JP2015039301A - Rice transplanter - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rice transplanter having a rotary type seedling planting device capable of correcting defects such as twisting of power transmission elements attributable to functioning of a non-uniform velocity member.SOLUTION: A rice transplanter of the present invention includes a reverse phase torque generation member 130 for adding a reverse phase torque Tan which becomes a reverse phase to a rotation torque T of a transplant mechanism 8 on the basis of a non-uniform velocity rotation power. The rice planter also includes a row-stopping clutch 102 for connecting or disconnecting the power transmission to the transplant mechanism 8 from a spacing speed change gear 26, in an elongate planting transmission case 31 of a seedling planting device 2. The reverse phase torque generation member 130 is disposed in the downstream side of the row-stopping clutch 102 in the planting transmission case 31.

Description

  The present invention relates to a rice transplanter in which a seedling planting apparatus having a seedling platform and a plurality of planting claws is attached to a traveling machine body and a seedling planting operation is continuously performed.

  In a conventional rice transplanter, a seedling planting apparatus having a seedling stage and a transplanting mechanism with planting claws is mounted on the rear part of the traveling machine 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. When the rotary case rotates once, the two planting claws are opposite to the rotary case. Make one turn in the direction. That is, the planting claw rotates while revolving around the axis of the rotary case.

  In seedling planting work using this type of rice transplanter, planting claws facing the direction of the front seedling platform are made while intermittently feeding the seedling platform on which the seedling mat is placed to the left and right at regular intervals. By revolving around the axis of the rotary case, the planting claws are reciprocated between the seedling stage and the field scene, and the seedlings are scraped one by one from the seedling mat and planted in the field. The operation period (planting period) of the planting claws in the seedling planting apparatus is linked to the traveling speed of the traveling machine body, and the seedling planting interval (between plants) 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 necessarily constant. For example, the desired number of plants to be planted per unit area varies depending on the region or the user. In this regard, the conventional rice transplanter is provided with an inter-strain 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 by the inter-strain transmission, the inter-strain is changed and the number of planted strains per unit area is changed.

  In recent years, taking into consideration the growth conditions of seedlings planted in the field, sparse planting has been carried out in which the plant spacing is longer than that of standard planting. However, the planting speed needs to be slowed as the plant strain increases. However, if the planting speed is simply slowed down by the inter-strain transmission, there is a problem that the planting claw tip is dragged in the field and the seedling falls forward or a floating seedling is generated.

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

Japanese Patent No. 4376154 JP 2003-189712 A

  Now, the power transmission system from the inter-strain transmission to the transplanting mechanism is composed of transmission elements such as gears and rotating shafts. A transmission element such as a rotating shaft is not a perfect rigid body, and is slightly elastically deformed when a load (rotational torque) is applied, and returns and deforms with an elastic restoring force when the load is released. That is, in the transmission element of the power transmission system, torsion and torsion release occur alternately with rotation, and this appears as vibration. On the other hand, the inconstant velocity member accelerates and decelerates the angular velocity during one rotation of the transmission element, and the load fluctuation acting on the transmission element is further increased by the acceleration and deceleration. For this reason, in the configuration in which the inconstant speed member functions at the time of sparse planting as in the above prior art, the vibration of the transmission element appears remarkably, and the operation period of the planting claw is shifted, resulting in poor planting. was there. Such a tendency appears more prominently as the traveling speed of the traveling vehicle increases.

  This invention is made | formed in view of the above present conditions, and is trying to prevent the malfunction, enjoying the advantage of an inconstant speed member.

  The invention according to claim 1 is a transmission case for shifting the power of an engine mounted on a traveling machine body, a seedling planting device having a transplanting mechanism with a planting claw for drawing a non-circular motion locus, and a traveling speed of the traveling machine body In a rice transplanter comprising: an inter-strain transmission for changing the strain between the transplant mechanisms by changing the operating speed of the transplant mechanism; and an inconstant speed member for transmitting the inconstant speed rotational power to the transplant mechanism. A reverse phase torque generating member that adds a reverse phase torque that is in a phase opposite to the rotational torque to the rotational torque of the transplanting mechanism based on power, further comprising a front / rear longitudinal planting transmission case in the seedling planting device In the planting transmission case, the reverse phase torque is generated downstream of the latching clutch in the planting transmission case. It is that are disposed member.

  According to a second aspect of the present invention, in the rice transplanter according to the first aspect, a plurality of combinations of the planting transmission case and the streaking clutch are provided, and the antiphase torque generating member is provided for each combination. It is.

  An inconstant speed gear is also arranged inside the rotary case constituting the transplanting mechanism, which operates the planting claw so as to draw a long non-circular motion trajectory up and down. This is different from an inconstant speed member (that is, a member that imparts inconstant speed rotation (acceleration / deceleration) to a transmission element of a power transmission system).

  According to the present invention, a transmission case for shifting the power of an engine mounted on a traveling machine body, a seedling planting device having a transplanting mechanism with a planting claw for drawing a non-circular motion locus, and the traveling speed of the traveling machine body In a rice transplanter equipped with an inter-strain transmission that changes the operating speed of the transplanting mechanism to change the stock, and an inconstant speed member that transmits the inconstant speed rotational power to the transplanting mechanism, The anti-phase torque generating member further includes an anti-phase torque generating member for adding an anti-phase torque having a phase opposite to that of the rotational torque with respect to the rotational torque of the transplanting mechanism based on the anti-phase torque generated from the anti-phase torque generating member. Cancels out the rotational torque of the transplantation mechanism due to the inconstant speed rotational power, and leveles load fluctuations (which may be referred to as torque fluctuations) acting on the transplantation mechanism. Smooth rotation of the mechanism is ensured. Therefore, it is possible to plant seedlings in an appropriate planting posture while suppressing the occurrence of a phenomenon called “shakuri”.

  Further, when the streak clutch is in a power cut-off state, the reverse phase torque is not generated, and there is no possibility that unnecessary torque is propagated around the transplantation mechanism. In addition, in the planting transmission case of the longitudinal direction in the seedling planting device, there is provided a strut clutch for interrupting power transmission from the inter-strain transmission to the transplant mechanism, and the stapling is stopped in the planting transmission case. Since the anti-phase torque generating member is disposed downstream of the clutch, the anti-phase torque generating member is positioned in the vicinity of the transplant mechanism that is the source of load fluctuation, and the anti-phase torque is The effect of offsetting the rotational torque of the transplantation mechanism, that is, the effect of leveling load fluctuations is high.

