JP5341822B2 - Work machine transmission structure - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To miniaturize a transmission mechanism for transmitting power from an engine to a hydraulic pump and traveling device, and an operation mechanism for operating it. <P>SOLUTION: A drive shaft 71 rotated and driven by the power of the engine 19 is interlocked and connected to a pump drive shaft 60 of the hydraulic pump, and each of a plurality of upstream-side gears 77 and 78 on the transmission upstream side in a transmission 21 is externally engaged and mounted in a state parallel with the drive shaft 71 along the core direction and in a state journaled relatively rotatably, and adjacent upstream-side gears 77 and 78 are interconnected so as to integrally rotate. A plurality of shift gears 86 and 87 on the downstream side of transmission are externally engaged and mounted to a driven shaft 75 integrally rotatably and slidably. A main clutch 72 is externally engaged and mounted to the drive shaft 71, and can be switched between the transmission state for transmitting the power of the drive shaft 71 to the upstream-side gear 77 positioned at one end side of the core direction and a blocking state for blocking the power transmission. <P>COPYRIGHT: (C)2012,JPO&amp;INPIT

Description

  The present invention includes a hydraulic pump in which power from the engine is transmitted to the traveling device via a main clutch and a gear-type transmission, and is driven by power from the engine to supply pressure oil to a hydraulic actuator. Relates to the transmission structure of the working machine.

Conventionally, in the working machine configured as described above, the power from the engine is transmitted to the drive shaft on the transmission upper side of the gear-type transmission via the belt transmission that also serves as the belt tension type clutch that constitutes the main clutch. In this transmission, the upper gear is fitted on the drive shaft so as to rotate integrally therewith, and the lower shift gear meshing with the upper gear can be rotated integrally with the driven shaft and slid in the axial direction by operating the shift operation member. It was configured to be freely fitted externally (see, for example, Patent Document 1).
Incidentally, the one described in Patent Document 1 has a configuration in which a working device is provided at the rear of the traveling machine body so as to be movable up and down by a hydraulic cylinder as a hydraulic actuator, and a hydraulic pump for supplying hydraulic oil to the hydraulic cylinder. ing.

  Although not described in Patent Document 1, a transmission device dedicated to driving a pump for transmitting engine power to a hydraulic pump is provided separately from a belt transmission device that transmits engine power to a gear-type transmission. It was the composition which comprises (for example, refer patent document 2).

JP-A-5-169998 JP 10-288150 A

  In the above conventional configuration, since the main clutch is configured by a belt tension type clutch, there is a clutch on / off operation structure for moving the tension pulley largely between the clutch on position and the clutch disengagement position and holding it at that position. In addition, a transmission device dedicated to driving the pump for transmitting the engine power to the hydraulic pump is required, so a transmission mechanism for transmitting the power from the engine to the hydraulic pump and the traveling device and There is a disadvantage that the operating mechanism for operating is enlarged.

  An object of the present invention is to provide a transmission mechanism for a working machine that can reduce the size of a transmission mechanism for transmitting power from an engine to a hydraulic pump and a traveling device and an operation mechanism for operating the transmission mechanism. It is in.

Transmission structure of the working machine according to the present invention, together with power from the engine is transmitted to the traveling device through the transmission of the main clutch and gear-type, pressure oil to drive has been hydraulic actuator by the power from the engine A transmission structure of a working machine provided with a hydraulic pump to be supplied , wherein a first characteristic configuration is that each of a plurality of upper gears on the transmission upper side in the transmission is driven to rotate by the power of the engine a drive shaft which is, together with the fitted is attached in a state where the upstream side gear and each in a state arranged along the axial direction of the drive shaft is axially supported relatively rotatably with respect to said drive shaft, coupled for rotation the upstream side gears with each other that they adjacent integrally and, a plurality of shift gear of the transmission downstream side of the speed change device, the operation of the rotatable therewith and shift operating member to the driven shaft More axial direction slidably fitted is mounted on the drive shaft and the pump drive shaft of the hydraulic pump is operatively connected via a relay shaft, the power reversal for the reverse gear in the transmission to the relay shaft The drive shaft and the driven shaft are arranged in a horizontal direction in a state where the drive gear is externally fitted so as to be relatively rotatable, the drive shaft is closer to the lower side than the driven shaft, and the relay shaft is Each of the drive shaft, the driven shaft, and the relay shaft is disposed in a transmission case in a state of being positioned above the drive shaft, and the main clutch is externally fitted to the drive shaft. is configured tell upper side gear switched between cutoff state of disconnecting the transmission state and the power transmission operably located in axial direction one end side of the plurality of the upstream side gears arranged along the axial direction of the power In the point.

