JP2014171460A - Transplanter - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a transplanter which can stably switch a uniform velocity passage and a non-uniform velocity passage without complicating a structure, in a transplanter which switches the uniform velocity passage for transmitting uniform velocity rotation power to a planting working machine side and the non-uniform velocity passage for transmitting non-uniform velocity rotation power to the planting working machine side.SOLUTION: A switching mechanism 48 switches a transmission passage to a uniform velocity passage side by a slide of a shit member 63 to one side of a switching shaft 47, and on the other hand, switches the transmission passage to a non-uniform velocity passage side by a slide of the shift member 63 to the other side of the switching shaft 47. The switching mechanism comprises a working mechanism 83 which slide-moves the shift member 63 to both directions of the switching shaft 47, and also comprises, at the working mechanism 83, an elastic member 94 which straddles a pivot when the shift member 63 is slid, and in which the energization direction to the shift member 63 is inverted.

Description

  The present invention relates to a transplanter for switching between a constant speed path for transmitting constant speed rotational power to the planting work machine side and an inconstant speed path for transmitting non-constant speed rotational power to the planting work machine side.

  A switching mechanism for switching the power transmission path to the planting work machine, and the switching mechanism transmits a constant speed rotational power to the planting work machine by sliding on the switching shaft of the shift member. And an inconstant speed path for transmitting inconstant speed rotational power to the planting work machine side, and the switching mechanism is configured to perform the shift in the constant speed direction on one side of the switching shaft. It is connected and operated by a constant speed clutch that switches the transmission path to the constant speed path side by being connected and operated by sliding of the member, and sliding of the shift member in the non-constant speed direction that is the other side of the switching shaft. Therefore, a transplanter having an inconstant speed clutch for switching the transmission path to the inconstant speed path side is known (see, in particular, Patent Document 1).

Japanese Patent No. 3776044 (FIG. 8)

  However, since the transplanter of the above document stably switches between the constant speed path and the inconstant speed path, the shift member is connected to the slide position where the constant speed clutch is connected and the inconstant speed clutch is connected. This requires a mechanism for positioning each slide position, and the structure is complicated.

  The present invention relates to a transplanter that performs switching between a constant speed path for transmitting constant speed rotational power to the planting work machine side and an inconstant speed path for transmitting non-constant speed rotational power to the planting work machine side. It is an object of the present invention to provide a transplanter capable of stably switching between a constant speed path and an inconstant speed path without complicating the speed.

  In order to solve the above-mentioned problem, a switching mechanism 48 for switching the power transmission path to the planting work machine 6 is provided, and the switching mechanism 48 is slid on the switching shaft 47 of the shift member 63 to thereby plant the planting work machine. In the transplanter for switching between a constant speed path for transmitting the constant speed rotational power to the 6 side and an inconstant speed path for transmitting the inconstant speed rotational power to the planting work machine 6 side, the switching mechanism 48 includes the switching mechanism 48 described above. A mesh-type constant speed clutch 82 that performs transmission path switching to the constant speed path side by being connected and operated by sliding of the shift member 63 in a constant speed direction on one side of the switching shaft 47, and the switching shaft 47 A mesh-type inconstant speed clutch 79 that is connected and operated by sliding the shift member 63 in the inconstant speed direction, which is the other side of the gear, and performs transmission path switching to the inconstant speed path side. Constant speed clutch 82 and non-constant speed clutch 9 is provided with an actuating mechanism 83 that slides the shift member 63 in the direction of the switching shaft 47 within a switching range between the fulcrum 9 and the urging direction beyond the fulcrum when the shift member 63 is slid in the middle of the switching range. The elastic member 94 to be reversed is provided in the operating mechanism 83, and the elastic member 94 urges the shift member 63 in the constant speed direction on the constant speed clutch 82 side, while the unequal speed clutch 79 side has an unequal speed. It is characterized by a structure that biases in the direction.

  A meshing type planting clutch 39 for intermittently transmitting power to the planting PTO shaft 33 that outputs power to the planting work machine 6 side is provided on the upstream side of transmission from the switching mechanism 48. In the rotation range of the planting PTO shaft 33 in a state where the planting claw 18 is not positioned at a predetermined position, a cutting regulation means 43 for regulating cutting operation by releasing the meshing of the planting clutch 39 is provided, etc. A connection restricting means for restricting the connection operation of the speed clutch 81 or the inconstant speed clutch 79 may be provided in the switching mechanism 48.

