 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), and each planting claw of the planting claw member 37. The anti-phase torque Tan is the smallest near the bottom dead point where 96 plants the seedlings.

The elastic stability 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-constant velocity driven bevel gear 99. As a result, as shown by the solid line in FIG. 18, the rotational torque T and the anti-phase torque Tan are combined, and the combined torque Tco is transmitted to the transplantation mechanism 8. That is, the rotational torque T leveled (offset) by the synthesis of the anti-phase torque Tan is transmitted to the transplantation mechanism 8. Therefore, the load fluctuation (which may be called torque fluctuation) acting on the transplant mechanism 8 is leveled, and the smooth rotation of the transplant mechanism 8 can be ensured. Therefore, it is possible to suppress the occurrence of a phenomenon called "hiccups" and plant seedlings in an appropriate planting posture.

As is clear from the above description and FIGS. 8 and 14 to 18, a mission case 11 for shifting the power of the engine 10 mounted on the traveling machine 1 and a planting claw 96 for drawing a non-circular operation locus are included. The seedling planting device 2 having the transplanting mechanism 8 of the above, the inter-strain transmission 26 that changes the operating speed of the transplanting mechanism 8 with respect to the traveling speed of the traveling machine 1 to change the inter-stocks, and the transplanting mechanism 8 have a non-uniform speed. In a rice planting machine provided with non-constant velocity members 98 and 99 for transmitting rotational power, the rotational torque T of the transplanting mechanism 8 based on the non-constant velocity rotational power is in the opposite phase to the rotational torque T. Since the anti-phase torque generating member 130 for adding 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 transplanting mechanism 8 due to the non-constant velocity rotational power. T is offset, and the load fluctuation (which may be called torque fluctuation) acting on the transplant mechanism 8 is leveled, so that the smooth rotation of the transplant mechanism 8 is ensured. Therefore, it is possible to suppress the occurrence of a phenomenon called "hiccups" and plant seedlings in an appropriate planting posture.

In particular, the power transmission system from the inter-stock transmission 26 to the transplant mechanism 8 includes rotating shafts 87 and 91 that intersect each other, and these intersecting rotating shafts 87 and 91 are configured to transmit power via a bevel gear pair. As the non-constant speed member, the bevel gear pair is configured as the non-constant speed gear pair 98, 99, and the anti-phase torque generating member 130 is attached to the non-uniform speed gear 99 on the downstream side of the non-uniform speed gear pairs 98, 99. Because the existing members of the non-constant speed gear pairs 98 and 99 can be utilized, it is advantageous in terms of cost.

(8). Second and Third Examples 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 first is that the end case 131 is removed from the rear end side of the planting transmission case 31 and the anti-phase torque generating member 130 is arranged on the rear side of the planting transmission case 31. It is different from that of the embodiment.

In this case, external teeth 141 are formed on the outer peripheral side of the operation ring 105 of the strip stop clutch 102. The outer teeth 142 of the operation ring 105 are meshed with a leveling spur gear 143 rotatably supported on the rear side in the planting transmission case 31. The rotation center shaft 144 of the leveling spur gear 143 extends parallel to the planting center shaft 91. A locking pin 145 is erected on one side surface of the leveling spur gear 143.

A tension spring 146 as a means for generating anti-phase torque is mounted on the locking pin 145 and the inner peripheral wall of the planting transmission case 31. The tension spring 146 constantly urges the locking pin 145 in the direction 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 have a kind of crank structure. In the second embodiment, the operation ring 105 of the strip stop clutch 102, the leveling spur gear 143, the locking pin 145, and the tension spring 146 form the anti-phase torque generating member 130. That is, the anti-phase torque generating member 130 is positioned on the downstream side of the strip stop clutch 102 in the planting transmission case 31. In the second embodiment as well, as in the case of the first embodiment, the anti-phase torque generating member 130 exists for each combination of the planting transmission case 31 and the streak clutch 102 of a total of four sets.

In the case of the above configuration, the elastic stability 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 streak clutch 102. As a result, as in the case of the first embodiment (as shown by the solid line in FIG. 18), the rotational torque T and the anti-phase torque Tan are combined, the combined torque Tco is transmitted to the transplanting mechanism 8, and the transplanting mechanism A smooth rotation of 8 can be ensured. Therefore, as in the case of the first embodiment, it is possible to suppress the occurrence of a phenomenon called "hiccups" and plant the seedlings in an appropriate planting posture.