  According to the first characteristic configuration, the drive shaft that is rotationally driven by the power of the engine and the pump drive shaft are interlocked and connected, so that the hydraulic pump is driven when the engine is operating.

  When the main clutch is switched to the disengaged state, the plurality of upper gears that are externally fitted to the drive shaft are externally fitted to the drive shaft so that they can rotate relative to each other directly or via needle bearings, etc. Even if the drive shaft is driven to rotate, the plurality of upper gears are not driven, so that no power is transmitted to the driven shaft.

  When the main clutch is switched to the transmission state, the plurality of upper gears are connected to rotate integrally, so that the rotational power of the drive shaft is connected to the plurality of upper gears via the upper gear positioned at one end in the axial direction. All the side gears are in a rotationally driven state, and in this state where all of the multiple upper gears are rotationally driven, the shift gear is slid and operated to selectively bite the multiple upper gears. As a result, the shifted rotational power is transmitted to the driven shaft.

  Thus, the drive shaft not only functions as a power transmission shaft for driving the hydraulic pump, but also serves as a support shaft for supporting the main clutch and a plurality of upper gears to which the power on the driven side of the main clutch is transmitted. A pump transmission shaft that is always driven while the engine is operating to drive the hydraulic pump, and a driven transmission shaft whose transmission state changes depending on whether the main clutch is engaged or not. The number of transmission shafts can be reduced and the transmission mechanism can be made more compact than those provided separately.

When the explanation is added, a cylindrical outer cylinder shaft as a driven transmission shaft whose transmission state changes depending on turning on and off of the main clutch is formed as a double cylinder structure that is externally fitted to the drive shaft so as to be relatively rotatable. Although it is possible to adopt a configuration in which a plurality of upper gears are externally fitted to the outer cylinder shaft by splines, the above configuration eliminates the need for a cylindrical outer cylinder shaft and the number of transmission shafts. Therefore, the transmission mechanism can be made compact.
Since the drive shaft and the pump drive shaft are interlocked and connected via a relay shaft, the relay shaft is always driven to rotate when the engine is in operation. The transmission gear can be externally fitted, and the transmission mechanism can be made compact by using both the shaft for supporting the power reversing gear for reverse shift and the relay shaft for driving the pump.
The drive shaft, the driven shaft, and the relay shaft are arranged in the lateral direction with the drive shaft closer to the lower side than the driven shaft, and the relay shaft is positioned above the drive shaft. Since each is installed in the transmission case, the size of the transmission case in the direction in which the drive shaft and driven shaft are aligned can be made compact by deploying the relay shaft using the space above the drive shaft. As a result, the transmission mechanism can be made compact.

  The main clutch is externally fitted to the drive shaft, and is configured to be freely switchable between a transmission state in which the power of the drive shaft is transmitted to the upper gear positioned at one end in the axial direction and a cutoff state in which the power transmission is cut off. The The main clutch is composed of, for example, a friction clutch or an interlocking clutch, etc. The clutch configured as described above is transmitted only by moving a friction plate, an interlocking member, or the like over a short distance in the axial direction. The operation can be switched between the state and the shut-off state, and the operation mechanism can be made compact compared to the belt tension clutch.

  Accordingly, it has become possible to provide a transmission structure for a work machine that can make the transmission mechanism for transmitting power from the engine to the hydraulic pump and the traveling device and the operation mechanism for operating the transmission mechanism compact.

  According to a second characteristic configuration of the present invention, in addition to the first characteristic configuration, the main clutch is configured by a multi-plate friction clutch.

According to the second feature configuration, the multi-plate friction type clutch is provided with a plurality of driving side friction plates and driven side friction plates, respectively, so that the contact area for transmission between the driving side friction plate and the driven side friction plate is reduced. The outer dimensions can be reduced while increasing the size, and the distance to move the friction plate in the axial direction can be shortened, so that the operating structure can be reduced , and the transmission mechanism can be made more compact. .