  With the elastic member exceeding the fulcrum, the meshing constant speed clutch is reliably meshed when sliding in the constant speed direction and is stably connected, and the meshing type constant speed clutch is operated when sliding in the non-constant speed direction. Since the inconstant speed clutch reliably engages and is stably connected, it is possible to smoothly switch between the constant speed path and the inconstant speed path, and a single elastic member that exceeds the fulcrum. Thus, the shift member can be biased in both the constant speed direction and the non-constant speed direction, so that the structure is simplified and the cost can be kept low.

  A meshing type planting clutch for intermittently transmitting power to the planting PTO shaft that outputs power to the planting machine side is provided upstream of the switching mechanism, and the planting claws of the planting machine are installed in advance. In a rotation range of the planting PTO shaft in a state where the planting PTO shaft is not positioned at a predetermined position, a cutting regulation means for regulating cutting operation by releasing the meshing of the planting clutch is provided, and the constant speed clutch or the non-constant speed clutch is connected. According to the switching mechanism provided with the connection regulating means for regulating the operation, even when the switching mechanism is provided, the planting claw can be prevented from being stopped in a state where the planting claw is not switched to the predetermined posture. In addition, when the restriction by the connection restricting means is released, the connection operation of the constant speed clutch or the inconstant speed clutch is smoothly executed by the elastic member.

It is a side view of the riding transplanter to which the present invention is applied. It is a side view which shows the movement locus | trajectory of the planting claw in the middle of planting work. It is a plane sectional view showing the power transmission structure of this riding transplanter. It is a side view which shows the power transmission structure of this riding transplanter. It is a plane sectional view which shows the structure which transmits motive power to a planting work machine. It is a front sectional view of a change case showing the composition of a change mechanism. (A) is sectional drawing of the switching case which shows the state which switched to the 1st path | route, (B) is sectional drawing of the switching case which shows the state which switched to the 2nd path | route. It is a side view which shows the structure of an action | operation mechanism. It is a side view which shows the movement locus | trajectory of the planting nail in the middle of making the traveling body drive forward and performing the planting work. (A), (B) is the front sectional view and plane sectional view of a switching case which show the composition of another embodiment of a switching mechanism, respectively.

  FIG. 1 is a side view of a riding transplanter to which the present invention is applied. The riding transplanter includes a traveling machine body 3 supported by a pair of left and right front and rear wheels 1 and 2, and a planting work machine 6 connected to a rear end portion of the traveling machine body 3 via a lifting link 4 so as to be driven up and down. It has.

  A bonnet 7 covering the engine is supported at the front portion of the traveling machine body 3 so as to be openable and closable. A rear side of the bonnet 7 in the traveling machine body 3 is provided with a cockpit 8 on which an operator gets. A seat 9 on which an operator is seated is disposed in the cockpit 8. A steering handle 11 is supported in front of the seat 9 so that a steering operation can be performed. A lever 12 is supported so that the lever can be operated, and a floor surface 8 a of the cockpit seat 8 is formed at a low position between the steering handle 11 and the seat 9.

  The planting work machine 6 includes a seedling mounting table 13 having a seedling mounting surface 13a formed on the back side thereof and a planting unit 14 disposed immediately below the seedling mounting table 13 with a steep upward inclination toward the front. Have. The planting part 14 extends in the front-rear direction and can be driven to rotate around a planter case 16 supported and fixed on the frame part 6 a side of the planting work machine 6 and a horizontal axis located at the rear end part of the planter case 16. And a planting claw 18 supported on both ends of the rotary case 17.

  FIG. 2 is a side view showing the movement locus of the planting claw during the planting operation. As the rotary case 17 rotates, the tip side of the planting claw 18 scrapes off the seedling Y on the seedling placing surface 13a of the seedling placing stand 13 while drawing an annular movement trajectory X to plant it in the field. The movement trajectory X has a long ring shape in the vertical direction, and the front trajectory (front trajectory) X1 in the movement trajectory X is an arc-shaped trajectory that rises in a mountain shape on the front side. The rear trajectory (rear trajectory) X2 in FIG. 2 is a trajectory extending vertically in the vertical direction.

  The posture of the planting claw 18 whose tip side is located immediately below the planter case 16 in the movement trajectory X is a planting posture in which the seedling Y is planted in the farm field. On the other hand, the posture of the planting claw 18 whose tip side is located on the planter case 16 side in the movement locus X is a retracted posture in which the planting claw 18 is stored on the side of the planter case 16.

  Then, the seedling Y is scraped off from the seedling stage 13 in the middle of switching from the retracted position to the planting position in the planting claw 18, and the seedling is seeded at a timing when the planting claw 18 is switched to the planting position. Y is planted in the field.