It is a top view of the 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 which shows the whole power transmission path | route, (B) is a perspective view of a transplant mechanism. (A) is a side view of a power transmission path, (B) is a side view of a place of a transplant mechanism, and (C) is a view showing a locus of a planting claw. (A) is a top view which shows a power transmission path | route, (B) is an external appearance perspective view of a stock change apparatus, (C) and (D) are external appearance perspective views of the center case provided in the planting part. (A) is an external appearance perspective view of the gear group in a stock change apparatus and a center case, (B) is a perspective view of the gear group in a center case. It is a transmission system diagram. (A) is a top view which shows the power transmission path | route to a planting apparatus, (B) is the isolation | separation top view of the terminal planting part of a power transmission path | route, (C) is the schematic of a bevel gear. (A) And (B) is a top view which shows the meshing state of a bevel gear, (C) (D) is a perspective view of a bevel gear, (E) is a contrast figure which arranged the pair of bevel gears. It is a graph which shows the relationship between the combination of the gear in an inter-strain transmission, and the number of planting stocks. It is a figure which shows the movement locus | trajectory of the planting nail | claw at the time of setting to 43 stocks of inconstant 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 unequal speed. It is a top view which shows the arrangement structure of the transplant mechanism in 1st Example. It is a plane sectional view showing a power transmission structure in a planting transmission case. It is an expanded plane sectional view of the rear part of a planting transmission case. It is an expanded side sectional view of the planting transmission case rear part. It is a figure which shows the relationship between the rotational torque of a transplant mechanism, and an antiphase torque. It is a power transmission system diagram from the planting transmission case to the transplanting mechanism in the second embodiment. It is a power transmission system diagram from the planting transmission case to the transplanting mechanism in the third embodiment. It is a power transmission system figure from the planting transmission case in 4th Example to the transplanting mechanism. It is explanatory drawing which shows typically the inconstant velocity member in 4th Example. It is explanatory drawing which shows typically the inconstant velocity member in 5th Example. It is explanatory drawing which shows typically the inconstant velocity member in 6th Example. It is explanatory drawing which shows typically the inconstant velocity member in 7th Example. It is explanatory drawing which shows typically the inconstant velocity member in 8th Example. It is explanatory drawing which shows typically the inconstant 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 riding type rice transplanter (hereinafter simply referred to as “rice transplanter”). In the following description, the front / rear / left / right wording is used to specify the direction, but the front / rear / left / right wording defines the forward direction of the rice transplanter as the front. The front view direction is opposite to the forward direction.

(1). First, an outline of a rice transplanter will be described with reference to FIGS. As shown in FIGS. 1-3, the rice transplanter has the traveling body 1 and the seedling planting apparatus 2 arrange | positioned behind it. The traveling machine body 1 has front and rear wheels 3, 4, a control seat 5, and a control handle 6, while the seedling planting device 2 has a seedling mounting base 7 and a transplanting mechanism 8 on which a seedling mat is placed. The rice transplanter of the embodiment is an eight-row planting type. For this reason, eight seedling mat placement areas are formed on the seedling placing stand 7, and eight transplanting mechanisms are provided at the rear portion 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 frame 9 made of a large number of frame members, and an engine 10 is supported by the front portion of the frame 9. A mission case 11 is disposed behind the engine 10. As clearly 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 hydrostatically continuously variable by a belt 13. Is transmitted to the machine (HST) 12. The engine 10 is covered with a hood 14. Further, a portion of the traveling machine body 1 excluding the hood 14 is covered with a vehicle body cover 15.

  A front axle device 17 is attached to the left and right side surfaces of the mission case 11, and the front wheel 3 is attached to the front axle device 17. A rear axle case 18 is disposed behind the transmission case 11, and the rear wheel 4 is attached to a rear axle that protrudes laterally from the rear axle case 18. The transmission case 11 and the rear axle case 18 are connected to each other by a longitudinal joint material 19. Two rear struts 20 are attached to the rear axle case 18, and the upper end of the rear strut 20 is fixed to a laterally long rear frame 9 a (see FIG. 3) that constitutes the rear end portion 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, the seedling planting device 2 moves up and down by expanding and contracting 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 by the rear wheel drive shaft 23. The rotation of the rear wheel drive shaft 23 is transmitted to the rear wheel 4 through a gear group provided on the rear axle case 18. The rice transplanter of the embodiment is provided with a leveling rotor 24 in the seedling planting device 2, and power is transmitted to the leveling rotor 24 by a rotor drive shaft 25 that protrudes backward from the rear axle case 18.

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

  The seedling planting apparatus 2 has a horizontally long main frame 28, and a center case 30 is fixed to a substantially right and left intermediate portion 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 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 left and right horizontally long planting drive shaft 32 passes through the front side (base end side) of the planting transmission case 31, and the transplanting mechanism 8 is driven by the rotation of the planting drive shaft 32 (details will be described later). To do). Further, power is transmitted from the PTO shaft 29 to the planting drive shaft 32 via a gear group built in the center case 30. The center case 30 is also provided with a laterally long lateral feed shaft 33, and the seedling stage 7 moves laterally by one pitch by the rotation of the lateral feed shaft 33.

  The seedling planting apparatus 2 has a group of belts 34 on which a seedling mat is placed, and the belts 34 are wound around a pair of upper and lower vertical feed shafts 35. When the seedling stage 7 has moved all the way to the left and right, the vertical feed support shaft 35 rotates and the seedling mat moves downward by one pitch.

  As shown in FIG. 4B, each transplantation mechanism 8 has one rotary case 36 and a planting claw member 37 that is rotatably provided at both ends thereof, and the rotary case 36 is rotated by half. Each time the seedling claw member 37 scrapes off the seedling and plantes it. Further, the rotary case 36 is set to rotate 1/2 when the PTO shaft 29 rotates once. The rotational speed of the PTO shaft 29 is basically proportional to the traveling speed of the traveling machine body 1, but by changing the relationship between the traveling speed and the rotational speed of the PTO shaft 29 by the stock transmission 26, seedling planting The interval (between stocks) can be changed.

(2). Inter-strain transmission structure / power transmission structure (upstream non-constant member)
Details of the power transmission system from the inter-strain transmission 26 to the transplanting mechanism 8 will be described below. First, the structure of the inter-strain transmission 26 and the power transmission structure corresponding thereto will be described mainly with reference to FIGS. The stock transmission 26 has a front / back split stock case 40 shown in FIG. 6 (B), and a gear group as shown in FIGS. 6 (A) and 6 (C) is arranged therein. .

  An input shaft 41 and an output shaft 42 are arranged inside the 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 cylindrical intermediate shaft 45 is fitted to the input shaft 41 so as to be relatively rotatable, and the intermediate shaft 45 is fitted in a state of rotating together with the output shaft 42 (a state in which relative rotation is impossible). A third gear 46 and a fourth gear 47 are slidably fitted on the intermediate shaft 45 by spline fitting or the like so as not to rotate relative to each other. Further, the upstream inconstant speed first gear 48 and the upstream inconstant speed third gear 121 are fitted to the intermediate shaft 45 so as to be relatively rotatable.