  In addition to the first feature configuration or the second feature configuration, the third feature configuration of the present invention is configured such that the engaged portion with which the shift operation member is engaged is an end portion on one axial direction of the driven shaft in the shift gear. It is in the point comprised and comprised in the state located in.

  According to the third characteristic configuration, the shift gear is provided in a state where the engaged portion is positioned at one end of the driven shaft in the axial direction, and the shift operation member is engaged with the engaged portion. The moving operation is performed in the axial direction of the driven shaft.

The shift gear is provided with, for example, two gear teeth having different gear diameters. However, when the engaged portion is positioned at an intermediate portion in the axial direction of the two gear teeth, the upper gear on which the two gear teeth are engaged is It is necessary to provide the shift gear in a state of being spaced apart in the axial direction than at least the width of the shift gear in the axial direction.
On the other hand, in the third characteristic configuration, since the engaged portion is located at the end on one side in the axial direction of the driven shaft, the two gear teeth are provided close to the axial direction, The upper gear with which the gear teeth are engaged only needs to be provided in a state separated by the axial width of the two gear teeth, compared to the case where the engaged portion is positioned between the two gear teeth. The shaft can be compactly arranged in the axial direction by the width of the engaging portion, whereby the transmission mechanism can be made compact.

  According to a fourth feature configuration of the present invention, in addition to the third feature configuration, each of the engaged portions of the plurality of shift gears is positioned at an end portion on the same side in the axial direction of the driven shaft. It is in a formed point.

  According to the fourth feature configuration, since each of the engaged portions in the plurality of shift gears is located at the end on the same side in the axial direction of the driven shaft, a plurality of shift operations to be engaged with each engaged portion. The members can be deployed close to each other, and the operation mechanism for operating them can be made compact.

The fifth characteristic configuration of the present invention, in addition to any one of the first feature structure to the fourth characterizing feature, a pair of the upstream side gear adjacent in said transmission apparatus, in a state of being close to the gear teeth portions, In addition, the axial direction of the drive shaft extends across the gear side walls located between the radially outer end portion where the gear tooth portion is formed and the radially inner end portion fitted on the drive shaft so as to be relatively rotatable. By connecting and attaching the connecting pins along the, the interlocking connection is made to rotate integrally.

  According to the fifth characteristic configuration, a simple structure in which the coupling pins are fitted and mounted across the gear side walls in a state where the gear teeth of the adjacent pair of upper gears are close to each other, the shaft core direction is wasted. A pair of upper gears that are interlocked and linked to rotate together can be deployed without gaps, and multiple upper gears can be arranged in the axial direction of the drive shaft. The transmission mechanism can be arranged in a compact manner, whereby the transmission mechanism can be made compact.

It is a whole side view of a riding type rice transplanter. It is a whole top view of a riding type rice transplanter. It is a cross-sectional top view of a mission case. It is a cross-sectional top view of a mission case. It is a cross-sectional plan view of the vicinity of the output shaft of a mission case. It is a side view which shows the linkage mechanism for gear shifting operation. It is a cross-sectional top view of a mission case. It is a side view of the front part of a mission case. It is a top view of the front part of a mission case. It is a side view of a linkage operation mechanism. It is a front view of a linkage operation mechanism. It is a vertical front view of a linkage operation mechanism. It is a cross-sectional top view of a linkage operation mechanism. It is a top view which shows a lever operation guide. It is a partial exploded perspective view of a linkage operation mechanism. It is a top view which shows the speed change operation state of a speed change lever. It is a figure which shows the correlation with a gear stage and a vehicle speed.

  Hereinafter, the case where the working machine transmission structure according to the present invention is applied to a riding type rice transplanter will be described with reference to the drawings.

  As shown in FIG. 1, a hydraulic cylinder 4 as an actuator that drives the link mechanism 3 and the link mechanism 3 up and down is provided at the rear of a traveling machine body A that includes a pair of left and right front wheels 1 and a pair of left and right rear wheels 2 as a traveling device. The seedling planting device 5 as a working device is supported at the rear part of the link mechanism 3, and a riding type rice transplanter as an example of a working device is configured.

  As shown in FIG. 1, the seedling planting device 5 includes a transmission case 6, a planting case 7 that is rotatably supported at the rear part of the transmission case 6, and a pair of plantings provided at both ends of the planting case 7. The arm 8, the grounding float 9, the seedling platform 10, and the like are configured. As the seedling platform 10 is driven to reciprocate laterally to the left and right, the planting case 7 is rotationally driven, and the seedling platform 10 The planting arm 8 is configured to alternately take out seedlings from the lower part and plant them on the rice field.