  The riding transplanter configured as described above transplants the seedling Y from the seedling stage 13 onto the field by moving the traveling body 3 forward while being driven to be planted while the planting work machine 6 is lowered. .

  FIG. 3 is a cross-sectional plan view showing the power transmission structure of the present transplanter. The engine power is transmitted to the transmission 21 in the transmission case 21a via the traveling HST 19 that is a hydraulic stepless transmission. The power transmitted to the transmission 21 is transmitted to the differential mechanism 23 through the traveling transmission mechanism 22 that is shifted by switching the meshing gears. The power transmitted to the differential mechanism 23 is distributed to the left and right and input to the left and right front axle cases 24, respectively, to drive the left and right front wheels 1 to rotate.

  In addition to the differential mechanism 23 described above, the power shifted by the traveling transmission mechanism 22 is also distributed and transmitted to the propeller shaft 26 in the front-rear direction that protrudes rearward from the mission case 21a. The power of the propeller shaft 26 is input into a left and right rear axle case 27 into which the rear end portion of the propeller shaft 26 is inserted, and drives the left and right rear wheels 2 to travel.

  Further, the power input to the mission case 21 a is shifted by the planting transmission mechanism 28 and then transmitted to the planting transmission shaft 29. A planting transmission gear 32 is provided in the middle of the planting transmission shaft 29. The power input to the planting transmission shaft 29 is transmitted to the planting transmission gear 32 via the torque limiter 31 on the planting transmission shaft 29. By this power transmission, the planting transmission gear 32 is rotationally driven around the planting transmission shaft 29.

  On the other hand, the planting PTO shaft 33 in the front-rear direction extending in the direction orthogonal to the planting transmission shaft 29 is supported by the transmission case 21a via a bearing 34 so as to be rotatable about its own axis. One end of the planted PTO shaft 33 protrudes rearward from the mission case 21a, and the other end of the PTO output gear 36 that always meshes with the planted transmission gear 32 is relatively rotatable (freely rotatable). It is supported.

  Between the PTO output gear 36 and the bearing 34 in the planting PTO shaft 33, an intermittent sleeve 37 supported so as to be slidable in the axial direction of the planting PTO shaft 33 is externally provided. The intermittent sleeve 37 is externally mounted so as to rotate synchronously (specifically, integrally rotate) with the planted PTO shaft 33, and the intermittent sleeve 37 is provided at the end of the outer peripheral surface of the intermittent sleeve 37 on the PTO output gear 36 side. A flange-like contact portion 38 that rotates integrally with 37 is extended, and a planting clutch 39 is provided between the intermittent sleeve 37 and the PTO output gear 36 so that the claws are engaged with each other. Yes.

  When the intermittent sleeve 37 is slid to the PTO output gear 36 side, the claws are engaged with each other and the planting clutch 39 is connected, and the planting PTO shaft 33 rotates integrally with the PTO output gear 36 (that is, planting). The power of the transmission shaft 29 is transmitted to the planting PTO shaft 33). On the other hand, when the intermittent sleeve 37 is slid to the side away from the PTO output gear 36, the meshing of the claws is released, the planting clutch 39 is disconnected, and the planting transmission shaft 29 to the planting PTO shaft 33. The power transmission of is cut off.

  Incidentally, the intermittent sleeve 38 is always urged toward the side to which the planting clutch 39 is connected by an elastic member 41 such as a compression spring that is externally mounted on the intermittent sleeve 38.

  Further, when the intermittent sleeve 37 is slid toward the side away from the PTO output gear 36 against the urging force of the elastic member 41, a regulating member 42 protruding from the inner wall of the mission case 21a toward the planting PTO shaft 33, The contact with the contact portion 38 restricts the cutting operation of the intermittent sleeve 37. A predetermined range around the axis of the planting PTO shaft 33 in the contact portion 38 is formed in a notch-shaped portion 38a, and planting is performed only when the notch-shaped portion 38a is located on the regulating member 42 side. Cutting operation of the PTO shaft 33 is allowed.

  That is, the contact portion 38 and the regulating member 42 permit the cutting operation of the planting clutch 39 only when the planting PTO shaft 33 is rotated to a predetermined position (allowable range), and the planting PTO shaft. When 33 is rotated to a position (restriction range) other than the allowable range, a cutting restriction means 43 that restricts the cutting operation of the planting clutch 39 is configured.

