JP2010041925A - Farm implement - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a farm implement which hardly lose its weight balance, when being mounted on a lightweight and small traveling machine. <P>SOLUTION: The farm implement 1 includes: a front frame 13 having a mounting portion 10 to be mounted on a traveling machine 100; a plurality of link members 41, 42 swingably connected to the front frame 13; a rear frame 45 connected to the movement end side of each link member 41, 42; and a transmission frame 51 rotatably connected to a rotation shaft 53 projected from the rear frame 45 and supporting a working portion 50. The transmission frame 51 can freely rotates between a forward-moving work position and a rearward-moving work position. In the farm implement 1, a forward movement driving shaft 22 and a rearward movement driving shaft 23 are disposed on the mounting portion 10 in parallel in the lateral direction of the traveling machine 100 in a state projected on the side of the rear frame 45, and a forward movement driven shaft 30 capable of being connected to the forward movement driving shaft 22 and a rearward movement driven shaft 30 capable of being connected to the rearward movement driving shaft 23 are projected from the front frame 13 side face of the transmission frame 51 and from the opposite side face, respectively, in a state that the link members 41, 42 are most folded up. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a farm work machine capable of performing an offset work while moving the working unit to an offset position opposite to that during normal work, and reversing its reverse relationship (reversing reverse) and moving the traveling machine body backward, It is particularly suitable for agricultural machines that are mounted on small traveling aircraft.

  Agricultural work machines that are attached to the rear part of the traveling machine body and perform the offset work while proceeding with the traveling of the traveling machine body with the working unit moved to the side of the traveling machine body, for example, a padding machine, with the offset work of the working part Thus, the reaction force of the force acting on the field from the working part acts as a moment for swinging the traveling machine body. This moment does not pose a problem when acting on a relatively large traveling aircraft with a large mass, but when acting on a lightweight, small traveling aircraft, the weight balance between the traveling aircraft and the coater is lost. As a result, the traveling machine body becomes unstable and the stable work cannot be performed.

  Therefore, a parallel link is connected to the main body side frame of the coater, a transmission frame having one end rotatably attached to the moving end side of the parallel link, and a working unit is attached to the other end of the transmission frame, The work part can be moved in an offset direction in the horizontal direction, and the work part can be moved to the front side by swinging the parallel link, and the work part can be moved to the forward work position on one side and the reverse work position on the other side. A machine has been proposed (see Patent Document 1).

Japanese Patent Laying-Open No. 2003-199405 (paragraphs 0009 to 0012, FIG. 5)

  This conventional coater is configured to transmit the power transmitted from the traveling machine body to the working part via a transmission mechanism consisting of a universal joint and a transmission shaft, but the universal joint has a limited power transmission direction. Therefore, the allowable swing angle of the parallel link is small. Also, if the transmission frame is extended in the direction along the rear frame arranged on the moving end side of the parallel link, the distance from the rear frame to the working part increases, so the longitudinal length of the coater increases. , The weight balance between the traveling machine body and the wrinkle coater is likely to be lost.

  Therefore, in the conventional coater, when the working part is at the forward working position, the working part is rotated by setting the transmission frame to a posture tilted forward from the turning center of the transmission frame with respect to the rear frame. Although it is moved to the forward working position from the center, it is necessary to increase the length of the transmission frame. For this reason, since the glazing machine itself is enlarged, it is not suitable for mounting on a small traveling machine body.

  On the other hand, when the working unit is moved to the reverse working position, the allowable swing angle to the other side of the parallel link is small, and the transmission frame is inclined to the rear side from the rotation center with respect to the rear frame. There is a limit in positioning the working part further forward. Furthermore, since the length of the transmission frame is large, the distance from the mounting portion to the working portion is also increased, and the moment that the reaction force of the force acting on the field from the working portion swings the traveling machine body is increased. Eventually, when the traveling machine body is light and small, the weight balance between the traveling machine body and the hull coater tends to be lost, and the traveling of the traveling machine body becomes unstable and stable work cannot be performed.

  The present invention has been made in view of such a problem, and when performing work while being mounted on a lightweight and small traveling machine body, a weight balance with the traveling machine body is not easily lost, and an agricultural machine capable of performing stable work. The purpose is to provide.

The agricultural machine according to claim 1 includes a front frame having a mounting portion to be mounted on a rear portion of the traveling machine body, a plurality of link members swingably connected to the front frame, and movement of the link members. A rear frame coupled to the end side, and a transmission frame that is pivotally coupled to a pivot shaft projecting from the rear frame and supports the working portion at a tip position;
In the agricultural work machine in which the transmission frame is rotatable about a rotation axis of the rear frame, and the work unit can rotate between a forward work position where the working part is in a forward work position and a reverse work position where the work part is in a backward work position.
A forward drive shaft that receives power from the traveling machine body and a backward drive shaft that protrudes to the rear frame side in the mounting portion are arranged in parallel in the traveling machine body width direction,
When the working part is moved to the forward working position, a forward driven shaft that can be connected to the forward drive shaft protrudes from the front frame side surface of the transmission frame, and from the opposite side surface, The reverse driven shaft that can be connected to the reverse drive shaft protrudes,
When the link member is in the most folded state,
When the transmission frame rotates about the rotation shaft and the working unit moves to the forward operation position, the forward driven shaft is connected to the forward drive shaft,
When the transmission frame rotates around the rotation shaft and the working unit moves to the reverse operation position, the reverse drive shaft is connected to the reverse drive shaft,
A bracket for rotatably supporting the link member from the front frame to the rear frame side is provided in parallel in the traveling machine body width direction. Of the two brackets, the bracket located on the folding side of the link member The overhang length from the front frame is smaller than the overhang length of the bracket located on the opposite side from the front frame.

  Two link members are paired on the plane, but two link members, or any one of the link members may be arranged in parallel in the vertical direction because the transmission frame is supported by the front frame. In some cases, three or three link members may be connected to the front frame.

  The rear frame is arranged in parallel with the front frame in the forward working posture and the backward working posture, and constitutes a parallel link together with a plurality of link members. The link member is in a folded state when the working portion is in the forward working posture and the backward working posture, the rear frame is closest to the front frame, the forward drive shaft, the backward drive shaft, and the forward driven shaft In addition, the distance from the front frame is adjusted so that the connection with the reverse driven shaft is possible.

  The direction in which the link member is folded is on the side where the working portion assumes the forward working posture, and is on the right side with respect to the traveling direction front side (forward direction) of the traveling machine body. When the working unit moves to the left with respect to the forward direction of the traveling machine body by the rotation of the transmission frame, the backward working posture is set.