  A cam-type main clutch 49 is provided on the output shaft 42. The main clutch 49 includes a fixed part 49a and a slide part 49b. The slide part 49b is urged toward the fixed part 49a by a clutch spring 49c (see FIG. 7C). When the slide part 49b moves away from the fixed part 49a against the clutch spring 49c, 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 being lifted, such as when traveling on the road or turning. The disengagement operation of the main clutch 49 is performed by lowering the main clutch operation shaft 50.

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

  The idle shaft 51 meshes with the upstream inconstant speed fourth gear 122 that always meshes with the upstream inconstant speed third gear 121, the sixth gear 54 that meshes with and away from the third gear 46, and the fourth gear 47. The seventh gear 55 that separates and the upstream unequal speed second gear 56 that is always meshed with the upstream unequal speed first 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 sixth gear 54 to the third gear 46. Accordingly, the rotational 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 inconstant speed first gear 48 and the upstream inconstant speed second gear 56 are non-circular profiles such as ellipses, 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 both the inconstant speed gears 48 and 56, the rotational speeds of the idle shaft 51 and the output shaft 42 are the same, and The output shaft 42 rotates in a state where the angular velocity is periodically changed during one rotation. The two inconstant speed gears 48 and 56 are non-circular and are always kept in meshing because of the particularity that the phase of meshing is always determined. Similarly, the upstream inconstant speed third gear 121 and the upstream inconstant speed fourth gear 122 have non-circular profiles such as ellipses, 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 both the inconstant speed gears 48 and 56, the rotational speeds of the idle shaft 51 and the output shaft 42 are the same, and The output shaft 42 rotates in a state where the angular velocity is periodically changed during one rotation. That is, the upstream inconstant speed first gear 48 and the upstream inconstant speed second gear 56 are non-circular gear pairs such as eccentric gears, and have a large acceleration / deceleration ratio (inconstant speed ratio). The upstream inconstant speed third gear 121 and the upstream inconstant speed fourth gear 122 are also non-circular gear pairs such as eccentric gears, but have a small acceleration / deceleration ratio (inconstant speed ratio).

  Here, in the rotary case 36, for example, at the time of sparse planting of 37 strains / square m, the highest speed phase of each planting claw 96 in the planting claw member 37 (the phase where the operation speed of the planting claw 96 becomes the highest speed) Acceleration / deceleration is provided so as to be near the bottom dead center, but in the embodiment, the upstream inconstant speed first gear 48 and the upstream inconstant speed second gear 56 provided in the inter-variety transmission 26 are used. A slightly larger acceleration / deceleration is applied to the rotational power from the stock case 40 to output the inconstant rotational power. Therefore, since the acceleration / deceleration ratio (unequal speed ratio) is larger than the combination of the upstream inconstant speed third gear 121 and the upstream inconstant speed fourth gear 122, the bottom of the operating locus of the planting claw 96 is near the bottom dead center. The operating speed of the is greatly increased. Further, the upstream inconstant speed third gear 121 and the upstream inconstant speed fourth gear 122 give slightly smaller acceleration / deceleration to the rotational power from the stock case 40 to output the inconstant rotational power. Therefore, since the acceleration / deceleration ratio (unequal speed ratio) is smaller than the combination of the upstream inconstant speed first gear 48 and the upstream inconstant speed fourth gear 56, the bottom of the operating locus of the planting claw 96 is near the bottom dead center. Increase the operating speed of. The upstream inconstant speed first to fourth gears 48, 56, 121, and 122 correspond to upstream inconstant speed members on the inter-strain transmission 26 side that transmit the inconstant speed rotational power to the transplantation mechanism 8.

  The fourth gear 47 and the upstream inconstant speed first gear 48 are provided with a first intermediate clutch 57 that can be engaged and separated. When the fourth gear 47 slides further to the right from the state of FIG. 8 once engaged with the seventh gear 55, the first intermediate clutch 57 is engaged. In a state where the first intermediate clutch 57 is engaged, the power of the idle shaft 51 is transmitted to the output shaft 42 via the upstream inconstant speed second gear 56 and the upstream inconstant speed first gear 48. In a state where the first intermediate clutch 57 is engaged, the third gear 46 and the fourth gear 47 are idling. Accordingly, the first intermediate clutch 57 serves to disconnect the connection between the intermediate shaft 45 and the upstream inconstant speed first gear 48.

  The third gear 46 and the upstream inconstant speed third gear 121 are also provided with a second intermediate clutch 123 that can be engaged and separated. When the third gear 46 slides further leftward from the state shown in FIG. 8 once engaged with the sixth gear 54, the second intermediate clutch 123 is engaged with the intermediate shaft 45. In a state where the second intermediate clutch 123 is engaged, the power of the idle shaft 51 is transmitted to the output shaft 42 via the upstream inconstant speed fourth gear 122 and the upstream inconstant speed third gear 121. In this case as well, if the second intermediate clutch 123 is engaged, the third gear 46 and the fourth gear 47 idle. Accordingly, the second intermediate clutch 123 serves to disconnect the connection between the intermediate shaft 45 and the upstream inconstant speed third gear 121.

  When the fifth gear 52 slides, switching in two stages is performed, and when the intermediate shaft 45 slides, switching in four stages is performed. Therefore, there are eight combinations (speed switching) as a whole. For example, the number of shares per 3.3 square meters can be changed to 37 to 85 shares, which covers almost all areas of sparse and dense planting. FIG. 11 shows the relationship between the combination of gears and the number of planted stocks in the embodiment. In the case where the first gear 43 and the fifth gear 52 are engaged with each other, if the fourth gear 47 and the seventh gear 55 are engaged, the number of planted stocks is set to the constant strain d, and the third gear 46 and the sixth gear 52 are combined. If the gear 54 is meshed, the number of planted stocks is set to a constant-speed f strain. If the second intermediate clutch 123 is engaged, the number of planted stocks is set to b strains with unequal speed. When the second gear 44 and the fifth gear 52 are meshed with each other, if the fourth gear 47 and the seventh gear 55 are meshed, the number of planted strains is set to a constant c strain, and the third gear 46 and the sixth gear 52 are coupled. If the gear 54 is meshed, the number of planted stocks is set to a constant speed e strain. If the first intermediate clutch 57 is engaged, the number of planted strains is set to a strain having an unequal speed. In this case, the number of stocks indicated in alphabets has a large relationship in alphabetical order.