Further, since the anti-phase torque generating member 130 is arranged on the downstream side of the strip stop clutch 102 in the planting transmission case 31, the anti-phase torque generating member 130 is located in the vicinity of the transplanting mechanism 8 which is the source of the load fluctuation. Will be positioned. Therefore, the effect of canceling the rotational torque T of the transplanting mechanism 8 with the anti-phase torque Tan, that is, the effect of leveling the load fluctuation is high. Moreover, since the anti-phase torque Tan is not generated when the strip stop clutch 102 is in the power cutoff state, there is no possibility that unnecessary torque is propagated around the transplant mechanism 8.

FIG. 20 shows a third embodiment of the anti-phase torque generating member 130. The third embodiment shown in FIG. 20 is a modification of the second embodiment described above. The third embodiment is common to the second embodiment in that the anti-phase torque generating member 130 is arranged on the rear side in the planting transmission case 31 and on the downstream side of the streak clutch 102. It is different from that of the second embodiment in that the anti-phase torque generating member 130 is provided separately from the streak clutch 102.

In this case, the leveling first flat gear 152 is fixed to the opposite side of the strip stop clutch 102 with the downstream non-uniform velocity driven bevel gear 99 sandwiched between the planting central shaft 91. The leveling first spur gear 152 meshes with the leveling second spur gear 153 rotatably supported on the rear side in the planting transmission case 31. The rotation center shaft 154 of the leveling second spur gear 153 extends parallel to the planting center shaft 91. A locking pin 155 is erected on one side surface of the leveling second spur gear 153.

A tension spring 156 as a means for generating anti-phase torque is mounted on the locking pin 155 and the inner peripheral wall of the planting transmission case 31. The tension spring 156 constantly urges the locking pin 155 in the direction away from the leveling first spur gear 152. The tension spring 156 expands and contracts due to the rotation of the leveling second spur gear 153. The leveling second spur gear 153 and the tension spring 156 have a kind of crank structure. In the third embodiment, the leveling first and second spur gears 152 and 153, the locking pin 155 and the tension spring 156 constitute the anti-phase torque generating member 130. In the third embodiment as well, the anti-phase torque generating member 130 exists for each combination of the planting transmission case 31 and the streak clutch 102 of a total of four sets. Even when configured as described above, the same effects as those in the second embodiment are obtained.

As is clear from the above-described embodiment and FIGS. 19 and 20, a transmission case 11 for shifting the power of the engine 10 mounted on the traveling machine 1 and a transplant with a planting claw 96 for drawing a non-circular operation locus. The seedling planting device 2 having the mechanism 8, the inter-strain transmission device 26 that changes the operating speed of the transplanting mechanism 8 with respect to the traveling speed of the traveling machine 1 to change the inter-stocks, and the transplanting mechanism 8 have a non-uniform rotational power. In the rice planting machine provided with the non-constant velocity members 98 and 99, the rotational torque T of the transplanting mechanism 8 based on the non-constant velocity rotational power is opposite to the rotational torque T. Since the anti-phase torque generating member 130 for adding the phase torque Tan is further provided, the anti-phase torque Tan from the anti-phase torque generating member 130 causes the rotational torque T of the transplanting mechanism 8 to be generated by the non-constant velocity rotational power. It will be offset, and the load fluctuation (which may be called torque fluctuation) acting on the transplant mechanism 8 will be leveled, and the smooth rotation of the transplant mechanism 8 will be ensured. Therefore, it is possible to suppress the occurrence of a phenomenon called "hiccups" and plant seedlings in an appropriate planting posture.

Further, when the strip stop clutch 102 is in the power cutoff state, the anti-phase torque Tan is not generated, and there is no possibility that unnecessary torque is propagated around the transplant mechanism 8. Moreover, in the front-rear longitudinal planting transmission case 31 of the seedling planting device 2, a strip-stop clutch 102 for interrupting power transmission from the inter-strain transmission 26 to the transplanting mechanism 8 is provided, and the planting transmission case Since the anti-phase torque generating member 130 is arranged on the downstream side of the strip stop clutch 102 in 31, the anti-phase torque generating member 130 is positioned in the vicinity of the transplanting mechanism 8 which is the source of load fluctuation. The anti-phase torque Tan cancels out the rotational torque T of the transplanting mechanism 8, that is, the effect of leveling the load fluctuation is high.