  In order to move the working part to the front side with the working part in the working posture, the rear frame needs to be closest to the front frame when the link member is in the folded state. From the frame, a bracket that rotatably supports the link member to the rear frame side is projected in parallel in the width direction of the traveling machine body, and from the front frame of the bracket located on the folding side of the link member of these two brackets. The overhang length of the bracket may be smaller than the overhang length of the bracket located on the opposite side from the front frame.

  When the overhanging lengths of the brackets arranged in parallel are equal, the distance between the two link members becomes small in the folded state of the link member, and the peripheral portion of the rotating shaft of the rear frame that supports the transmission frame is difficult to fit. On the other hand, the extension length of the bracket located on the folding side of the link member is smaller than the extension length of the bracket located on the opposite side, so that the distance between the link members is equal in the folded state of the link member. Larger than the case can be secured. As a result, the space surrounded by the front frame and both link members is widened, and the forward driven shaft and the reverse driven shaft, etc., which are located around the rotating shaft of the rear frame in the folded state of the link member, etc. The rear frame can be brought close to the front frame while being accommodated between both link members.

  The transmission frame rotates around the rotation axis of the rear frame when the link member is in the folded state, and is moved from the forward operation position where the working unit is in the forward operation posture to the reverse operation position where it is in the reverse operation posture. To move from the reverse work position to the forward work position. The transmission frame is rotated by a hydraulic cylinder as will be described later.

  When the working part is at the forward working position, the forward driven shaft protrudes from the side surface of the transmission frame on the front frame side, and the backward driven shaft protrudes from the opposite side surface, that is, the side surface on the rear side in the traveling direction of the agricultural work machine. . When the working unit moves to the reverse operation position, the reverse driven shaft protrudes from the side surface on the front frame side of the transmission frame, and the forward drive shaft protrudes from the opposite side surface on the rear side in the traveling direction of the agricultural work machine.

  When the link member is folded, the rear frame is closest to the front frame, and when the working part is in the forward working position, the forward drive shaft projects from the rear of the front frame mounting part toward the rear frame. And the forward driven shaft protrudes from the front frame side surface of the transmission frame, so that the forward driven shaft of the transmission frame is connected to the forward drive shaft.

  When the link member is folded and the working portion is in the reverse working position, the reverse drive shaft projects from the rear of the front frame mounting portion toward the rear frame, and the front frame side of the transmission frame. Since the reverse driven shaft protrudes from the side surface, the reverse drive shaft of the transmission frame is connected to the reverse drive shaft. Since the drive shaft and the driven shaft are directly connected via a clutch, the forward drive shaft and the reverse drive shaft, and the forward drive shaft and the reverse drive shaft include a clutch. The forward driven shaft and the backward driven shaft may be independent separate driven shafts or may be a single continuous driven shaft. In the latter case, the driven shaft penetrates the transmission frame in the width direction.

  In this way, the forward driven shaft is connected to the forward drive shaft only by the rotation of the transmission frame, and the reverse driven shaft is connected to the reverse drive shaft, so that the driven shaft and the drive shaft are connected. It is not necessary to move the transmission frame to the front frame side in the traveling direction of the farm work machine, and a driving device for performing the operation becomes unnecessary.

  By not having to move the transmission frame to the front frame side, the transmission frame, that is, the working part can be arranged at the position closest to the traveling machine body side, and the traveling direction of the agricultural machine itself when working on the agricultural machine The length (length in the front-rear direction) can be minimized. Therefore, even if the reaction force of the force acting on the field from the working portion becomes a moment and acts on the traveling machine body, the magnitude of the moment can be kept to a minimum. As a result, even when the traveling machine body is light and small, it is possible to avoid or reduce the situation where the weight balance between the traveling machine body and the agricultural machine is lost, to stabilize the traveling machine body, and to stabilize the work by the agricultural machine. Can be performed.

  The fact that the forward driven shaft is connected to the forward drive shaft only by the rotation of the transmission frame and the backward driven shaft is connected to the reverse drive shaft is specifically the rotational center of the transmission frame. The shaft is located on a straight line that passes through the midpoint of a straight line that passes through the forward drive shaft and a straight line that passes through the reverse drive shaft, and the forward driven shaft and the reverse driven shaft are turned from the rotary shaft, the forward drive shaft and the reverse drive shaft. This is possible by being located on a straight line passing through a position that is half the distance from the drive shaft.

  By positioning the rotation axis on a straight line passing through the midpoint of the straight line passing through the forward drive shaft and the reverse drive shaft, the driven shaft is positioned on a straight line at a certain distance from the rotary shaft. As long as the link member is in the folded state, the axis of the driven shaft can be positioned on the axis of the drive shaft regardless of the rotation of the transmission frame.

  Therefore, the forward driven shaft and the reverse driven shaft are located on a straight line passing through a position that is a half of the distance between the forward drive shaft and the reverse drive shaft from the rotation shaft. In the folded state of the link member, either the forward drive shaft or the reverse drive shaft is connected to either the forward drive shaft or the reverse drive shaft. As described above, when the working portion is in the forward working position, the forward driven shaft is connected to the forward driving shaft, and when the working portion is in the backward working position, the backward driven shaft is connected to the backward driving shaft. .

  To make it possible to connect the forward driven shaft to the forward drive shaft only by rotating the transmission frame and to connect the reverse driven shaft to the reverse drive shaft, the transmission frame, that is, the working part is closest to the traveling machine body side. Therefore, the length of the agricultural machine itself in the traveling direction can be minimized when the agricultural machine is working. Therefore, even when the traveling machine body is light and small, the situation in which the weight balance between the traveling machine body and the agricultural working machine is lost can be avoided or reduced, and the traveling of the traveling machine body can be stabilized.

  Hereinafter, the best mode for carrying out the present invention will be described with reference to the drawings. The drawing shows a case where the working unit 50 supported by the transmission frame is a padding working unit and the farm work machine 1 is a padding machine, but the form of the farm working machine 1 (working unit 50) is not limited at all. Includes all agricultural machines 1 capable of offset work.