  The restriction range is appropriately set so that the planting clutch 39 is not disconnected while the planting claws 18 are in the planting posture. The cutting restricting means 43 can reliably prevent the planting claw 18 from being damaged due to the vehicle body traveling while the planting claw 18 is stopped in the planting posture and the planting claw 18 being dragged in the field. .

  FIG. 4 is a side view showing a power transmission structure of the present riding transplanter, and FIG. 5 is a plan sectional view showing a structure for transmitting power to the planting machine. The power from the planted PTO shaft 33 is fed back and forth in the forward and backward direction through the switching case 46 disposed behind the transmission case 21a and diagonally above the rear axle case 27 via the longitudinal transmission shaft 44. It is transmitted to the shaft (input shaft) 47.

  The power transmitted to the switching input shaft 47 is input to a switching mechanism 48 in the switching case 46, and the power input to the switching mechanism 48 is a switching output shaft (output shaft) in the front-rear direction that protrudes rearward from the switching case 46. ) 49. A front end portion of a transmission shaft 52 is connected to the rear end portion of the switching output shaft 49 via a universal joint 51, and planting work is connected to the rear end portion of the transmission shaft 52 via a universal joint 55. The front end portion of the planting input shaft 54 that protrudes forward from the gear box 53 of the machine 6 is connected, whereby the power output from the switching output shaft 49 is input to the planting work machine 6.

  The power input to the planting machine 6 is transmitted from the gear box 53 to the right and left planting shafts 56 projecting to the left and right sides. The power of the planting shaft 56 is input into each planter case 16 from the front end side. The power input into the planter case 16 causes the rotary case 17 supported on the rear end side of the planter case 16 to be rotationally driven, whereby the planting work machine 6 is driven to be planted.

  FIG. 6 is a front sectional view of the switching case showing the configuration of the switching mechanism, FIG. 7A is a sectional view of the switching case showing the state of switching to the first path, and FIG. It is sectional drawing of the switching case which shows the state which switched to the 2nd path | route. This switching mechanism 48 is a power transmission path to the planting work machine 6 (specifically, a power transmission path between the planting PTO shaft 33 of the transmission 21 and the planting input shaft 54 of the planting work machine 6). Are switched between the first route and the second route.

  A specific configuration will be described. The switching mechanism 48 includes the above-described switching input shaft (switching shaft) 47 and switching output shaft (switching shaft) 49 having the same axis, and the switching input shaft 47 and switching output shaft 49. And a non-constant speed shaft 57 which is a transmission shaft arranged in parallel in the switching case 46, and is supported by the switching input shaft 47 so as to be relatively rotatable about the shaft (specifically, freely rotatable) and An input-side eccentric gear 58, which is an eccentric gear eccentric with respect to the switching input shaft 47, is supported by the non-constant speed shaft 57 so as to perform synchronous rotation (specifically, integral rotation) around the axis. An inconstant speed side eccentric gear 59 which is an eccentric gear eccentric with respect to the constant speed shaft 57 and a fixed speed shaft 57 are supported and fixed to the inconstant speed shaft 57 so as to rotate synchronously (specifically, rotate integrally). And a non-constant speed side gear 61 that is a transmission gear and a synchronous rotation (specifically, And a switching output gear 62 that is a transmission gear that is supported and fixed to the switching output shaft 49 so as to always mesh with the inconstant speed side transmission gear 61 and a switching input shaft 47 that is a switching shaft or a switching output. A connecting sleeve (shift member) 63 that is externally slidable on the shaft 49 (in the illustrated example, the switching input shaft 47) and an unequal speed shaft 57 that is externally slidable in the axial direction and the unequal A switching sleeve (shift member) 64 that rotates relative to the fast shaft 57 (is free to rotate), and an outer peripheral side of the switching sleeve 64 so as to rotate synchronously (specifically, rotate integrally) with the switching sleeve 64. And a braking mechanism 67 for applying a braking force to the rotating cam 66.

  The brake mechanism 67 includes a brake arm 71 that swings in a direction away from and close to the periphery of the cam 66 with a swing shaft 68 parallel to the inconstant speed shaft 57 as a fulcrum, and the swing shaft 68 as a fulcrum. An operating arm 72 that is swung integrally with the braking arm 71, a support shaft 73 that is linearly extended and supported along a swinging locus drawn by the tip of the operating arm 72, and an exterior to the support shaft 73. Further, an elastic member 74 such as a compression spring for elastically urging the operation arm 72 is provided on the side where the brake arm 71 is swung to the peripheral side of the cam 66.