  Here, the upstream inconstant speed 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, and thereby the operation of the planting claw 96 in the transplanting mechanism 8. The fastest phase at which the speed is the fastest can be changed within the range before and after the bottom dead center. FIG. 12 shows, as an example, an operation locus of the planting claw 96 when 43 strains are set at unequal speed. The reference symbol MS1 in FIG. 12 indicates that the upstream inconstant speed third gear 121 and the upstream inconstant speed fourth gear 122 are set so that the operating speed of the planting claw 96 becomes the highest speed on the front side (upstream side) from the bottom dead center. MS2 is the highest speed phase when assembled, and MS2 is the upstream inconstant speed third gear 121 and the upstream inconstant speed fourth gear 122 so that the operating speed of the planting claw 96 becomes the fastest near the bottom dead center. Is the fastest phase when. The symbol MS3 is assembled with the upstream non-constant speed third gear 121 and the upstream non-constant speed fourth gear 122 so that the operation speed of the planting claw 96 is the highest after the bottom dead center (downstream side). Is the fastest phase.

  Depending on the relationship with the assembling accuracy, for example, the upstream inconstant speed third gear 121 and the upstream inconstant speed fourth gear 122 are assembled so that the front side (upstream side) from the bottom dead center is the highest 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 further, the rear side (downstream side) from the bottom dead center is the highest speed. It is possible to assemble the upstream inconstant speed third gear 121 and the upstream inconstant speed fourth gear 122 so as to be in the phase MS3. That is, for example, when the twist of the power transmission system is large due to the relationship with the assembling accuracy and the operation period of the planting claw 96 is concerned, 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 fastest phase around the bottom dead center. Then, the so-called “sucking” of the planting claw 96 can be suppressed or the vibration of the power transmission system can be suppressed. Needless to say, the upstream inconstant speed first gear 48 and the upstream inconstant speed second gear 56 may be assembled to the intermediate shaft 45 or the idle shaft 51 by adjusting the mounting phase.

  A fertilizer rotation shaft 58 extending in parallel with the input shaft 41 and the output shaft 42 is rotatably disposed on the upper portion of the inter-case case 40, and the fertilizer rotation shaft 58 is engaged with the first gear 43. A gear 59 is fitted so as to be relatively rotatable. Power is transmitted from the fertilizer rotating shaft 58 to the fertilizer driving shaft 62 via the bevel gear 61.

  As shown in FIG. 7 (A), the inter-stock transmission 26 has two operation shafts, a first operation shaft 63 and a second operation shaft 64. These operation shafts 63 and 64 have a longitudinal and longitudinal posture, and are exposed in front of the inter-case case 40. As can be understood from FIG. 6B, the first operation shaft 63 can be slid back and forth with the first lever 65, and the second operation 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). Next, the internal structure of the center case 30 (that is, the planting part transmission) will be described with reference to FIGS. The center case 30 is formed of a left and right split type 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 and right longitudinal intermediate shaft 70 is disposed 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, a lateral feed drive shaft 72 is disposed in a horizontally long posture, and the lateral feed shaft 33 is connected to the lateral feed drive shaft 72.

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

  The ratio of the number of teeth of the pair of the lateral feed amount adjusting gears 73 and 74 is different, 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 to the PTO shaft 29 is changed. . As a result, the lateral feed pitch of the seedling stage 7 changes and the amount of seedling scraping changes.

  The center case 30 has a projecting portion 30a extending rearward and downward, and a horizontally long planting output shaft 78 is rotatably held by the projecting portion 30a. The planting output shaft 78 includes an intermediate shaft 70. A first relay gear 79 fixed to the side, a second relay gear 80 fitted to the transverse feed drive shaft 72 so as to be relatively rotatable, a third relay gear 82 rotatably held on the center case 30 via an idle shaft 81, The 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. Accordingly, the rotational speed between the PTO shaft 29 and the planting output shaft 78 has a 1: 1 relationship. Since the third relay gear 82 is a simple idle gear, the number of teeth does not affect the rotational speed of the fourth relay gear 84.

  The planting output shaft 78 and the planting drive shaft 32 located adjacent thereto are connected by a coupling (sleeve) 86. A relay shaft 85 is disposed 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 for each transplantation mechanism 8, and adjacent planting drive shafts 32 are connected by a coupling 86. The planting output shaft 78, each planting drive shaft 32, and the relay shaft 85 can be formed as a single structure made of a single bar.

(4). Structure of Transplant Mechanism / Power Transmission Structure Next, the structure of the transplant mechanism 8 and the power transmission structure for the structure will be described. These form the main part of the embodiment, and are mainly displayed in FIGS. 8 to 10 (see also FIG. 6A). The planting transmission case 31 has a hollow structure, and as shown in FIG. 8, a longitudinally planting transmission shaft 87 is rotatably held therein.

  Power is transmitted to the planting transmission shaft 87 from the planting drive shaft 32 by the second bevel gear pair 88a, 88b. Of the second bevel gear pair 88 a and 88 b, the bevel gear 88 b 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. When a predetermined load or more is applied to the planting transmission shaft 87, the engagement is released and the power transmission is interrupted.

  On the rear side (front end 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 portion. 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 overlapped. The sun gear 92 described above is disposed in the longitudinal middle portion thereof, the intermediate gear 93 is disposed outside thereof, and the planetary gear is disposed outside thereof. A gear 94 is arranged. Each gear 92, 93, 94 is non-circular and eccentric. The planting claw member 37 is fixed to the unit shaft 95 fixed to the planetary gear 94.

  As clearly shown in FIG. 5, the planting claw member 37 is provided with a planting claw 96 and a protruding rod 97, and as shown in FIG. The seedlings are planted in the field by moving only to the field and projecting near the bottom dead center and the rod 97 moving forward relative to the planting claws 96.

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

  The downstream inconstant speed main drive 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 fixed to the planting transmission shaft 87 by welding and is not relatively rotatable. The downstream inconstant speed driven bevel gear 99 is fitted to the planting center shaft 91 so as to be capable of relative rotation, and has a cam portion 103 that meshes with the latching 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 in a relatively non-rotatable manner. The strut clutch 102 is normally pushed by the spring 106 so as to mesh with the downstream inconstant speed driven bevel gear 99. When the operating rod 129 is operated, the streak clutch 102 is separated from the downstream inconstant speed 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 operation at the shore, there are cases where it is not desired to operate a part of the four pairs of transplantation mechanisms 8, and in such a case, by operating the retaining clutch 102, The function can be stopped. In other words, the streaking function to reduce the number of planting streaks is exhibited.