  FIG. 1 shows a front frame 13 having a mounting portion 10 attached to the rear portion of a traveling machine body 100, and a plurality of parallel link members 41 and 42 that are pivotably connected to the front frame 13 and constitute a parallel link 40. And a rear frame 45 connected to the moving end side of each link member 41, 42, and a transmission frame 51 rotatably connected to a rotation shaft 53 (rotation center) projecting from the rear frame 45. 1 shows an agricultural machine 1. The working unit 50 is supported at the front end position of the transmission frame 51, and the transmission frame 51 has a forward working position where the working unit 50 is in the forward working posture and a backward working posture around the rotation shaft 53 of the rear frame 45. It is freely rotatable between the reverse work position. In the following, an example of a basket coater as the farm work machine 1 will be described.

  As shown in FIGS. 1 and 2, the farm work machine (spider coater) 1 is connected to the traveling machine body 100 at the mounting portion 10 of the front frame 13 having the input shaft 4 to which power from the traveling machine body 100 is input. It is attached to the traveling machine body 100 by being connected to a three-point link coupling mechanism (not shown) provided at the rear part of the traveling machine body 100 and performs a smearing operation according to the forward movement and the backward movement of the traveling machine body 100.

  The mounting portion 10 is joined to a connecting frame 11 that can be connected to the three-point link connecting mechanism of the traveling machine body 100 and a rear side of the connecting frame 11 via a pair of support arms 12 and 12 ′ arranged in parallel in the width direction of the traveling machine body 100. The input shaft 4 is disposed at the lower center of the connecting frame 11 in the length direction (the width direction of the traveling machine body 100). Power from a PTO shaft (not shown) of the traveling machine body 100 is transmitted to the input shaft 4 via a transmission shaft (not shown).

  A pair of support arms 12, 12 ′ projecting rearward at a predetermined interval in the length direction of the connection frame 11 are connected to the rear end side of the connection frame 11 so as to be rotatable in the vertical direction. A front frame 13 is joined to the rear ends of the arms 12 and 12 ′. The front frame 13 has a length sufficient to support the link members 41 and 42 at a distance. The front frame 13 is reinforced and mounted with a forward drive shaft 22 and a reverse drive shaft 23 that receive power from the traveling machine body 100, and an attachment frame 15 for connecting the link members 41 and 42 is provided in the front frame. 13 is fixed so as to surround.

  The mounting frame 15 is disposed between the link members 41 and 42 arranged in parallel, and in particular, the forward drive shaft 22 (see FIG. 8) and the reverse drive shaft 23 (see FIG. 8), which are output shafts located on the back (rear) side of the input shaft 4. In order to secure a space for storing the rotation center portion of the transmission frame 51 on the rear (rear) side of the reference), the traveling machine body 100 is shifted with respect to the input shaft 4 in the width direction. Specifically, since the forward drive shaft 22 is disposed on the same line as the input shaft 4, the rotational shaft 53 (rotation center) is only half the distance between the forward drive shaft 22 and the reverse drive shaft 23. From the same line of the input shaft 4, the traveling machine body 100 is shifted to the left with respect to the forward direction.

  Box-shaped brackets 16 and 17 for supporting the link members 41 and 42 project toward the rear side (transmission frame 51) side from both side positions in the length direction of the mounting frame 15, respectively, and end portions on the rear side. Support shafts 18 and 20 that pivotally support the link members 41 and 42 are provided at positions. Of the brackets 16, 17, the overhanging length of the bracket 17 from the mounting frame 15 is opposite to the folding side of the link members 41, 42 (forward operation position side), that is, the right side with respect to the forward direction of the traveling machine body 100. The length of the bracket 16 located on the left side of the side (reverse working position side) is smaller than the protruding length from the mounting frame 15. A large distance is secured between the link members 41 and 42 in the folded state of the link members 41 and 42, and the forward driven shaft 31 (see FIG. 8) and the reverse drive located around the rotating shafts 52 and 53 of the rear frame 45 This is because the rear frame 45 is brought closer to the mounting frame 15 (front frame 13) while the driven shaft 32 and the like are accommodated between the link members 41 and 42.

  The front end portion of the first link member 41 located on the working portion 50 side when in the forward working position is connected to the support shaft 18 of the bracket 17 located on the right side with respect to the forward direction of the traveling machine body 100, and on the left side. A second link member 42 located on the working unit 50 side when in the reverse working position is connected to the support shaft 20 of the bracket 16 located. Both end portions of the rear frame 45 are connected to the rear end portions (moving side end portions) of the link members 41 and 42. At the rear end portion of the first link member 41, an extension portion 41a is formed that projects from the connecting position with the rear frame 45 by bending (inclining) rearward with respect to the axis of the first link member 41. A later-described (electric type) hydraulic cylinder 61 is connected to the extension 41a. The extension 41a is bent and protrudes rearward from the link member 41, so that the hydraulic cylinder 61 is installed between the parallel link 40 and the transmission frame 51 while avoiding interference between the hydraulic cylinder 61 and the link member 41. Have been able to.

  A support shaft 20 penetrating from the left bracket 16 protrudes in the vertical direction, and the link member 42 is connected to the upper end of the support shaft 20. The lower end of the support shaft 20 is disposed in parallel with the link member 42. A link member 43 that supports 51 is connected. The parallel link 40 includes a mounting frame 15 (front frame 13) and a rear frame 45 which are parallel to each other, and a link member 41, a link member 42 and a link member 43 which are parallel to each other.

  Coaxial rotation shafts 52 and 53 are disposed between the rear end portions of the link member 42 and the link member 43, the link member 42 and the rear frame 45 are rotatably connected to the upper rotation shaft 52, and the lower side The link member 43 and the transmission frame 51 are rotatably connected to the rotation shaft 53. When all the link members 41 to 43 are rotated by expansion and contraction of the hydraulic cylinder 61, the rear frame 45 rotates around the rotation shaft 52 and moves away from the mounting frame 15 (front frame 13). When the hydraulic cylinder 61 expands and contracts while all the link members 41 to 43 are in the folded state, the transmission frame 51 rotates around the rotation shaft 53. When the hydraulic cylinder 61 contracts from the state of FIG. 1 where the working unit 50 is at the forward working position Pf, the transmission frame 51 rotates about the pivot shaft 53 as the pivot center O, and reaches 180 ° to the reverse working position Pb shown in FIG. Rotate. The transmission frame 51 can also move to the intermediate storage position Ph (see FIG. 8).

  The transmission frame 51 has a box shape in order to store a power transmission mechanism that transmits power to the working unit 50, and projects from the rotating shaft 53 to the working unit (spreading working unit) 50 side. It is constructed and a working part (spreading working part) 50 is connected to the tip part. The working unit 50 is rotated up and down by a working posture adjusting screw 47 installed between the connecting frame 11 and the front frame 13 so that the working posture can be adjusted. The power transmission mechanism transmits power from a forward passive clutch 31 or a reverse passive clutch 32 described later to the working unit 50.