  A support shaft 73 is inserted into the distal end portion of the operation arm 72 in a state where the swing of the operation arm 72 is allowed. The above-described compression spring 74 is positioned between the nut 76 screwed to the outer periphery of the support shaft 73 and the tip of the upper machine operation arm 72. As described above, the compression spring 74 urges the operation arm 72 so that the braking arm 71 contacts the peripheral edge of the cam 66.

  When the braking arm 71 and the outer peripheral edge of the cam 66 are in contact with each other, the braking arm 71 resists the elastic force of the compression spring 74 as the contact position is further from the rotation center of the cam 66. The braking force acting on the cam 66 is increased by being swung to a position far from the rotation center of the 66. That is, an appropriate braking force can be applied from the compression spring 74 by appropriately setting the distance between the rotation center of the cam 66 and the outer peripheral edge of the cam 66. Incidentally, a contact portion 71 a having an arcuate periphery that smoothly contacts the periphery of the cam 66 is integrally formed at the tip of the braking arm 71.

  Engagement grooves 63 a and 64 a are respectively provided in the outer periphery of the connection sleeve 63 and the switching sleeve 64. The plate-like actuating body 77 having a pair of notch portions (engagement portions) 77a and 77b formed in an arc shape so as to engage with the two engagement grooves 63a and 64a, respectively, causes the connection sleeve 63 and The switching sleeve 64 is slid integrally. That is, the connection sleeve 63, the switching sleeve 64, and the operating body 77 constitute a path switching unit 78 that switches the transmission path to the planting work machine 6 between the first path and the second path.

  When the path switching unit 78 is slid in the first path direction (inconstant speed direction) that is one side of the switching shafts 47 and 49 (specifically, the input side eccentric gear 58 side), the connection sleeve A claw meshing-type first path side clutch (unequal speed clutch) 79 formed between 63 and the input side eccentric gear 58 is connected and operated by the engagement of the claws and is unequal with the switching sleeve 64. In addition to the connection operation of the braking clutch 81 formed between the speed side eccentric gear 59 and the connection operation of the first path side clutch 79, the brake clutch 81 is formed between the connection sleeve 63 and the switching output gear 62. The claw meshing-type second path side clutch (constant speed clutch) 82 is disconnected by releasing the engagement between the claws.

  In this state (first path selection state), the switching input shaft 47 → the input side eccentric gear 58 → the inconstant speed side eccentric gear 59 → the inconstant speed shaft 57 → the inconstant speed side gear 61 → the switching output gear 62 → the switching output. The power is transmitted in the order of the shaft 49, and the cam 66 → the switching sleeve 64 → the inconstant speed side eccentric gear 59 → the inconstant speed shaft 57 → the inconstant speed side gear 61 → the switching output gear 62 → the switching output shaft 49. The braking force from the braking mechanism 67 is transmitted.

  Then, the unequal speed power is transmitted to the switching output shaft 49 by the eccentric transmission from the input side eccentric gear 58 to the inconstant speed side eccentric gear 59 and the braking force from the braking mechanism 67. Incidentally, here, “transmission of inconstant speed power” means that the constant speed rotational power input to the switching input shaft 47 becomes the inconstant speed rotational power and is transmitted to the switching output shaft 49. . On the other hand, “transmission of constant speed power” means that the constant speed rotational power input to the switching input shaft 58 is transmitted to the switching output shaft 49 while maintaining the constant speed rotational power.

  When the path switching unit 78 is slid in the second path direction (constant speed direction) which is the other side (specifically, the switching output gear 62 side) opposite to the one side of the switching shafts 47 and 49, The first path side clutch 79 is disengaged and the brake clutch 81 is disengaged by releasing the engagement of the claws. In addition, the second path side clutch 82 is engaged with the claws as the first path side clutch 79 is disengaged. The connection is activated by meshing. In this state (second route selection state), the switching output shaft 49 is rotated integrally with the switching input shaft 47, and the braking force from the braking mechanism 67 is inoperative with respect to the switching output shaft 49. The power of the switching input shaft 47 is transmitted to the switching output shaft 49 at a constant speed.

  In the switching mechanism 48, as described above, the switching between the first path and the second path is performed by sliding the path switching unit 78 (shift members 63, 64) to both sides of the switching shafts 47, 49 in the axial direction. . A switching range set between the first path side clutch 79 and the second path side clutch 82 of the path switching unit 78 (specifically, a range between the input side eccentric gear 58 and the switching output gear 62). Thus, an operating mechanism 83 for slidingly moving the connection sleeve 63 and the switching sleeve 64 (the shift members 63 and 64) is provided.