  As shown in FIG. 1, a hopper 12 for storing fertilizer and a feeding portion 13 are fixed to the rear side of the driver seat 11, and a blower 14 is provided below the driver seat 11. Further, the ground float 9 is provided with a groove forming device 15, and a hose 16 is connected across the feeding portion 13 and the groove forming device 15, and fertilizer is supplied from the hopper 12 along with the seedling planting as described above. The fertilizer is fed by a predetermined amount by the feed unit 13, and the fertilizer is supplied to the grooving device 15 through the hose 16 by the blower 14, and the fertilizer is supplied to the rice field through the grooving device 15. .

  As shown in FIG. 1, a transmission case 17A is fixed to the front part of the traveling machine body A, and an engine 19 is supported on a support frame 18 connected to the front part of the transmission case 17A. The right and left front axle cases 20 are connected to the right and left lateral sides of the mission case 17A, and the right and left front wheels 1 can be steered around the vertical axis of the right and left front axle cases 20. It is supported by.

Next, the transmission structure will be described.
As shown in FIGS. 3 to 5, the motive power of the engine 19 is transmitted to a drive shaft 71 provided in a transmission case 17 </ b> B for transmission that is connected to the front side of the transmission case 17 </ b> A via a transmission belt 70. The power of the drive shaft 71 is transmitted to the gear-type main transmission 21 as a travel transmission via the main clutch 72, and the power shifted by the main transmission 21 is transmitted to the front wheels via the auxiliary transmission 74. is transmitted to the 1 and rear wheels 2, whereas, is configured as a power that is the shift in the main transmission 21 is transmitted to the seedling planting apparatus 5 through the speed change device 50 and the planting clutch 57 between lines Yes.

  The transmission belt 70 is wound around an output pulley 70A provided on the output shaft 19a of the engine 19 and an input pulley 70B provided on the drive shaft 71 of the transmission case 17B. A cooling fan 70C is disposed outside the input pulley 70B and is coupled to the drive shaft 71 so as to be integrally rotatable. The outer case portion 17Ba of the transmission case 17B is bolt-connected to the inner case portion of the transmission case 17B, and a conical shape having the axis of the drive shaft 71 as a vertex at a portion located on the outer peripheral portion of the drive shaft 71 A portion 17BT is formed. Further, a conical portion 17BT having the apex of the speed change output shaft 75 as an apex is formed at a portion of the outer case portion 17Ba of the transmission case 17B where the speed change output shaft 75 is pivotally supported. The conical portion 17BT on the outer peripheral portion of the drive shaft 71 is partially connected. Radial ribs are provided on the outer peripheral surfaces of these conical portions 17BT and 17BT, and the conical portions 17BT and 17BT are configured to ensure the required strength while reducing the size of the outer case portion 17Ba. Has been.

  The input pulley 70B includes a pulley main body portion 70Ba formed in a conical shape along the outer surface of the conical portion 17BT of the outer case portion 17Ba, and a belt winding portion 70Bb disposed on the outer periphery of the pulley main body portion 70Ba. It is integrally formed. A conical recess 70Bc is formed inside the pulley body 70Ba, and the input pulley 70B is connected to the drive shaft 71 in a state where a part of the conical portion 17BT of the outer case portion 17Ba enters the recess 70Bc. ing. As a result, a space Q is formed in which the distance in the axial direction of the drive shaft 71 between the cooling pulley 70C and the outer peripheral side of the input pulley 70B increases, and the input pulley 70B is less likely to be blocked by this space Q. Thus, the cooling air by the cooling fan 70C is circulated to the lateral outer side of the transmission case 17B so that the lateral outer surface of the transmission case 17B can be efficiently cooled with a compact structure.

  The main transmission 21 has a traveling shift state of the traveling machine body A in a low-speed forward shift state (hereinafter referred to as forward first speed), a medium-speed forward shift state (hereinafter referred to as forward second speed), and a high-speed forward shift state (hereinafter referred to as forward speed). , The third forward speed) and the reverse gear shift state (hereinafter referred to as the reverse gear state), that is, it is configured to be freely switchable between four shift speeds of three forward speeds and one reverse speed.