  As shown in FIG. 1, the working unit (spreading working unit) 50 includes a pre-processing unit 55 that cuts an old paddle formed along the periphery of the field and deposits the soil, and an old paddle cut from the piled up soil And a trimming part 57 to be applied to. The pretreatment unit 55 includes a tilling rotor that is rotatably supported. The tilling rotor is connected to and supported by the transmission frame 51. The trimming unit 57 includes a polyhedral drum 58 that is rotatably supported. The polyhedral drum 58 is connected to and supported by the transmission frame 51. Power from the driven shaft 30 (see FIG. 13) is transmitted to the tilling rotor and the polyhedral drum 58 via a power transmission mechanism in the transmission frame 51.

  A forward drive shaft 22 and a reverse drive shaft 23, which are arranged at a predetermined distance in the length direction, are attached to an intermediate portion in the longitudinal direction of the front frame 13 (attachment frame 15). ) To the rear frame 45 side. The forward drive shaft 22 is positioned on the same axis as the input shaft 4, and the power from the input shaft 4 is transmitted to the forward drive shaft 22 via the universal joint 24 and the like.

  The power transmitted to the forward drive shaft 22 is transmitted to the reverse drive shaft 23 through gears attached to the forward drive shaft 22 and the reverse drive shaft 23. When power is transmitted to the forward drive shaft 22, power is also transmitted to the reverse drive shaft 23, and both drive shafts 22 and 23 rotate. A forward drive clutch 27 (see FIG. 8) is connected to the distal end portion of the forward drive shaft 22, and a reverse drive clutch 28 (see FIG. 8) is connected to the distal end portion of the reverse drive shaft 23. The protruding lengths of the forward drive shaft 22 and the reverse drive shaft 23 from the front frame 13 are equal, and the distances from the front frame 13 to the tips of the forward drive clutch 27 and the reverse drive clutch 28 are also equal. The forward drive shaft and the reverse drive shaft in claim 1 include a forward drive clutch 27 and a reverse drive clutch 28, respectively.

  As shown in FIG. 8, an axis parallel to the axes of the forward drive shaft 22 and the reverse drive shaft 23 is located near the rotational center O of the transmission frame 51 and closer to the working unit 50 than the rotational shaft 53. A driven shaft 30 is supported. The driven shaft 30 is mounted through the transmission frame 51, and both end portions in the axial direction protrude from the side surface of the transmission frame 51. The distance from each side surface of the transmission frame 51 to each tip of the driven shaft 30 is equal. In this embodiment, the driven shaft 30 serves as both the forward driven shaft and the reverse driven shaft in claim 1. However, the driven shaft 30 is separated into the forward drive and the reverse drive, and each of them is separated from the forward drive shaft 22 and the reverse drive shaft. The drive shaft 23 may be connected. Even when the driven shaft 30 is separated for forward movement and backward movement, the respective axes are arranged on the same line.

  When the working unit 50 is in the forward working position shown in FIG. 1, the tip of the driven shaft 30 (see FIG. 8) on the side protruding from the side surface on the front frame 13 side of the transmission frame 51 as shown in FIG. A forward passive clutch 31 is connected, and a reverse passive clutch 32 (see FIG. 8) is connected to the tip of the driven shaft 30 on the side protruding from the rear side surface. The distances from the side surfaces of the transmission frame 51 to the tips of the forward passive clutch 31 and the reverse passive clutch 32 are also equal. The forward passive clutch 31 and the reverse passive clutch 32 correspond to the forward driven shaft and the backward driven shaft in claim 1, respectively.

  A rotation shaft 53 serving as a rotation center O of the transmission frame 51 is positioned on a straight line passing through a midpoint between a straight line passing through the forward drive shaft 22 and a straight line passing through the reverse drive shaft 23. The passive clutch 32 is located on a straight line passing through a position that is a half of the distance between the forward drive shaft 22 and the reverse drive shaft 23 from the rotation shaft 53. As a result, as long as the link members 41 to 43 are in the folded state, the axis of the driven shaft 30 (the forward passive clutch 31 and the reverse passive clutch 32) is used as the forward drive shaft regardless of the rotation of the transmission frame 51. 22 (forward drive clutch 27) or reverse drive shaft 23 (reverse drive clutch 28) can be positioned on the axis.

  Accordingly, when the link members 41 to 43 are in the folded state and the working unit 50 shown in FIG. 1 is in the forward working position, the forward passive clutch of the driven shaft 30 of the forward drive shaft 22 (forward drive clutch 27). When the axes 31 are in a state where they can be connected to each other and the working unit 50 shown in FIG. 4 is in the reverse operation position, the reverse of the driven shaft 30 of the reverse drive shaft 23 (reverse drive clutch 28). The axes of the passive clutch 32 for use coincide with each other and can be connected to each other.

  In addition to the positional relationship between the drive shafts 22 and 23 and the driven shaft 30 in the length direction of the front frame 13, the distance between the front frame 13 and the transmission frame 51 when the link members 41 to 43 are in the folded state. Is adjusted, the forward drive shaft 22 (forward drive clutch 27) is connected to the forward passive clutch 31 of the driven shaft 30, and the reverse drive shaft 23 (reverse drive is shown in FIG. 4). The drive clutch 28) is connected to the reverse passive clutch 32 for the driven shaft 30.

  The distance between the front frame 13 and the transmission frame 51 is that the transmission frame 51 has finished rotating around the rotation shaft 53 and the forward passive clutch of the driven shaft 30 is driven by the forward drive shaft 22 (forward drive clutch 27). When 31 is going to oppose, it sets so that it may become the distance which can be connected when the forward passive clutch 31 and the forward drive clutch 27 oppose, rotating relatively. An angle θ formed with the traveling direction of the traveling machine body 100 when the link members 41 to 43 are in a folded state is set so that the distance between the clutches 31 and 27 is relatively rotated. .

  It should be noted that when the forward passive clutch 31 and the forward drive clutch 27 are shifted from an angled state to an opposing (no angled) state, a coil spring or the like connected to at least one of the shafts is attached. Since the biasing member absorbs the relative displacement and the relative rotational displacement, the connection can be made smoothly even if contact is started with an angle.