  FIG. 8 is a side view showing the configuration of the operating mechanism. As shown in FIGS. 1 and 6 to 8, the operating mechanism 83 includes an operating shaft 84, which is parallel to the switching shafts 47 and 49 and supported by the switching case 46 so as to be slidable in its own axial direction. 84, an operating arm 86 supported in the switching case 46 so as to be swingable along the axial direction of 84, a connecting arm 87 supported on the switching case 46 side so as to swing together with the operating arm 86, and steering The switching operation lever (switching operation tool) 88 supported on the seat 9 side of the seat 8 so as to be able to swing back and forth, the lower end portion of the switching operation lever 88 and the distal end portion of the connecting arm 87 are both rotatable. And a connecting rod 89 connected to each other.

  The switching operation lever 88 is supported on the traveling machine body 3 side so as to be able to swing back and forth with a swing shaft 91 in the left and right direction located at its lower part (base end) as a fulcrum. A portion extending upward from 91 serves as a grip portion 88a, and a portion extending downward from the swing shaft 91 serves as a connecting portion 88b. The upper end portion of the connecting rod 89 is rotatably connected to the center side of the connecting portion 88b.

  Also, a left and right connecting pin 92 integrally projecting from the lower end (tip) of the connecting portion 88b and a left and right direction projecting on the opposite side across the swing shaft 91 of the connecting pin 92 are formed. Both ends of a tension spring (elastic member) 94 are rotatably connected to the support pin 93.

  The imaginary line connecting the swing shaft 91 and the support pin 93 in a side view becomes the reference line L beyond the fulcrum, and the switching operation lever 88 is positioned so that the connecting portion 88b is positioned below the reference line L. In the case of swinging, the switching operation lever 88 is urged forward by the tension spring 94, while the switching operation is performed so that the connecting portion 88b is positioned above the reference line L. When the lever 88 is swung, the switching operation lever 88 is urged backward by the tension spring 94. That is, since the biasing direction is reversed with reference to the reference line L, the single tension spring 94 can bias the switching operation lever 88 to both sides in the swinging direction.

  When the switching operation lever 88 is swung forward, the connecting portion 88b is swung rearward, and the switching operation lever 88 is moved to the first path switching position (indeterminate) by switching the urging direction of the tension spring 94 when the fulcrum is exceeded. It is swung to the constant speed switching position). Along with this, the connecting rod 89 moves rearward and obliquely downward, the connecting arm 87 swings backward, the operating arm 86 swings forward, the operating shaft 84 slides forward together with the operating body 77, and the path is switched. The unit 78 is moved to the first path side, the first path side clutch 79 is connected and the brake clutch 81 is connected and the switching mechanism 48 is switched to the first path selection state.

  On the other hand, when the switching operation lever 88 is swung rearward, the connecting portion 88b is swung forward, and the switching operation lever 88 is moved to the second path switching position by switching the biasing direction of the tension spring 94 when the fulcrum is exceeded. It is swung to (constant speed switching position). Along with this, the connecting rod 89 moves obliquely upward and forward, the connecting arm 86 swings forward, the operating arm 86 swings backward, the operating shaft 84 slides backward together with the operating body, and the path switching unit. 78 is moved to the second path side, the second path side clutch 82 is connected and the brake clutch 81 is disconnected, and the switching mechanism 48 is switched to the second path selection state.

  That is, the tension spring 94 described above causes the path switching unit 78 (shift member 63) to move in the sliding position near the first path side clutch 79 (on the side of the inconstant speed clutch 79 side) due to the reversal action of the urging direction due to the fulcrum being exceeded. The path switching unit 78 (shift member 63) is urged in the first path direction (unconstant speed direction) while the second position of the path switching unit 78 (shift member 63) is the second position at the slide position near the second path side clutch 82 (constant speed clutch 82 side). Energize in the route direction (constant speed direction)

  Further, the first path side clutch 79 and the second path side clutch 82 are intermittently engaged by the engagement and disengagement of the claws. However, when the connection sleeve 63 (and the switching input shaft 47) is rotated within a predetermined range (restriction range), the connection operation of the first path side clutch 79 and the second path side clutch 82 is restricted. Connection restriction means (not shown) is provided for the first path side clutch 79 and the second path side clutch 82, respectively. This restriction range is set to a rotation range in which the above-described planting clutch 39 can be disconnected.