(5). Downstream Inconstant Speed Member In the embodiment, the downstream inconstant speed bevel gear pair 98, 99 has a function of rotating (acceleration / deceleration) at inconstant speed (the downstream inconstant speed bevel gear pair 98, 99 is used as the downstream inconstant speed member. Is adopted). This point will be described mainly based on FIGS. 10 and 9C. As shown in FIG. 10 (E), when a large number of teeth 107 are formed on the downstream inconstant speed main driving bevel gear 98, the distance from the tip of each tooth 107 to the axis O1 is gradually increased and narrowed again. doing. That is, each tooth 107 has a pitch cone angle minimum portion 108 with the shortest distance from the axis O1 to the tip, and a pitch cone angle maximum portion 109 with the widest distance from the axis O1 to the tip. The distance between them 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 decentered with respect to a perfect circle (reference numeral 110 ′ indicates the pitch circle in the case of a true circle). ing). In other words, 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 inconstant speed main drive bevel gear 98 of the embodiment, As the outer peripheral surface of the spindle moves in the circumferential direction, the inclination angle θ1 (see FIGS. 10A and 10C) of the outer peripheral surface is gradually changed.

  The downstream inconstant speed driven bevel gear 99 has teeth 112 that are twice the number of teeth of the downstream inconstant speed driven bevel gear 98. And the position of the axial direction of each tooth | gear 112 has shifted | deviated little by little so that it can grasp | ascertain clearly from FIG. 10 (A) (B). In other words, also in the downstream inconstant speed driven bevel gear 99 of the embodiment, as in the downstream inconstant speed driven bevel gear 98, as the outer peripheral surface of the imaginary circular cylinder moves in the circumferential direction, the inclination angle θ2 of the outer peripheral surface (FIG. 10). (See (A)) is gradually changed.

  Since the downstream inconstant speed driven bevel gear 99 has twice the number of teeth of the downstream inconstant speed driven bevel gear 98, the downstream inconstant speed driven bevel gear 99 has two pitch cone angle maximum parts 113 and a minimum pitch cone angle minimum. Part 114. Therefore, as shown in FIG. 9 (C), the pitch circle 115 of the downstream inconstant speed 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 inconstant velocity bevel gear pair 98, 99 continuously changes the pitch cone angles θ1, θ2 along the rotation direction in a state where the cone distance γ (see FIG. 10C) is constant. It is. As can be seen from the above description, the downstream inconstant bevel gear pair 98, 99 as the downstream inconstant speed member is a single stage, and the upstream inconstant speed first to fourth gears 48, 56 as the upstream inconstant speed member. , 121, 122 are not changed (no speed switching).

  As described above, the pitch circles 110 and 115 of the downstream inconstant velocity bevel gears 98 and 99 are eccentric with respect to a perfect circle having a shape close to an ellipse and centering on the rotation axes O1 and O2, and the outer diameter shape thereof. By making each of the circles into perfect circles, the pair of downstream inconstant speed bevel gears 98, 99 can be formed in the same size as a normal bevel gear, and the assembly space for the pair of downstream inconstant speed bevel gears 98, 99 in the power transmission system Can be made smaller and more compact. In this case, the idea of manufacturing the downstream inconstant velocity bevel gears 98 and 99 is that the distorted cone shape formed with a constant cone distance is cut by a cylinder having the common rotation axes O1 and O2, and the outer diameter shape is true. It will be a circle.

  Here, the upstream inconstant speed bevel gear pair 98, 99 also adjusts the mounting phase in the same manner as the upstream inconstant speed first to fourth gears 48, 56, 121, 122, and the above-mentioned maximum speed phase is set to the bottom dead center. The setting can be changed in a direction further away from the position. FIG. 13 shows, as an example, a change in angular velocity of the planting claw 96 when 43 strains are set at unequal speed. The thick one-dot chain line in FIG. 13A is obtained by assembling the upstream inconstant speed third gear 121 and the upstream inconstant speed fourth gear 122 so that the front side (upstream side) from the bottom dead center is the fastest phase MS1. In this case, the downstream inconstant velocity bevel gear pair 98, 99 is further assembled so that the front side from the bottom dead center is the highest speed phase MS1 '(see FIG. 12). A 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 set so that the vicinity of the bottom dead center is the fastest phase MS2. This is a case where 98 and 99 are assembled. The thick two-dot chain line in FIG. 13C assembles the upstream inconstant speed third gear 121 and the upstream inconstant speed fourth gear 122 so that the rear side (downstream side) from the bottom dead center is the highest speed phase MS3. In addition, the downstream inconstant velocity bevel gear pair 98, 99 is further assembled so that the rearmost side from the bottom dead center is the highest speed phase MS3 ′ (see FIG. 12). When configured in this manner, the operation 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. 5C shows the relationship between the number of planted stocks per 3.3 square meters and the movement trajectory of the planting claws 96. As can be seen from this figure, even when the planting claw 96 rises directly above the bottom dead center when densely planted, the planting claw 96 escapes poorly at the time of sparse planting, causing a phenomenon that the seedling is moved forward. Understandable.

  And in embodiment, the upstream inconstant speed 1st-4th gear 48,56,121,122 was provided in the inter-strain transmission 26, and the downstream inconstant speed bevel gear pair 98,99 was provided in the seedling planting apparatus 2. By providing, the planting claw member 37 is accelerated and rotated so that the operation speed is increased in the vicinity where the planting claw 96 is located at the bottom dead center. For this reason, 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 moving the seedling forward.

  In the embodiment, since the inconstant speed member is separated and arranged in the inter-strain transmission device 26 and the seedling planting device 2, the distance from the inter-strain transmission device 26 to the downstream inconstant speed bevel gear pair 98, 99 is compared with the conventional one. The ratio of non-uniform rotation is small. As a result, torsion occurring 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 transplanting mechanism 8 can be ensured. Moreover, since the play which generate | occur | produces in a power transmission system can also be suppressed, the malfunction that the timing of unequal speed shifts | deviates and the planting posture of a seedling is disturbed can also be prevented.

  Now, since the transplanting mechanism 8 has a configuration 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 generates a large inertia force. In addition, a large load is generated when the seedling is scraped, and a negative load is generated thereafter. That is, due to the swinging 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 transplant mechanism 8. Such torque fluctuations appear remarkably when the resonance rotational speed is exceeded even when rotating at a constant speed during dense planting (because the transplanting mechanism 8 rotates at a higher speed during dense planting than during loose 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 has shifted to scraping of the seedlings. It can be said that the planting claw member 37 acts to cancel each other's load fluctuations. However, since a large torque is required for scraping off the seedlings, the function of leveling the torque fluctuation is weak only by the movement of the two planting claw members 37. For this reason, the transplanting mechanism 8 does not rotate smoothly, and a phenomenon called “sucking” easily occurs.

  On the other hand, when the transplant mechanism 8 is slightly rotated at a non-uniform speed by the downstream inconstant speed bevel gear pair 98, 99 even in the dense planting state as in the embodiment, the seedling scraping by the planting claw member 37 causes the inertial force. In addition, since the transplantation mechanism 8 is decelerated after the seedling is scraped off, it is possible to suppress a large inertial force from acting on the transplantation mechanism 8. For this reason, load fluctuations (or torque fluctuations) acting on the transplantation mechanism 8 can be leveled to ensure smooth rotation.