That is, as shown in FIG. 3, in the main transmission 21, the transmission case 17B and the drive shaft 71, the transmission output shaft 75, and the reverse rotation relay shaft 76 are arranged in a direction in which the rotation axis is aligned horizontally. It is supported rotatably. Each of the two first and second upper gears 77, 78 is aligned with the drive shaft 71 along the axial direction of the drive shaft 71, and each of the first and second upper gears 77. , 78 are externally fitted and mounted so as to be rotatably supported relative to the drive shaft 71 via a needle bearing 149, and the two first and second upper gears 77, 78 are integrated with each other. It is provided in an interlocked connection to rotate.

Of the two first and second upper gears 77, 78, the upper first gear 77 located on the main clutch 72 side has a forward first speed drive gear portion 79 as a gear tooth portion and a forward first gear 77. A drive gear portion 80 for the second speed is provided, and the upper second gear 78 located on the opposite side of the main clutch 72 has a drive gear portion 81 for the third forward speed and a reverse drive as a gear tooth portion. A gear portion 82 is provided, and the reverse drive gear portion 82 is provided in a state of being engaged with a relay gear 84 that is rotatably supported by a reverse rotation relay shaft 76 via a bearing 83.

The two first and second upper gears 77, 78 are adjacent to each other, the driving gear portion 80 for the second forward speed of the upper first gear 77 and the third forward speed of the upper second gear 78. By connecting and attaching a connecting pin 85 along the axial direction of the drive shaft 71 across the drive gear portion 81, the drive gear portion 81 is interlocked and connected to rotate integrally.

When the explanation is added, two adjacent first and second upper gears 77 and 78 include a driving gear portion 80 as a gear tooth portion for forward second speed of the upper first gear 77 and an upper first gear 77. Positioned between the drive gear portion 81 for forward third speed as a gear tooth portion of the 2 gear 78 and between the radially outer end portion and the radially inner end portion of the drive gear portion 80. Connecting pin along the axial direction of the drive shaft 71 across the gear side wall portion and the gear side wall portion positioned between the radially outer end portion and the radially inner end portion of the drive gear portion 81 for the third forward speed. By fitting and mounting 85, it is configured to be interlocked to be integrally rotated.

Further, two first and second shift gears 86 and 87 are externally fitted to the speed change output shaft 75 so as to be integrally rotatable and slidable in the axial direction. Of the two first and second shift gears 86, 87, the first shift gear 86 located on the main clutch 72 side includes a driven gear portion 88 for forward first speed and a driven gear portion 89 for forward second speed. The second shift gear 87 provided on the opposite side of the main clutch 72 is provided with a driven gear portion 90 for the third forward speed and a drive gear portion 91 for the reverse movement.

The first shift gear 86, first speed position location of the driven gear portion 88 for forward first speed with each other bite and the driving gear portion 79 of the forward first speed, the driven gear portion 89 for forward second speed is the second forward second speed position location mutually biting the drive gear unit 80 for fast slide operably provided at three positions of any of the driven gear portion 88 and 89 is not Awa also bite the neutral position, the second shift gear 87, the third forward third speed position location of the driven gear portion 90 for fast with each other bite and the driving gear 81 for forward third speed, the reverse position of the driven gear portion 91 with each other bite the relay gear 84 for reverse for reverse, one of the driven The gear portions 90 and 91 are also slidably provided at three neutral positions where they do not bite.

  In other words, when the second shift gear 87 is operated to the neutral position and the first shift gear 86 is operated to the first speed position, the first forward gear is switched, the second shift gear 87 is operated to the neutral position and the first shift gear 86 is moved to the first position. When it is operated to the 2nd speed position, it switches to the forward 2nd speed, when the 1st shift gear 86 is operated to the neutral position and the 2nd shift gear 87 is operated to the 3rd speed position, it switches to the 3rd forward speed, and the 1st shift gear 86 is When the neutral position is operated and the second shift gear 87 is operated to the reverse position, the reverse state is switched.

As shown in FIG. 7, the first shift operating member 92 for moving the first shift gear 86 in the axial direction is supported by the mission case 17A so as to be slidable, and is held by the ball detent mechanism B. The operation rod 94 is integrally provided, and can be switched to the three positions by sliding the operation rod 94. Further, the second shift operation member 93 for moving the second shift gear 87 in the axial direction is also an operation rod 95 configured to hold the position by the ball detent mechanism B, similarly to the first shift operation member 92. And is configured to be switchable to the three positions by sliding the operation rod 95.
The operating rods 94 and 95 are provided so as to protrude outward from the transmission case 17B. The operating structure of the operating rods 94 and 95 will be described later.