  For this reason, when the planting clutch 39 is disengageable, switching from the disengaged state of the first path side clutch 79 to the connected state is prohibited, and switching from the disengaged state of the second path side clutch 82 to the connected state is prohibited. Is prohibited. On the other hand, when the planting clutch 39 cannot be disconnected, the switching of the first path side clutch 79 from the disconnected state to the connected state is permitted, and the switching of the second path side clutch 79 from the disconnected state to the connected state is allowed. Is acceptable.

  Incidentally, when the connection sleeve 63 and the switching input shaft 47 are rotated within the regulation range while the path switching unit 78 is urged in the first path direction by the elastic force of the tension spring 94, the connection regulation described above is performed. By the action of the means, as described above, the connection operation of the first path side clutch 79 is restricted. However, even in such a state, when the connection sleeve 63 and the switching input shaft 47 are rotated outside the regulation range (when the planting clutch 39 is switched to a state where the planting clutch 39 is not disconnected), the first path direction by the tension spring 94 is set. The first path side clutch 79 is immediately connected as a result of the biasing.

  Similarly, when the connection sleeve 63 and the switching input shaft 47 are rotated within the regulation range while the path switching unit 78 is biased in the second path direction by the elastic force of the tension spring 94, As described above, the connection operation of the second path side clutch 82 is restricted by the action of the connection restricting means. However, even in such a state, when the connection sleeve 63 and the switching input shaft 47 are rotated out of the restriction range (when the planting clutch 39 is switched to a state where the planting clutch 39 is not disengaged), the second path direction by the tension spring 94 is set. The second path side clutch 82 is immediately connected as a result of the biasing.

  As described above, the single tension spring 94 functions as a member for assisting smooth path switching operation by the switching mechanism 48, and is provided in the first path side clutch 79 and the second path side clutch 82, respectively. The connection restricting means reliably prevents the planting claws from being damaged due to the vehicle body traveling while the planting claws 18 are stopped in the planting posture and the planting claws 18 being dragged in the field. The brake clutch 81 may also be provided with connection restriction means having the same configuration as described above.

  Next, based on FIG.2 and FIG.9, the effect | action at the time of planting by the planting nail | claw 18 is transmitted at inconstant speed.

  FIG. 9 is a side view showing the movement trajectory of the planting claws during the planting operation while the traveling machine body travels forward. The movement restriction X in FIG. 2 and the movement locus X in FIG. 9 are movement loci when the planting claw 18 of the riding transplanter that is traveling forward and performing the planting operation is viewed from the traveling machine body 3 side. A movement locus X ′ in FIG. 9 is a movement locus when the planting claw 18 of the riding transplanter traveling forward and performing the planting operation is viewed from the field side, and the locus X ″ in FIG. FIG. 5 is a movement locus when a planting claw of a conventional riding transplanter traveling forward and performing planting work is viewed from the field side.

  In the first path selection state of the switching mechanism 48, the position (the ground contact position) where the tip of the planting claw 18 moves down the front track X1 and reaches the field scene in the circular movement track X drawn by the tip of the planting claw 18. ) At P1, the braking force from the braking mechanism 67 to the planting claw 18 begins to decrease. Subsequently, when the tip of the planting claw 18 at the ground contact position P1 reaches the lowest position P2, the planting claw 18 is switched to the planting posture, and the seedling Y is planted in the field and planted from the braking mechanism 67. The braking force on the claw 18 is completely inactive.

  Subsequently, when the tip of the planting claw 18 at the lowest position P2 reaches the position (brake start position) P3 immediately after the rear locus X2 is moved upward, the braking force from the braking mechanism 67 to the planting claw 18 is increased. It begins to act and then gradually increases. Subsequently, when the tip of the planting claw 18 at the brake start position P3 moves upward to the middle position (brake maximum position) P4 of the rear locus X2, the braking force from the braking mechanism 67 to the planting claw 18 is maximized. Become.

  Subsequently, after the tip of the planting claw 18 at the brake maximum position P4 reaches the uppermost position, the position immediately after starting to move downward on the front locus X1 becomes the scraping start position P5, and this brake maximum position P4 During the process from the scraping start position P5 to the scraping start position P5, the braking force from the braking mechanism 67 to the planting claw 18 gradually decreases, and before the tip of the planting claw 18 reaches the scraping start position P5, The braking force becomes zero, and scraping of the seedling Y on the seedling mount 13 is started.

  Subsequently, the braking force from the braking mechanism 67 to the planting claw 18 starts to act at the position (brake start position) P6 immediately after the tip of the planting claw 18 passes the scraping start position P5, and then gradually. While increasing, the scraping of the seedling Y from the seedling mount 13 is completed. When the tip of the planting claw 18 at the brake start position P6 moves downward to the midway position (brake maximum position) P7 of the front locus X1, the braking force from the braking mechanism 67 to the planting claw 18 becomes maximum. Subsequently, the tip of the planting claw 18 at the brake maximum position P7 moves downward on the front locus X1 and returns to the ground contact position P1 described above. This cycle is repeated thereafter.