(7). First Example of Antiphase Torque Generating Member Next, a first example of the antiphase torque generating member 130 will be described with reference to FIGS. 8 and 14 to 18. In the rice transplanter of the embodiment, the rotational torque T of the transplanting mechanism 8 based on the unequal speed rotational power of the upstream unequal speed and downstream unequal speed bevel gear pairs 98 and 99 is opposite to the rotational torque T. An anti-phase torque generating member 130 for adding the phase torque Tan is provided. In the first embodiment, the antiphase torque generating member 130 is provided in each of a plurality of (four) planting transmission cases 31. Since the planting transmission case 31 is provided with each planting transmission case 31, the antiphase torque generating member 130 exists for each of a total of four combinations of the planting transmission case 31 and the planting clutch 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 planting transmission case 31. The end case 131 may be a separate structure that is detachably attached to the rear end side of the planting transmission case 31. The planting transmission case 31 and the end case 131 communicate with each other. A planting branch shaft 132 having a longitudinal length is rotatably supported through a bearing at a communicating portion between the planting transmission case 31 and the end case 131. A leveling bevel gear 133 that always meshes with the downstream inconstant 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 speed main drive bevel gear 98 are in a positional relationship facing (opposing) before and after sandwiching the planting center shaft 91.

  The leveling bevel gear 133 is formed in the same shape as the downstream inconstant speed main drive bevel gear 98. That is, the leveling bevel gear 133 has the same number of teeth as that of the downstream inconstant speed main driving bevel gear 98 and the pitch cone angle in the rotational direction with a constant cone distance in the same manner as the downstream inconstant speed main driving bevel gear 98. It is formed in a shape that is continuously changed along. Accordingly, the leveling bevel gear 133 and the planting branch shaft 132 rotate in the reverse direction at the same speed as the downstream inconstant speed main driving bevel gear 98 (revolving at twice the speed of the downstream inconstant speed driven bevel gear 99). .

  The rear end side of the planting branch shaft 132 protrudes in the middle in the vertical direction in the end case 131. An eccentric shaft 134 extending in parallel with the planting branch shaft 132 is fixed to the projecting portion on the rear end side. The axis of the eccentric shaft 134 is eccentric with respect to the rotation center of the planting branch shaft 132. For this reason, the planting branch shaft 132 and the eccentric shaft 134 are in the form of a crankshaft (the function of the crankshaft is exhibited). A locking pin 135 is attached to the lower side in the end case 131. A tension spring 136 as a means for generating an antiphase torque is mounted on the eccentric shaft 134 and the locking pin 135. The tension spring 136 is always biased in the direction in which the eccentric shaft 134 is moved to the lower side of the planting branch shaft 132. When the eccentric shaft 134 passes just above the planting branch shaft 132, the tension spring 136 is set so as to exceed the fulcrum. In the first embodiment, the planting branch shaft 132, the eccentric shaft 134, and the tension spring 136 constitute the antiphase torque generating member 130.

  A drive spur gear 137 is fixed to the rear end side protruding portion of the planting branch shaft 132. A power take-out shaft 138 extending in parallel with the planting 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-out shaft 138. The drive spur gear 137 and the driven spur gear 139 are always meshed. The rear end side of the power take-out shaft 138 protrudes rearward from the rear surface of the end case 131. The rotational power of the planting transmission shaft 87 is transmitted to the power take-out shaft 138 through the downstream inconstant velocity bevel gear pair 98, 99, the leveling bevel gear 133, the planting branch shaft 132, the driving flat gear 137, and the driven flat gear 139. Is done. When an optional device such as a medicine spreader is mounted on the seedling planting device 2, the rotational power of the power take-out 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 transplanting mechanism 8, the antiphase torque Tan, and the combined torque Tco obtained by combining these torques. 18 represents the rotational torque T (variation torque) of the planting center shaft 91, and the rotational torque T is near the bottom dead center where the planting claws 96 of the planting claw member 37 plant the seedlings. Become the largest. 18 represents the reverse phase torque Tan generated by the antiphase torque generating member 130 (the planting branch shaft 132, the eccentric shaft 134, and the tension spring 136). In the vicinity of the bottom dead center 96 where seedlings are planted, the antiphase torque Tan is 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 through the downstream inconstant speed driven bevel gear 99. As a result, as shown 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 transplantation mechanism 8. That is, the rotational torque T leveled (cancelled) by the synthesis of the antiphase torque Tan is transmitted to the transplantation mechanism 8. For this reason, load variation (which may be referred to as torque variation) acting on the transplantation mechanism 8 is leveled, and smooth rotation of the transplantation mechanism 8 can be ensured. Therefore, it is possible to plant seedlings in an appropriate planting posture while suppressing the occurrence of a phenomenon called “shakuri”.

  As is apparent from the above description and FIGS. 8 and 14 to 18, the transmission case 11 that shifts the power of the engine 10 mounted on the traveling machine body 1 and the planting claw 96 that draws a non-circular movement locus are provided. A seedling planting apparatus 2 having a transplanting mechanism 8, an 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 body 1 to change the strain, and the transplanting mechanism 8 at an inconstant speed. In the rice transplanter including the inconstant speed members 98 and 99 for transmitting the rotational power, the rotational torque T is in a phase opposite to the rotational torque T of the transplanting mechanism 8 based on the inconstant speed rotational power. The anti-phase torque generating member 130 for adding the anti-phase torque Tan to be further provided, so that the anti-phase torque Tan from the anti-phase torque generating member 130 is transferred by the inconstant speed rotational power. Will be to offset the rotation torque T, the load fluctuation acting on the implant mechanism 8 (which may be referred to as a torque variation) and leveling, smooth rotation of the implant mechanism 8 is secured. Therefore, it is possible to plant seedlings in an appropriate planting posture while suppressing the occurrence of a phenomenon called “shakuri”.

  In particular, the power transmission system from the inter-strain transmission 26 to the transplanting 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. The bevel gear pair is configured as an inconstant speed gear pair 98, 99 as the inconstant speed member, and the antiphase torque generating member 130 is added to the inconstant speed gear 99 on the downstream side of the inconstant speed gear pair 98, 99. Since these are connected, the existing member of the inconstant speed gear pair 98, 99 can be utilized, which is advantageous in terms of cost.

(8). Second and Third Embodiments of Antiphase Torque Generating Member Next, a second embodiment of the antiphase torque generating member 130 will be described with reference to FIG. In the second embodiment, the end case 131 is eliminated from the rear end side of the planting transmission case 31 and the antiphase torque generating member 130 is disposed on the rear side of the planting transmission case 31. This is different from the example.