In the first and second shift gears 86 and 87, the engaged portion k with which the first and second shift operation members 92 and 93 are engaged is positioned at the end on one side in the axial direction of the transmission output shaft 75. It is configured for. In other words, each of the engaged portions k of the two shift gears 86 and 87 is located at the end on the same side in the axial direction of the speed change output shaft 75 (the left end in the case shown in FIG. 7). It is formed with.
As shown in FIG. 3, when the shift gear 86 is in the neutral position, the engaged gear k of the shift gear 86 is a drive gear portion for the first forward speed as viewed in a direction perpendicular to the axis of the transmission output shaft 75. 79 is deployed in an overlapping state. Further, when the second shift gear 87 is in the neutral position, the engaged portion k of the second shift gear 87 overlaps the drive gear portion 81 for the third forward speed as viewed in a direction orthogonal to the axis of the transmission output shaft 75. It is deployed in a state to do.

As shown in FIG. 17, in the main transmission 21, the difference Δαa between the speed ratio α3 at the third forward speed (F3) and the speed ratio α2 at the second forward speed (F2) is the same as that at the second forward speed (F2). It is configured to be smaller than the difference Δαb between the speed ratio α2 and the speed ratio α1 at the first forward speed (F1).
In other words, as shown in FIG. 17, the straight line L connecting the origin and the third forward speed (F3) , in other words, the speed ratio for each of the plurality of speed stages is set in a state where the speed ratio difference is constant. Compared to the case, the transmission gear ratio α2 at the second forward speed (F2) is set to be larger, and the transmission gear ratio α1 at the first forward speed (F1) is set to be smaller.

  By the way, the gear ratio of the sub-transmission device 74 is set so that the sub-transmission device 74 is switched to the high speed side so that the traveling speed is suitable for road travel rather than traveling on the field. Therefore, during the work in the field, the sub-transmission device 74 is maintained in the state switched to the low speed side.

Next, the shift operation structure of the main transmission 21 will be described.
As shown in FIGS. 2 and 6, a shift lever 99 for operating the main transmission 21 is provided in the guide hole 152 at the left side of the control handle 98 in the handle post 97 erected on the front of the aircraft control unit 96. It is provided so that it can be operated along.
As shown in FIG. 16, the speed change lever 99 is a low speed forward operation position for switching the main transmission 21 to the first forward speed (hereinafter referred to as forward first speed position (F1)), and a medium speed for switching to the second forward speed. A forward operation position (hereinafter referred to as forward second speed position (F2)) and a high-speed forward operation position (hereinafter referred to as forward third speed position (F3)) for switching to forward third speed are configured to be switchable. In addition, the reverse operation position (R) for switching the main transmission 21 to the reverse operation state and the third forward speed position (F3) are opposed to each other in a state where they can be switched with each other in accordance with the movement operation along the longitudinal direction of the body. Is provided.

  The transmission lever 99 includes a longitudinal slimming portion 99a provided in a state in which an elongated rectangular opening 97A formed on the upper surface of the lateral side portion of the handle post 97 is communicated vertically, and the longitudinal slimming portion 99a. And a grip portion 99b provided at the extended end portion. The vertical slimming portion 99a of the transmission lever 99 extends obliquely upward and laterally upward from the communicating portion with respect to the opening 97A, is bent at the extension end, and extends obliquely upward and rearward. The grip 99b of the speed change lever 99 is provided in the vicinity of the outer peripheral end of the steering handle 98 so as to overlap the steering handle 98 in a side view. As a result, the grip portion 99b of the speed change lever 99 is operated in the vicinity of the control handle 98 while the periphery of the handle post 97 is made compact without providing a lever guide or the like protruding to the side or rear side of the handle post 97. It can be deployed at an easy position.

  The speed change lever 99 is supported so as to be swingable in the left and right direction of the machine body and the front and rear direction of the machine body, and the speed change lever 99 is operated in the forward direction while being swung leftward from the neutral position N. The linkage operation mechanism 101 that links the transmission lever 99 and the main transmission 21 is switched to the forward third speed position (F3) by switching to the reverse operation position (R) when operated backward. Is provided.