  Thus, the outer edge shape of the cam 66 described above is set so that the braking force of the braking mechanism 67 is applied to the planting claw 18. With the above action, the tip of the planting claw 18 moves at high speed on the upper side and the lower side of the annular movement track X, and the tip of the planting claw 18 in the middle part of the front track X1 and the rear track X2. The movement speed of is slow. For this reason, as shown in FIG. 9, the planting claw 18 quickly passes the lower end position for planting the seedling Y, and the seedling Y and the planting claw 18 are efficiently prevented from being dragged in the field as compared with the conventional case. (See the shape of the lower end of the movement trajectories X ′ and X ″ in FIG. 9).

  According to the passenger transplanter configured as described above, it is possible to smoothly switch between the non-constant speed path and the constant speed path by the switching mechanism 48 and the operation mechanism 83. By switching to the non-constant speed path, a desired transplantation can be performed. It is easy to perform attachment work.

  Next, a different point from the above-mentioned form is demonstrated about another embodiment of the switching mechanism 48 based on FIG.

  10A and 10B are a front sectional view and a plan sectional view of a switching case showing the configuration of another embodiment of the switching mechanism, respectively. In the switching mechanism 48 shown in the figure, the switching sleeve 64 is omitted from the above-described configuration, and the cam 66 is rotated in synchronism with the inconstant speed shaft 57 (specifically, integrally rotated). The actuator 78 is attached only to the connection sleeve 63.

  Therefore, the braking force from the braking mechanism 67 acts on the switching output shaft 49 when the switching mechanism 48 is in both the first route selection state and the second route selection state. However, in the first path selection state, power is eccentrically transmitted by the pair of eccentric gears 58 and 59 constituting the eccentric gear train, whereas in the second path selection state, such transmission is not performed. In both states, the transmission state is greatly different.

  That is, the state of power transmission to the planting claw 18 is switched by switching from the first route selection state to the second route selection state or from the second route selection state to the first route selection state. This is the same as the embodiment described above.

6 Planting work machine 18 Planting claw 33 Planting PTO shaft 39 Planting clutch 43 Cutting restriction means 47 Switching input shaft (switching shaft)
48 Switching mechanism 63 Connection sleeve (shift member)
79 First path side clutch (non-constant speed clutch)
82 Second path side clutch (constant speed clutch)
83 Actuating mechanism 94 Compression spring (elastic member)

Claims (2)

  A switching mechanism (48) for switching the power transmission path to the planting work machine (6) is provided, and the switching mechanism (48) slides on the switching shaft (47) of the shift member (63) by planting. In the transplanting machine that switches between the constant speed path for transmitting the constant speed rotational power to the attached work machine (6) side and the inconstant speed path for transmitting the non-constant speed rotational power to the planting work machine (6) side, The switching mechanism (48) is connected and operated by sliding of the shift member (63) in the constant speed direction, which is one side of the switching shaft (47), to switch the transmission path to the constant speed path. The engagement-type constant speed clutch (82) and the shift member (63) slide in the non-constant speed direction, which is the other side of the switching shaft (47). A mesh-type non-constant speed clutch (79) that performs transmission path switching, An operating mechanism (83) for sliding the shift member (63) in the direction of the switching shaft (47) in the switching range between the speed clutch (82) and the inconstant speed clutch (79) is provided. An elastic member (94) whose urging direction is reversed when the shift member (63) is slid is provided in the operating mechanism (83), and the shift member (63) is provided by the elastic member (94). ) In the constant speed direction on the constant speed clutch (82) side, and in a non-constant speed direction on the non-constant speed clutch (79) side.   A meshing type planting clutch (39) for intermittently transmitting power to a planting PTO shaft (33) that outputs power to the planting work machine (6) side is disposed upstream of the switching mechanism (48). The planting clutch (39) is engaged in the rotational range of the planting PTO shaft (33) when the planting claw (18) of the planting work machine (6) is not located at a predetermined position. The switching mechanism (48) is provided with a disconnecting restriction means (43) for restricting the disconnection operation by the release, and the switching mechanism (48) is provided with a connection restricting means for restricting the connection operation of the constant speed clutch (81) or the inconstant speed clutch (79). The transplanter according to claim 1.

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