  In this case, external teeth 141 are formed on the outer peripheral side of the operation ring 105 of the hooking clutch 102. The outer teeth 142 of the operation ring 105 mesh with a leveling flat gear 143 that is rotatably supported on the rear side in the planting transmission case 31. The rotation center shaft 144 of the leveling flat gear 143 extends in parallel with the planting center shaft 91. A locking pin 145 is provided upright on one side of the leveling flat gear 143.

  A tension spring 146 as a means for generating a reverse phase torque is mounted on the locking pin 145 and the inner peripheral wall of the planting transmission case 31. The tension spring 146 always urges the locking pin 145 in a direction away from the operation ring 105. The tension spring 146 expands and contracts by the rotation of the leveling flat gear 143. The leveling flat gear 143 and the tension spring 146 have a kind of crank structure. In the second embodiment, the operation ring 105, the leveling flat gear 143, the locking pin 145, and the tension spring 146 constitute the antiphase torque generating member 130. That is, the anti-phase torque generating member 130 is positioned in the planting transmission case 31 on the downstream side of the line stopping clutch 102. In the second embodiment, as in the case of the first embodiment, there are anti-phase torque generating members 130 for each combination of a total of four sets of the planting transmission case 31 and the hooking clutch 102.

  When configured as described above, the elastic restoring force of the tension spring 146 is transmitted from the leveling flat gear 143 to the planting center shaft 91 through 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 antiphase torque Tan are combined, and the combined torque Tco is transmitted to the transplantation mechanism 8 to transfer the transplantation mechanism. 8 smooth rotations can be secured. Therefore, as in the case of the first embodiment, it is possible to plant seedlings in an appropriate planting posture while suppressing the occurrence of a phenomenon called “shackle”.

  Further, since the reverse phase torque generating member 130 is disposed in the planting transmission case 31 on the downstream side of the strut clutch 102, the reverse phase torque generating member 130 is located in the vicinity of the transplant mechanism 8 that is the source of the load fluctuation. Will be located. For this reason, the effect of offsetting the rotational torque T of the transplanting mechanism 8 with the antiphase torque Tan, that is, the effect of leveling the load fluctuation is high. Moreover, since the antiphase torque Tan is not generated when the strut clutch 102 is in the power cut-off state, there is no possibility that unnecessary torque is propagated around the transplant mechanism 8.

  FIG. 20 shows a third embodiment of the antiphase 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 disposed on the rear side in the planting transmission case 31 and on the downstream side of the anchoring clutch 102. The second embodiment is different from the second embodiment in that an anti-phase torque generating member 130 is provided independently of the hooking clutch 102.

  In this case, the leveling first flat gear 152 is fixed to the planting center shaft 91 on the opposite side of the streak clutch 102 with the downstream inconstant speed driven bevel gear 99 interposed therebetween. The leveling first spur gear 152 meshes with a 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 flat gear 153 extends in parallel with the planting center shaft 91. A locking pin 155 is provided upright on one side of the leveling second flat gear 153.

  A tension spring 156 is mounted on the locking pin 155 and the inner peripheral wall of the planting transmission case 31 as a means for generating a reverse phase torque. The tension spring 156 always urges the locking pin 155 in a direction away from the leveling first spur gear 152. The tension spring 156 expands and contracts by the rotation of the leveling second flat gear 153. The leveling second flat gear 153 and the tension spring 156 have a kind of crank structure. In the third embodiment, the leveling first and second flat gears 152 and 153, the locking pin 155 and the tension spring 156 constitute the antiphase torque generating member 130. In the third embodiment as well, there are anti-phase torque generating members 130 for each combination of a total of four sets of planting transmission cases 31 and streak clutches 102. Also when comprised as mentioned above, there exists an effect similar to 2nd Example.

  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 machine body 1, and the transplantation with the planting claws 96 that draw a non-circular motion locus A seedling planting device 2 having a mechanism 8, a strain transmission device 26 that changes the operating speed of the transplanting mechanism 8 with respect to the traveling speed of the traveling machine body 1 to change the strain, and the transplanting mechanism 8 with inconstant rotational power. In the rice transplanter provided with the inconstant speed members 98 and 99 for transmitting the rotation torque T, the rotational torque T of the transplantation mechanism 8 based on the inconstant speed 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 is used as the transplanting mechanism 8 by the inconstant speed rotational power. Will be to offset the rotation torque T, the load fluctuation acting on the implant mechanism 8 (which may be referred to as a torque variation) and leveling, smooth rotation of the implant mechanism 8 is secured. Therefore, it is possible to plant seedlings in an appropriate planting posture while suppressing the occurrence of a phenomenon called “shakuri”.

  Further, when the streak clutch 102 is in a power cut-off state, the antiphase torque Tan is not generated, and there is no possibility that unnecessary torque is propagated around the transplant mechanism 8. In addition, the planting transmission case 31 is provided in the planting transmission case 31 having a longitudinal longitudinal direction in the seedling planting device 2 to interrupt power transmission from the inter-strain transmission 26 to the transplanting mechanism 8. 31, the reverse phase torque generating member 130 is disposed downstream of the streak clutch 102, so that the reverse phase torque generating member 130 is positioned in the vicinity of the transplantation mechanism 8 that is the source of load fluctuation. Therefore, the effect of canceling the rotational torque T of the transplantation mechanism 8 with the antiphase torque Tan, that is, the effect of leveling the load fluctuation is high.

(9). Fourth to Ninth Embodiments of Antiphase Torque Generating Member Next, a fourth embodiment of the antiphase torque generating member 130 will be described with reference to FIGS. 21 and 22. In the fourth embodiment, the antiphase torque generating member 130 is applied to a structure in which the rotation of the planting drive shaft 32 is transmitted to the planting central shaft 91 by the chain 163. In this case, the driving 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. Within the planting transmission case 31, a power transmission chain 163 is wound around the main sprocket 161 and the driven sprocket 162. A torque limiter 164 is slidably fitted on the planting drive shaft 32 so as not to be relatively rotatable. When a load exceeding a predetermined value 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 interrupted. The planting center shaft 91 is fitted with a slidable clutch 102 for interrupting power transmission from the driven sprocket 162 to the planting center shaft 91 so as to be slidable and relatively non-rotatable. As shown in FIG. 22, the main sprocket 161 and the driven sprocket 162 are configured as inconstant speed sprockets having an elliptical shape (non-circular shape). An idle roller 163 ′ is brought into contact with the chain 163. With such a configuration, the planting center shaft 91 is imparted with nonuniform rotation. In the fourth embodiment, the reduction ratio in the chain 163 transmission is ½ on average.