Hereinafter, the linkage operation mechanism 101 will be described.
As shown in FIG. 6, the linkage operation mechanism 101 is provided in a state of being located at a base end side portion of the speed change lever 99 inside the handle post 97. Then, as shown in FIGS. 10 to 12 and 15, the support member 100 having a substantially U-shape in a side view and fixed to the frame body 102 </ b> A extending from the vertical frame 102 of the handle post 97 extends along the left-right direction of the machine body. Thus, the support shaft 103 is installed and supported. A first boss member 104 is rotatably supported on the support shaft 103 to rotatably support the transmission lever 99 around the horizontal axis X1. The connection is integrally fixed to the first boss member 104. A second boss member 106 is connected to the upper end of the tool 105 for supporting the speed change lever 99 so as to be rotatable about the front and rear axis X2.

  A round bar is bent into a substantially L-shape, and an upper portion 107A in the front-and-back orientation is fitted into the second boss member 106 so as to be relatively rotatable, and a lower portion 107B is directed downward in the up-and-down posture. An extended interlocking operation member 107 is provided, and a connection member 153 fixedly connected to the lower end portion of the speed change lever 99 is integrally fixedly connected to the interlocking operation member 107. That is, the interlocking operation member 107 is configured to be swung integrally with the speed change lever 99.

  Therefore, the speed change lever 99 can be swung in the longitudinal direction of the machine body by turning around the axis of the support shaft 103 (horizontal axis X1), and the axis of the second boss member 106 (front and rear axis X2). It is supported by the support member 100 so as to be swingable in the left-right direction of the machine body by turning around.

As shown in FIGS. 10 to 13, 15, the first support shaft 103 is supported at the left and right sides of the first boss member 104 so as to be rotatable around the horizontal axis X <b> 1 of the support shaft 103. A linkage member 109 and a second linkage member 108 are provided.
The first linkage member 109 is pivotally supported by a support shaft 103 so as to be pivotable, and an engagement action portion 109B extending downward from the pivotal support 109A and bent into a substantially L shape. And it comprises the operation part 109C which extends back from the pivot part 109A integrally, and the one end side of the push-pull rod 111 is pivotally connected. Similarly to the first linkage member 109, the second linkage member 108 includes a pivot portion 108A, an engagement action portion 108B, and an operation portion 108C in which one end side of the push-pull rod 110 is pivotally connected.

  As shown in FIGS. 7 to 9, a rotation operation shaft 112 is provided on the outer side of the mission case 17A in the vicinity of the operation rod 94 for shift operation, and is rotatable about its own axis. The other end of the push-pull rod 110 is pivotally connected to an operation arm 113 provided on one side of the moving operation shaft 112, and the other side of the rotation operation shaft 112 is engaged with the operated portion 94 </ b> A of the operation rod 94. An operation tool 114 is provided, and is configured such that as the push-pull rod 110 is pushed and pulled up and down, the rotation operation shaft 112 rotates and the operation rod 94 can be slid.

  Similarly to the operation rod 94, the operation rod 95 for the shift operation is also provided with a rotation operation shaft 115 that is rotatable around its own axis, and an operation arm 116 in which the other end side of the push-pull rod 111 is pivotally connected. An operating tool 117 that locks the operated portion 95A of the operating rod 95 is provided. As the push-pull rod 111 is pushed up and down, the turning operation shaft 115 rotates to move the operating rod 95. It is configured to be slidable.

As shown in FIGS. 11 and 12, the first linkage member 109 and the second linkage member 108 are formed by bending plate members to form engagement action portions 108B and 109B and operation portions 108C and 109C, respectively. The engagement action portion 109B of the linkage member 109 and the engagement action portion 108B of the second linkage member 108 are arranged in a state where the lower end portions thereof face each other, and the interlock operation member 107 swings left and right. Engagement recesses 119 and 120 that are engaged and engaged by moving are formed. Further, rod-like members 121 and 122 formed by bending round bars along the inner edge portions of the engaging recesses 119 and 120 with which the interlocking operation member 107 engages are integrated with the respective engaging action portions 108B and 109B. It is fixed by welding.
As shown in FIG. 13, the first linkage member 109 and the second linkage member 108 (specifically, rod-shaped members 121 and 122 integrally welded to them) are in the neutral position N. It is provided in a form overlapping with the operation member 107 in the longitudinal direction of the machine body (up and down direction in FIG. 13).