  The transmission frame 51 is pivoted by the expansion and contraction of the hydraulic cylinder 61 (electric type) extending between the extension frame 41a projecting rearward from the rear end of the first link member 41 and the transmission frame 51. Rotating around (rotating shaft 53), the state of the forward working position shown in FIG. 1 and the state of the backward working position shown in FIG. 4 are switched. One end of the hydraulic cylinder 61 is connected to the extension 41 a and the other end is connected to a rotating member 62 disposed between the transmission frame 51 and the rear frame 45.

  The rotating member 62 has a long hole-like opening 62a projectingly provided on the transmission frame 51 so that the operating part 64 can be relatively moved. The rotating member 62 projects on the rear frame 45 in a state where the operating part 64 is inserted through the opening 62a. The support shaft 63 is pivotally connected. In the drawing, the operation portion 64 is related to the rotation shaft 53 so that the transmission frame 51 can be rotated 180 degrees around the rotation shaft 53 while the rotation angle of the rotation member 62 by the hydraulic cylinder 61 is about 90 degrees or less. The link member 41 is provided on the folding side, that is, on the extension 41 a side to which one end of the hydraulic cylinder 61 is connected, and the support shaft 63 is disposed on the front frame 13 side with respect to the rotation shaft 53. The support shaft 63 protrudes from the bottom surface of the rear frame 45.

  Specifically, on the plane, the operation unit 64 is disposed on a line in the axial direction of the transmission frame 51 (direction orthogonal to the traveling direction of the traveling machine body 100) through the rotation shaft 53, and travels through the rotation shaft 53. By disposing the support shaft 63 on a straight line in the traveling direction of the machine body 100, the transmission frame 51 can be rotated 180 degrees while the rotation angle of the rotation member 62 is set to about 90 degrees.

  Corresponding to the operation part 64 projecting from the extension part 41 a side of the transmission frame 51 and the support shaft 63 projecting from the front frame 13 side of the rear frame 45, the rotating member 62 has the rotating shaft 53. It is formed in a C-shaped shape that wraps around. Further, since the operation portion 64 is rotated around the support shaft 63 (rotation center O ′) by the axial force from the hydraulic cylinder 61 received by the connection portion with the hydraulic cylinder 61, the connection portion is related to the operation portion 64 with respect to the support shaft 63. It is formed on the opposite side.

  In the forward working position of the working unit 50 shown in FIG. 1, the link members 41 and 42 are in the folded state, and the hydraulic cylinder 61 is in the extended state. From the state shown in FIG. 1, by contracting the hydraulic cylinder 61, the rotating member 62 moves around the support shaft 63 as the connecting portion of the rotating member 62 to the hydraulic cylinder 61 is drawn toward the hydraulic cylinder 61 side. In FIG. 1, the operation portion 64 (transmission frame 51) that rotates clockwise and engages with the opening 62 a is dragged by the rotation member 62 and attempts to rotate.

  While the rotation member 62 rotates around the support shaft 63, the transmission frame 51 rotates around the rotation shaft 53. Therefore, when the operation unit 64 is in the state shown in FIGS. When the operation unit 64 is positioned on a straight line connecting the support shaft 63 and the rotation shaft 53, the distance from the support shaft 63 to the operation unit 64 is maximized. Thus, since the distance from the support shaft 63 to the operation unit 64 changes until the transmission frame 51 shifts from the forward work position to the reverse work position, the opening 62a is made to follow the change in the distance. It is formed in a long hole shape.

  The state in which the hydraulic cylinder 61 contracts and the rotating member 62 rotates the operating portion 64 until it is positioned on a straight line connecting the support shaft 63 and the rotating shaft 53 is the intermediate position shown in FIG. The part 64 is located on the farthest side from the support shaft 63 of the opening 62a. Further, the situation in which the hydraulic cylinder 61 is fully contracted and the operating portion 64 is moved from the forward working position to the symmetrical position with respect to the rotation shaft 53 is the backward working position shown in FIG. In the state shown in FIG. 4, the operation portion 64 is located closest to the support shaft 63 of the opening 62a. From the state shown in FIG. 4, the hydraulic cylinder 61 is extended, and the rotating member 62 is rotated in the reverse direction (counterclockwise), thereby returning to the forward working position in FIG. 1 through the state in FIG. 3.

  Here, the offset amount Xr of the working unit (spreading working unit) 50 moved to the reverse working position Pb shown in FIG. 4 is equal to that of the working unit (spreading working unit) 50 moved to the forward working position Pf shown in FIG. It is larger than the offset amount Xf. This difference ΔX = (Xr−Xf) in the offset amount corresponds to the distance D between the forward drive shaft 22 and the reverse drive shaft 23 in plan view, and as described above, the driven shaft at the forward work position. 30 is positioned on the same axis as the forward drive shaft 22, and the driven shaft 30 is located at a distance of ½ of the distance between the forward drive shaft 22 and the reverse drive shaft 23 from the rotation shaft 53. It is related to being located on a straight line passing through.

  In this relationship, when the offset amount Xr of the working unit 50 at the reverse working position Pb is to be made larger by, for example, Y than the offset amount Xf of the working unit 50 moved to the forward working position Pf, the two drive shafts 22, 23 are used. The distance between them may be set to Y. That is, the offset amount Xr of the working unit 50 during the reverse operation can be arbitrarily set within a range in which the two drive shafts 22 and 23 can be arranged.

  A restraint / release device 80 that restrains the rotation of the transmission frame 51 when the working unit 50 is in the forward work position and the reverse work position on the rear frame 45 and releases the restraint when switching between the states. Is placed. In FIG. 1, a region where the restraint / release device 80 is disposed on the rear frame 45 is shown as a restraint / release mechanism portion 84.

  The restraining / releasing device 80 includes an engaged portion 81 projecting from the transmission frame 51, a forward engagement member 82 that can be engaged with the engaged portion 81 when the working portion 50 is in the forward working position, Either the reverse side engagement member 83 that can be engaged with the engaged portion 81 when the working unit 50 is in the reverse operation position, or the forward side engagement member 82 or the reverse side engagement member 83 is engaged. The release member 85 which cancels | releases the state engaged with the part 81 is provided.

  The forward side engaging member 82 is rotatably installed at a position corresponding to the engaged portion 81 of the rear frame 45 when the working unit 50 is in the forward working position, and when the working unit 50 is in the forward working position. At one end, the engaged portion 81 can be engaged. The reverse side engagement member 83 is rotatably installed at a position of the rear frame 45 corresponding to the engaged portion 81 when the working unit 50 is in the reverse working position, and when the working unit 50 is in the reverse working position. At one end, the engaged portion 81 can be engaged.