(9). Fourth to Ninth Examples of Anti-Phase Torque Generation Member Next, a fourth embodiment of the anti-phase torque generation member 130 will be described with reference to FIGS. 21 and 22. In the fourth embodiment, the anti-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 driven sprocket 161 is rotatably supported on the planting drive shaft 32 in the planting transmission case 31, while the driven sprocket 162 is rotatably supported on the planting center shaft 91. In the planting transmission case 31, a chain 163 for power transmission is wound around the main sprocket 161 and the driven sprocket 162. A torque limiter 164 is slidably fitted to the planting drive shaft 32 so that it cannot rotate relative to each other. When a load of a predetermined value or more is applied to the planting drive shaft 32, the torque limiter 164 is disengaged and the power transmission from the planting drive shaft 32 to the main sprocket 161 is cut off. The planting center shaft 91 is fitted with a streak clutch 102 that connects the power transmission from the driven sprocket 162 to the planting center shaft 91 so as to be slidable and non-relatively rotatable. As shown in FIG. 22, the main sprocket 161 and the driven sprocket 162 are formed as an elliptical (non-circular) non-constant velocity sprocket. An idle roller 163'is brought into contact with the chain 163. With such a configuration, the planting center shaft 91 is provided with non-constant velocity rotation. In the fourth embodiment, the reduction ratio in the chain 163 transmission is 1/2 on average.

A power take-out shaft 165 extending in parallel with the planting center shaft 91 is rotatably supported on the rear end side of the planting transmission case 31 with respect to the planting center shaft 91. One end side (right end side in the embodiment) of the power take-out shaft 165 is projected outward from the planting transmission case 31 to the left and right. The leveling main sprocket 166 is fixed to the opposite side of the streak clutch 102 with the driven sprocket 162 sandwiched between the planting center shaft 91, while the leveling driven sprocket 167 is fixed to the power take-out shaft 165. ing. A chain 168 for power transmission is wound around a main sprocket for leveling 166 and a driven sprocket for leveling 167. The rotational power of the planting center shaft 91 is branched and transmitted to the power take-out shaft 165 via the sprocket and the chain transmission system 166 to 168. When an optional device such as a chemical sprayer is attached to the seedling planting device 2, the rotational power of the power extraction shaft 165 is transmitted to the optional device.

The other end side of the power take-out shaft 165 is bent in a crank shape. A tension spring 169 as a means for generating anti-phase torque is mounted on the crank tip side of the power take-out shaft 165 and the inner peripheral wall of the planting transmission case 31. The tension spring 169 is constantly urged to move the crank tip side of the power take-out shaft 165 to the lower side of the rotation center of the power take-out shaft 165. The rotation of the power take-out shaft 165 via the leveling driven sprocket 167 causes the tension spring 169 to expand and contract. In the fourth embodiment, the power take-out shaft 165, the leveling main and driven sprockets 166, 167, the chain 168 and the tension spring 169 constitute the anti-phase torque generating member 130. That is, the power take-out shaft 165 is one of the components of the anti-phase torque generating member 130. In the fourth embodiment as well, the anti-phase torque generating member 130 exists for each combination of the planting transmission case 31 and the streak clutch 102 of a total of four sets. Even when configured as described above, the same effects as in the second and third embodiments are obtained.

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

The sixth embodiment shown in FIG. 24 and the seventh embodiment shown in FIG. 25 are modifications of the fourth embodiment shown in FIGS. 21 and 22. In the sixth embodiment shown in FIG. 24, the main sprocket 161 provided on the planting drive shaft 32 is formed as a circular constant velocity sprocket. In the seventh embodiment shown in FIG. 25, the main sprocket 161 provided on the planting drive shaft 32 is formed as a circular but eccentric non-constant velocity sprocket. In the sixth and seventh embodiments, the reduction ratio in the chain 163 transmission is 1/2 on average.

In the eighth embodiment shown in FIG. 26, the main sprocket 161 provided on the planting drive shaft 32 is configured as a circular but eccentric non-constant velocity sprocket, and the driven sprocket 162 provided on the planting central shaft 91 is a circular constant velocity sprocket. I'm using a sprocket. The reduction ratio in the chain 163 transmission in this case is also 1/2 on average.

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

As is clear from the above-described embodiment and FIGS. 21 to 27, a transmission case 11 for shifting the power of the engine 10 mounted on the traveling machine 1 and a transplant with a planting claw 96 for drawing a non-circular operation locus. The seedling planting device 2 having the mechanism 8, the inter-strain transmission 26 that changes the operating speed of the transplant mechanism 8 with respect to the traveling speed of the traveling machine 1 to change between stocks, and the transplant mechanism 8 have non-constant speed rotational power. In a rice planting machine provided with non-constant velocity members 161, 162 for transmitting the above, the rotational torque T of the transplanting mechanism 8 based on the non-constant velocity rotational power is opposite to the rotational torque T. A reverse phase torque generating member 130 for adding a phase torque Tan is further provided, and power can be transmitted to the planting transmission case 31 which is longitudinally longitudinal in the seedling planting device 2 and to an optional device mounted on the seedling planting device 2. Since the power take-out shaft 165 is provided and the power take-out shaft 165 is a component of the anti-phase torque generating member 130, the load fluctuation (torque fluctuation) acting on the transplantation mechanism 8 is leveled and the transplantation mechanism 8 is used. While ensuring smooth rotation, the power take-out shaft 165 can be effectively used to be used as the anti-phase torque generating member 130, and the power transmission structure to the seedling planting device 2 can be simplified and reduced in weight. Can contribute to.