  A power take-off shaft 165 extending in parallel with the planting center shaft 91 is rotatably supported on the rear 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 protruded from the planting transmission case 31 to the left and right outwards. The leveling main drive sprocket 166 is fixed on the opposite side of the anchoring clutch 102 across the driven sprocket 162 in the planting center shaft 91, while the leveling driven sprocket 167 is fixed to the power take-out shaft 165. ing. A power transmission chain 168 is wound around the leveling main drive sprocket 166 and the leveling driven sprocket 167. Via the sprocket and chain transmission systems 166 to 168, the rotational power of the planting center shaft 91 is branched and transmitted to the power take-out shaft 165. When an optional device such as a medicine spreader is attached to the seedling planting device 2, the rotational power of the power take-out shaft 165 is transmitted to the optional device.

  The other end side of the power take-out shaft 165 is bent into a crank shape. A tension spring 169 as a means for generating a reverse phase torque is mounted on the crank front end side of the power take-off shaft 165 and the inner peripheral wall of the planting transmission case 31. The tension spring 169 always urges the crank end of the power take-off shaft 165 to move below the rotation center of the power take-out shaft 165. The tension spring 169 expands and contracts by the rotation of the power take-out shaft 165 via the leveled driven sprocket 167. In the fourth embodiment, the power take-off shaft 165, the leveling main and driven sprockets 166 and 167, the chain 168, and the tension spring 169 constitute the antiphase torque generating member 130. That is, the power take-out shaft 165 is one of the components of the antiphase torque generating member 130. In the fourth embodiment as well, there are anti-phase torque generating members 130 for each combination of the four sets of planting transmission cases 31 and the hooking clutch 102. Also when comprised as mentioned above, there exists an effect similar to the 2nd and 3rd Example.

  As in the fourth embodiment, 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 antiphase torque generating member. 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 circular but eccentric constant speed sprockets. A main driving gear 171 is fixed to the idle shaft 170, and a driven gear 172 is fixed to the planting center shaft 91. By engaging the main driving gear 171 and the driven gear 172, the planting center shaft 91 is imparted with non-uniform speed rotation. The average reduction ratio in the chain 163 transmission is 1, but the reduction ratio in the gear transmission from the main driving gear 171 to the driven gear 172 is ½. An idle roller 163 ′ is brought into contact with the chain 163. A configuration may be adopted in which only one of the sprockets 161 and 162 is decentered and one is not decentered.

  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 configured as a circular constant velocity sprocket. In the seventh embodiment shown in FIG. 25, the main driving sprocket 161 provided on the planting drive shaft 32 is configured as a circular but eccentric constant speed sprocket. In the sixth and seventh embodiments, the reduction ratio in the chain 163 transmission is ½ 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 speed sprocket, and the driven sprocket 162 provided on the planting central shaft 91 is formed as a circular constant speed. Sprocket. In this case, the reduction ratio in the chain 163 transmission is also ½ 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 inconstant sprocket having an elliptical shape (non-circular), and the driven sprocket 162 provided on the planting central shaft 91 is provided. A non-uniform sprocket having a polygonal shape (non-circular shape) is formed. In this case, the reduction ratio in the chain 163 transmission is also ½ on average. Since the driven sprocket 162 is formed in a substantially square shape, four times of acceleration / deceleration occurs in one rotation of the planting center shaft 91.

  As is clear from the above embodiment and FIGS. 21 to 27, a transmission case 11 for shifting the power of the engine 10 mounted on the traveling machine body 1 and a transplant with a planting claw 96 that draws a non-circular motion trajectory. A seedling planting device 2 having a mechanism 8, a strain transmission device 26 that changes the operating speed of the transplanting mechanism 8 with respect to the traveling speed of the traveling machine body 1 to change the strain, and the transplanting mechanism 8 with inconstant rotational power. In the rice transplanter including the inconstant speed members 161 and 162 for transmitting the rotation torque T, the rotational torque T of the transplanting mechanism 8 based on the inconstant speed rotational power is opposite to the rotational torque T. An anti-phase torque generating member 130 for adding a phase torque Tan is further provided, and power is transmitted to an optional device mounted on the seedling planting device 2 in the longitudinal transmission planting case 31 of the seedling planting device 2. Since a possible power take-off shaft 165 is provided and the power take-out shaft 165 is a constituent element of the anti-phase torque generating member 130, load variation (torque variation) acting on the transplantation mechanism 8 is leveled and the transplantation is performed. While ensuring smooth rotation of the mechanism 8, the power take-off shaft 165 can be effectively used as the reverse phase torque generating member 130, and the power transmission structure to the seedling planting device 2 can be simplified. Can contribute to weight reduction.

(10). Others The present invention can be embodied in various ways other than the above embodiment. For example, the inter-stock transmission 26 can be built in the mission case 11, and in this case, one upstream inconstant speed member is built in the mission case 11. When providing an inconstant speed member in each of the traveling body 1 and the seedling planting device 2, the acceleration / deceleration ratio (the inconstant speed ratio) may be set as necessary. Therefore, in some cases, the acceleration / deceleration ratio (unequal speed ratio) on the traveling machine body 1 side can be made smaller than the inconstant speed conversion ratio in the seedling planting device 2. Instead of chain transmission, belt transmission (timing belt is preferred) may be adopted. In any of the first to ninth embodiments, the crank structure portion and the tension spring of the antiphase torque generating member 130 can be arranged outside the planting transmission case 31.

DESCRIPTION OF SYMBOLS 1 Traveling machine body 2 Seedling planting device 8 Transplanting mechanism 10 Engine 11 Transmission case 26 Stock transmission device 36 Rotary case 37 Planting claw member 40 Stocking 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 Thread 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 Leveling first flat gear 153 Leveling second flat gear 161 Main drive sprocket 162 Driven sprocket 163, 168 Chain 164 Torque limiter 165 Power take-off shaft 166 Leveling Main drive sprocket 167 leveling follower Sprockets 169 tension spring

Claims (2)

A transmission case for shifting the power of an engine mounted on a traveling machine body, a seedling planting device having a transplanting mechanism with a planting claw for drawing a non-circular movement locus, and an operating speed of the transplanting mechanism with respect to a traveling speed of the traveling machine body In a rice transplanter equipped with an inter-variety transmission for shifting the stock and changing the stock, and an inconstant speed member for transmitting inconstant speed rotational power to the transplanting mechanism,
An anti-phase torque generating member for adding anti-phase torque that is in reverse phase to the rotational torque with respect to the rotational torque of the transplant mechanism based on the inconstant speed rotational power;
In the seedling planting device, in the longitudinal longitudinal planting transmission case, there is provided a strut clutch that cuts off power transmission from the inter-strain transmission to the transplant mechanism, and in the planting transmission case, from the strut clutch Also arranges the anti-phase torque generating member on the downstream side,
Rice transplanter. A plurality of combinations of the planting transmission case and the hooking clutch are provided, and the antiphase torque generating member is provided for each combination.
The rice transplanter according to claim 1.

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