  The release member 85 is connected directly or indirectly to the other end portions of the forward side engagement member 82 and the reverse side engagement member 83, and rotates the forward side engagement member 82 and the reverse side engagement member 83 by expansion and contraction. The state where one of the forward side engaging member 82 and the backward side engaging member 83 is engaged with the engaged portion 81 is released.

  The engaged portion 81 protrudes from the transmission frame 51 so that it rotates around the rotation shaft 53 as the transmission frame 51 rotates. Regardless of whether the transmission frame 51 is rotated or not (regardless of the forward working position or the reverse working position), the axial direction of the transmission frame 51 is always in the direction orthogonal to the traveling direction. Accordingly, the engaging portions 82 a and 83 a that are formed at one end portions of the forward-side engaging member 82 and the backward-side engaging member 83 and engage with the engaged portion 81 pass through the rotation shaft 53 and travel vehicle body 100. It is arrange | positioned in the symmetrical position with respect to the traveling direction.

  Since the engaging portions 82 a and 83 a are disposed at symmetrical positions with respect to the rotation shaft 53, the main body portion 87 of the forward-side engagement member 82 and the main body portion 88 of the reverse-side engagement member 83 pass through the rotation shaft 53. These are arranged symmetrically with respect to the traveling direction of the traveling machine body 100, and are respectively supported by the rear frame 45 so as to be rotatable at positions where the engaging portions 82a and 83a engage with the engaged portion 81 by rotation. In the drawing, when the engaging portion 82a and the engaging portion 83a are engaged with the engaged portion 81, the forward-side engaging member 82 and the reverse-side engaging member are located at a position near the front frame 13 of the engaged portion 81. The rotation shaft of the joint member 83 is arranged.

  Since the forward side engagement member 82 and the reverse side engagement member 83 are arranged symmetrically with respect to the traveling direction of the traveling machine body 100, the forward side engagement member 82 and the reverse side engagement member 83 are simultaneously operated to rotate in the drawing. A connecting member 89 is installed between the main body portions 87 and 88 of the forward-side engaging member 82 and the backward-side engaging member 83 so that the end portions 89a on both sides of the connecting member 89 are connected to each other. The release member 85 pulls the connecting member 89 in the traveling direction of the traveling machine body 100 to engage one of the engaging member 82 and the engaging member 83 engaged with the engaged portion 81. Release from.

  A connecting member 89b is installed between the release member 85 and the connecting member 89 to linearly move the connecting member 89 in the traveling direction of the traveling machine body 100. One end of the connecting member 89b is connected to the connecting member 89 and the other end. Is connected to the release member 85. Between the connecting member 89b and the release member 85, the engaging members 82a and 83a are urged in the direction in which the engaging portions 82a and 83a are engaged with the engaged portion 81 by urging the connecting member 89 toward the front frame 13 in a normal state. A biasing member (compression spring) 89c that maintains the engaged state when any of the engaging portions 82a and 83a is engaged with the engaged portion 81 is interposed.

  When the working portion 50 is in the forward working position in FIG. 1, the engaging portion 82 a of the forward-side engaging member 82 is engaged with the engaged portion 81. In this state, when the transmission frame 51 is rotated around the rotation shaft 53 to shift to the reverse operation position, or to shift to the retracted state, the release member 85 resists the biasing member 89c and causes the connecting member 89 to move. The engagement state of the engaging portion 82a with the engaged portion 81 is released by pulling it toward the releasing member 85 side.

  When the working portion 50 is in the reverse working position in FIG. 4, the engaging portion 83 a of the reverse side engaging member 83 is engaged with the engaged portion 81, and at this time also when the transmission frame 51 is rotated. Further, the release member 85 pulls the connecting member 89 against the biasing member 89c to release the engagement state of the engagement portion 83a with the engaged portion 81.

  Since the release member 85 can release the engagement of the engaging portions 82a and 83a with the engaged portion 81 as long as it draws at least the connecting member 89 toward the release member 85, the release device 84 has a straight line. Various driving devices having a function of transmitting motion to the connecting member 89 can be used. However, in the illustrated example, when the release member 85 pulls the connecting member 89 and releases the engagement of the engaging portions 82a and 83a, the release member 85 itself does not have the ability to return to the normal state. In order to cope with this, a motor capable of switching between forward rotation and reverse rotation, particularly a wiper motor or a stepping motor, is used as the release member 85. In this case, when the release member 85 (motor) rotates in the forward direction, the connecting member 89 is attracted, and in the reverse direction, the connection member 89b is returned to the normal state, and the urging member 89c exhibits a restoring force. Return.

  When an electric motor is used as the release member 85, a vibration suppressing member such as a vibration isolating rubber is interposed between the electric motor on the rear frame 45 in order to suppress propagation of vibration generated by the electric motor itself. Be made. The operation control of the electric motor is controlled by the controller according to the operation content from an operation switch (not shown).

  On either one of the front frame 13 (attachment frame 15) and the rear frame 45, a restraint / release device 70 for maintaining the link members 41 to 43 in a folded state is installed.

  The restraining / releasing device 70 rotates around an engaged portion 72 protruding from one of the front frame 13 (mounting frame 15) and the rear frame 45, and a support shaft Q protruding from the other. The engaging member 71 is engageable with the engaged portion 72 at one end when the link members 41 to 43 are in the folded state, and is connected to the other end of the engaging member 71, and is engaged by expansion and contraction. A release member 73 for rotating the 71 around the support shaft Q and releasing the state where the engagement member 71 is engaged with the engaged portion 72 is provided.

  In the drawing, a hook portion 71 a formed at the distal end portion of the engaging member 71 is engaged with the support shaft 18 protruding from the bracket 17 on the right side in the forward direction of the traveling machine body 100, and the support shaft 18 is engaged with the engaged portion 72. Since the support shaft Q that pivotally supports the engaging member 71 is provided on the rear frame 45, the engaging member 71 is pivoted on the front frame 13 (mounting frame 15) or the bracket 17. The support shaft Q may be used as the engaged portion 72. In any part of the engaging member 71, a biasing member 75 that exerts a restoring force in a direction in which the hook portion 71 a of the engaging member 71 is engaged with the engaged portion 72 (support shaft 18) is maintained. Is placed. In the drawing, one end of the urging member 75 is connected to the end 71 b of the engaging member 71 on the release member 73 side, and the other end of the urging member 75 is connected to any part of the rear frame 45. In this case, the urging member 75 exhibits a restoring force when it receives a tensile force from the operation member 74 in the axial direction as a tension spring.