(10). Others The invention of the present application can be embodied in various ways other than the above-described embodiments. For example, the inter-stock transmission 26 can be built in the mission case 11, and in this case, one upstream non-constant velocity member is built in the mission case 11. When a non-constant velocity member is provided for each of the traveling machine body 1 and the seedling planting device 2, the acceleration / reduction ratio (non-constant velocity ratio) may be set as necessary. Therefore, in some cases, the acceleration / deceleration ratio (non-constant velocity ratio) on the traveling machine body 1 side can be made smaller than the non-constant velocity conversion ratio on the seedling planting device 2. A belt transmission (preferably a timing belt) may be adopted instead of the chain transmission. In any of the first to ninth embodiments, the crank structure portion and the tension spring of the anti-phase torque generating member 130 can be arranged outside the planting transmission case 31.

1 Traveling machine 2 Seedling planting device 8 Transplant mechanism 10 Engine 11 Mission case 26 Inter-sprocket transmission 36 Rotary case 37 Planting claw member 40 Inter-sprocket case 87 Planting transmission shaft 91 Planting center shaft 96 Planting claw 98 Downstream non-uniform speed Main driving bevel gear 99 Downstream non-uniform speed driven bevel gear 102 Thread stop clutch 105 Operation ring 130 Opposite phase torque generating member 131 End case 132 Planted branch shaft 133 Leveling bevel gear 134 Eccentric shaft 136 Tensile spring 142 External teeth 143 Leveling flat Gears 145, 155 Locking pins 146, 156, 169 Pull spring 152 1st flat gear for leveling 153 2nd flat gear for leveling 161 Driven sprocket 162 Driven sprocket 163, 168 Chain 164 Torque limiter 165 Power take-out shaft 166 Leveling Main drive sprocket 167 Leveling driven sprocket 169 Tensile spring

Claims (5)

A seedling planting device supported by the running part,
It is equipped with an inter-strain transmission that can transmit power to the seedling planting device and change the working speed of the seedling planting device with respect to the traveling speed of the traveling unit.
The inter-strain transmission can switch the power transmitted to the seedling planting device in multiple stages.
The inter-strain transmission includes a first switching mechanism and a second switching mechanism for switching the input power in a plurality of shift stages on the power transmission path to the seedling planting device.
The power transmitted to the seedling planting device can be switched by the combination of each shift stage selected by the first switching mechanism and the second switching mechanism.
Among the plurality of powers, the operating speed of the seedling planting device with respect to the traveling speed includes a dense planting power having a predetermined speed and a sparse planting power having a speed slower than the dense planting power, and the sparse planting power is the first switching mechanism. By selecting the speed change stage for sparse planting and selecting the corresponding specific speed change stage in the second switching mechanism, the transmission to the seedling planting device is configured.
Of the plurality of powers, the powers other than the sparsely planted powers are planted in any combination of the gears different from the sparsely planted gears in the first switching mechanism and the gears selectable in the second switching mechanism. It is configured so that it can be transmitted to the device.
Rice transplanter. Of the plurality of powers, the power other than the sparsely planted power can be any combination of the plurality of gears that can be selected by the first switching mechanism other than the sparsely planted gears and the second gears that can be selected by the second switching mechanism. , Configured so that it can be transmitted to the seedling planting device,
The rice transplanter according to claim 1. Of the plurality of powers, the power for sparse planting, which has the slowest operating speed of the seedling planting device with respect to the traveling speed, selects the sparsely planted shift stage in the first switching mechanism and corresponds to a specific speed change in the second switching mechanism. By selecting the stage, it is configured to transmit to the seedling planting device,
The rice transplanter according to claim 2. The sparsely planted transmission stage of the first switching mechanism is a non-constant speed member that transmits power at a non-constant speed.
The rice transplanter according to claim 1. The inter-stock transmission has at least two sparsely planted transmission stages in the first switching mechanism.
The second switching mechanism has different specific gears corresponding to the sparsely planted gears of the first switching mechanism.
The rice transplanter according to claim 1 or 4.

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