  A release member 73 is connected directly or indirectly to the end of the engaging member 71 opposite to the hook portion 71a with respect to the support shaft Q. As described above, the urging member 75 tries to maintain the engaged state of the hook portion 71a, so that the release member 73 exerts a force in the direction of releasing the engagement against the urging member 75. Give it. Therefore, in the drawing, the operation member 74 is connected to the release member 73, and a force is applied to the engagement member 71 through the operation member 74 in a direction to release the engagement. In the illustrated case, the release member 73 pushes the operating member 74 toward the front frame 13 to rotate the engaging member 71 clockwise about the support shaft Q, and the hook portion 71a is moved to the engaged portion 72 (support shaft). Remove from 18). In a state where the hook portion 71 a is detached from the engaged portion 72, the urging member 75 exerts a restoring force, thereby rotating the engaging member 71 counterclockwise and engaging the hook portion 71 a with the engaged portion 72. Return to a state where it can be matched.

  If the release member 73 also has a function of transmitting a linear motion to the operation member 74 or the engagement member 71, various drive devices can be used, but the release used in the restraint / release device 80 in the drawing. A wiper motor is used in the same manner as the member 85. In this case, the operating member 74 is moved toward the front frame 13 by the rotation of the output shaft of the wiper motor, whereby the engaging member 71 is rotated around the support shaft Q, and the hook portion 71a is detached from the engaged portion 72. When the power of the wiper motor is turned off, the urging member 75 returns the operation member 74 to the original position and rotates the engagement member 71 in the engagement direction.

  FIG. 8 shows the storage state of the agricultural working machine 1, and FIG. 7 shows a state where the transmission frame 51 and the working unit 50 are omitted from FIG. In this state, the engagement member 71 in FIG. 1 is disengaged from the engaged portion 72 (support shaft 18), and the link members 41 to 43 are moved from the folded state to the left side with respect to the traveling direction of the traveling machine body 100. In an inclined state, the link members 41 to 43 can be freely swung by vibration. Therefore, in the drawing, the holding device 41A for restraining the link member 41 in the retracted state to the working unit 50 is disposed in the link member 41 and the working unit 50, thereby preventing the link members 41 to 43 from freely swinging.

  The holding device 41 </ b> A includes a pin-shaped (projection-shaped) fitting member 41 b that projects from the side surface of the link member 41 located on the working unit 50 side among the plurality of link members 41 to 43, and a link between the working unit 50. 1. It consists of a plate-like or box-like fitted member 54 that is fixed to the member 41 side and has an opening through which the fitting member 41b can be inserted, and is fitted to the fitting member 41b as shown in FIGS. The members 54 are arranged at positions where they are fitted together when the link member 41 is rotated to the storage position of the transmission frame 51.

  The fitting member 41 b rotates around the support shaft 18 on which one end of the link member 41 is pivotally supported, and the fitted member 54 keeps the transmission frame 51 parallel to the rear frame 45 as the hydraulic cylinder 61 extends. Since the parallel movement is performed while maintaining, the fitting member 41b and the fitting member 54 are arranged at the positions where the rotation locus of the fitting member 41b and the movement locus of the fitting member 54 intersect each other. Is done.

  Since the fitting member 41b meets the engaged portion 54 that rotates around the support shaft 18 and moves in parallel, the opening of the engaged portion 54 approaches while rotating, and the fitting member 41b is in the opening when contacting. A width larger than the width of the fitting member 41b is given in the direction of the rotation surface of the fitting member 41b so as to enter. In a state where the fitting member 41b is fitted to the fitted member 54, the fitting member 41b penetrates the opening of the fitted member 54 and is formed around the fitting member 41b as shown in FIG. The flange 41c is locked to the fitted member 54 from the link member 41 side. A pin 41d is inserted into the fitting member 41b penetrating the opening of the fitted member 54 to prevent the fitting member 54 from coming out of the opening. The pin 41d is locked to the fitted member 54 so as to come out, and the fitting member 41b is restrained to the fitted member 54. When not in use, the pin 41d is temporarily fixed to one of the fitted members 54 as shown in FIG.

  Here, the operation of the agricultural work machine 1 when moving the work unit 50 from the forward work position Pf to the reverse work position Pb will be described. In the state where the working unit 50 is at the forward working position Pf, the parallel link 40 is swung with a predetermined angle θ on one side, and the restraint / release device 70 locks the swing of the parallel link 40. Is in a state of being

  First, the operation switch is operated so that the working unit 50 moves from the forward work position Pf to the reverse work position Pb. When the operation switch is operated, the release member (electric motor) 85 of the restraint / release device 80 rotates the forward-side engagement member 82 counterclockwise to engage the engaged portion 82a with the engaged portion 81. Is released and the rotation lock state of the transmission frame 45 is released.

  When the rotation of the transmission frame 45 is in an unlocked state, the hydraulic cylinder 61 contracts and the rotation member 62 rotates clockwise. Accordingly, the opening 62a formed in the rotation member 62 is an operating portion. 64 (see FIG. 9) is pressed, and the transmission frame 45 rotates clockwise about its rotation fulcrum O. At the same time, the front passive clutch 31 (see FIG. 13) rotates clockwise around the rotation fulcrum O of the transmission frame 45 and disengages from the front drive clutch 27 (see FIG. 13).

  When the hydraulic cylinder 61 further contracts, the working unit 50 rotates clockwise from the forward working position Pf as shown in FIG. 3 and moves to the other side of the traveling machine body 100 through the rear of the traveling machine body 100. As the working unit 50 moves to the reverse operation position Pb, the engaged portion 81 enters the engaging portion 83a of the reverse engagement member 83, and the reverse engagement member 83 engages with the engaged portion 81. Then, the rotation of the transmission frame 51 is restrained, and the rear passive clutch 32 is connected to the rear drive clutch 28, and the movement of the working unit 50 to the reverse working position Pb is completed.

  As described above, the working unit 50 can be moved from the forward working position Pf to the backward working position Pb by the expansion and contraction of the single hydraulic cylinder 61. For this reason, when the leading end of the traveling machine body 100 reaches the end of the field, the work unit 50 is moved to the reverse position, and the traveling machine body 100 is moved backward, so that the unworked portion that is left in the corner of the field is painted. It is possible to shorten the time required to perform and improve the workability of the entire glazing operation.

  Next, a procedure for moving the working unit 50 from the reverse work position Pb to the storage position Ph will be described. First, when the operation switch is operated, the restraining / releasing device 80 is activated to release the rotation lock state of the transmission frame 51, and then the hydraulic cylinder 61 is extended as shown in FIG. It moves from the work position Pb to the forward work position Pf.

  When the working portion 50 moves to the forward working position Pf, the engaged portion 81 enters the engaging portion 82a of the forward side engaging member 82 of the restraining / releasing device 80 as shown in FIG. The movement is restrained, and the front passive clutch 31 is connected to the front drive clutch 27. Subsequently, the restraining / releasing device 70 is actuated to rotate the engaging member 71 clockwise, so that the rocking lock state of the parallel link 40 is released.

  When the swing lock state of the parallel link 40 is released, the hydraulic cylinder 61 extends. Here, since the rotation of the working unit 50 is restrained by the restraining / releasing device 80, the transmission frame 51, the rear frame 45, and the turning member 62 behave integrally. For this reason, even if the hydraulic cylinder 61 extends, the rotating member 62 does not rotate. On the other hand, as the hydraulic cylinder 61 extends, the force that the hydraulic cylinder 61 extends, that is, the force directed to the other side is transmitted to the rear frame 45 via the rotating member 62, so the first link member 41, The 2 link member 42 and the 3rd link member 43 are rotated to the other side.

  As described above, the extension of the hydraulic cylinder 61 causes the parallel link 40 to rotate to the storage side, and the rear frame 45 moves to the storage side. As the parallel link 40 swings to the storage side, a fitting member 41b provided on one side surface of the first link member 41 projects from the working portion 50 as shown in FIGS. The opening of the fitting member 54 is inserted. As the parallel link 40 swings to the other side, the front passive clutch 31 moves obliquely rearward and disengages from the front drive clutch 27. Thereafter, when the flange 41c of the fitting member 41b hits the fitted member 54, the extension of the hydraulic cylinder 61 is stopped, and the swing of the parallel link 40 to the other side is completed. Here, the locking pin is passed through the fitting member 41b inserted through the opening of the fitted member 54, and the swing of the parallel link 40 is locked.

  Thus, even if the working unit 50 moves to any of the forward working position Pf and the backward working position Pb, the moving end side of the parallel link 40 is in a position close to the front frame 13 side, and the parallel link 40 moves. Since the end side is disposed at a position close to the traveling machine body 100 side, the working unit 50 attached to the moving end side of the parallel link 40 can be disposed close to the traveling machine body 100 side.

  For this reason, the length of the agricultural machine itself in the front-rear direction can be shortened during the operation of the agricultural machine, and even if the reaction force of the force acting on the field from the working unit 50 acts as a moment on the traveling machine body 100, The magnitude of this moment can be made relatively small. As a result, even when the traveling machine body 100 is light and small, it is possible to prevent the weight balance between the traveling machine body 100 and the agricultural machine from being lost, and the traveling machine body 100 can be stably traveled to perform work by the agricultural machine 1. It can be performed stably.

  In the above-described embodiment, a case where a mortar coater is targeted as an example of an agricultural machine is shown, but a ditcher may also be targeted.

It is the top view which showed the agricultural working machine of the state which the working part moved to the advance work position. It is the left view which showed the agricultural working machine of the state which the working part moved to the advance work position. It is the top view which showed the agricultural working machine in the middle of the movement which reverses a working part. It is the top view which showed the agricultural machine of the state which the working part moved to the reverse work position. It is the top view which showed the relationship between the rotation member and the restraint / release apparatus for link members. It is the top view which showed a mode that the hydraulic cylinder contracted from the state of FIG. It is the top view which showed a mode that engagement of the engagement member which comprises the restraint / cancellation | release apparatus shown in FIG. 5 was cancelled | released. It is the top view which showed the agricultural machine of the state which the working part moved to the storing position. FIG. 9 is an elevational view of the rear side of FIG. 8.

Explanation of symbols

1 …… Agricultural working machine (spider coater) 10 …… Mounting part 13 …… Front frame,
22 …… Forward drive shaft, 23 …… Forward drive shaft, 30 …… Driving shaft,
40 ... Parallel link, 41 ... Link member, 42 ... Link member,
45 …… Rear frame, 50 …… Working part (spreading working part), 51 …… Transmission frame, 53 …… Rotating shaft,
70 …… Restraining / releasing device, 71 …… engaging member, 72 …… engaged portion, 73 …… releasing member, 74 …… operating member,
80 …… Restraining / releasing device, 81 …… engaged portion, 82 …… forward engaging member, 83 …… reverse engaging member, 85 …… release member,
100 …… Running aircraft

Claims (2)

A front frame having a mounting portion to be mounted on the rear portion of the traveling machine body, a plurality of link members swingably connected to the front frame, and a rear frame connected to the moving end side of each link member; After that, it has a transmission frame that is rotatably connected to a rotation shaft protruding from the frame, and that supports the working portion at the tip position.
In the agricultural work machine in which the transmission frame is rotatable about a rotation axis of the rear frame, and the work unit can rotate between a forward work position where the working part is in a forward work position and a reverse work position where the work part is in a backward work position.
A forward drive shaft that receives power from the traveling machine body and a backward drive shaft that protrudes to the rear frame side in the mounting portion are arranged in parallel in the traveling machine body width direction,
When the working part is moved to the forward working position, a forward driven shaft that can be connected to the forward drive shaft protrudes from the front frame side surface of the transmission frame, and from the opposite side surface, The reverse driven shaft that can be connected to the reverse drive shaft protrudes,
When the link member is in the most folded state,
When the transmission frame rotates about the rotation shaft and the working unit moves to the forward operation position, the forward driven shaft is connected to the forward drive shaft,
When the transmission frame rotates around the rotation shaft and the working unit moves to the reverse operation position, the reverse drive shaft is connected to the reverse drive shaft,
A bracket for rotatably supporting the link member from the front frame to the rear frame side is provided in parallel in the traveling machine body width direction. Of the two brackets, the bracket located on the folding side of the link member An agricultural working machine characterized in that an overhang length from the front frame is smaller than an overhang length of the bracket located on the opposite side from the front frame. The rotation shaft serving as the rotation center of the transmission frame is located on a straight line passing through a midpoint of a straight line passing through the forward drive shaft and a straight line passing through the reverse drive shaft,
The forward driven shaft and the reverse driven shaft are positioned on a straight line passing through a position that is a half of the distance between the forward drive shaft and the reverse drive shaft from the rotation shaft. The agricultural machine according to claim 1, wherein

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