As shown in FIG. 14, on the bottom surface portion 100A of the lower portion of the support member 100, a left / right movement path L1 allowing operation in the left / right direction of the machine body from the neutral position N of the interlocking operation member 107, and a left side of the left / right movement path L1 Lever guide hole 123 provided with a left front / rear movement path L2 allowing operation in the longitudinal direction of the machine from the end position and a right front / rear movement path L3 allowing operation in the longitudinal direction of the machine from the right end position of the left / right movement path L1. The lever operation guide G is configured by the bottom surface portion 100 </ b> A of the support member 100.

  However, the moving direction of the interlocking operation member 107 and the moving direction of the speed change lever 99 are opposite to each other. When the speed change lever 99 is swung leftward, the interlocking operation member 107 swings rightward. When 99 is swung forward, the interlocking operation member 107 is swung backward.

In the linkage operation mechanism 101 having the above-described configuration, the linkage member 107 is operated in the longitudinal direction while the linkage operation member 107 is swung from the neutral position N to the right end position of the left-right movement path L1, whereby the first linkage member 109 is linked. The second linkage member 108 is operated in an interlocked manner by being operated and operated in the longitudinal direction of the body while the interlocking operation member 107 is swung from the neutral position N to the left end position of the left-right movement path L1. The main transmission 21 is switched between the forward third speed and the reverse state by the operation of the first linkage member 109, and the forward second speed and the forward first speed by the operation of the second linkage member 108. Can be switched to.

Further, the reverse transmission state detection sensor S that detects that the main transmission 21 has been switched to the reverse drive state detects the first linkage member 109 in the linkage operation mechanism 101, so that the main transmission 21 is in the reverse drive state. It is comprised so that it may detect that it switched to.
That is, as shown in FIG. 10, the reverse state detection sensor S is provided at the front side portion of the first linkage member 109 while being supported by the support member 100, and the first linkage member 109 is swung forward. Then, the first linkage member 109 comes into contact with the reverse state detection sensor S, and this is detected by the reverse state detection sensor S. In this way, the first linkage member 109 is also used as a detection action member of the reverse state detection sensor S.

When the rear Susumujo state is detected by the reverse state detection sensor S, for the hydraulic cylinder 4 so that the control device H as control means for controlling operation of each section raises the seedling planting apparatus 5 to the maximum raised position The operation of the hydraulic control valve V is controlled. Although not described in detail, the control device H detects the amount of vertical movement based on the contact pressure fluctuation of the center grounding float 9 when working and running in the field, and increases the height of the seedling planting device 5 relative to the rice field. It is configured to perform up-and-down control to control the hydraulic cylinder 4 so as to maintain the set value.

In a state where the interlocking operation member 107 (transmission lever 99) is positioned on the left and right movement path L1, the neutral position can be obtained from both sides in the left and right direction in a state where the manual operation can be performed on the left and right movement path L1 against the urging force When the interlocking operation member 107 returns to the neutral position N , the neutral biasing mechanism 125 that presses and biases to return to N switches to the operating state, and interlocks against the biasing force of the neutral biasing mechanism 125. A movement restricting member 124 that switches in conjunction with the neutral urging mechanism 125 is provided so that when the operating member 107 is operated to the left end position or the right end position of the left and right movement path L1, the operation biasing member 107 is switched to the inactive state. It has been.

Next, the neutral urging mechanism 125 will be described.
As shown in FIGS. 12, 13, and 15, substantially U-shaped brackets 126 are fixed to the outer sides of the vertical wall portions 100 </ b> B on the left and right sides of the support member 100, and the horizontal axis is attached to each bracket 126. Each of the swing arms 127 is pivotally connected so as to be swingable around X3. At the lower end of each swing arm 127, a round bar is formed in a substantially U shape so that it extends to the outer side in the front-rear direction of the support member 100 and the front-rear center part protrudes toward the interlocking operation member 107. The contact restricting members 128 are integrally fixed, and the contact restricting members 128 are pulled in the direction in which the contact restricting members 128 approach each other across the front and rear side portions of the contact restricting members 128 in the swing arms 127 on both the left and right sides. An energizing coil spring 129 is stretched.

The contact restricting members 128 on both the left and right sides are pulled and urged toward each other by the urging force of the coil spring 129, and the swing arm 127 is in contact with the vertical wall portion 100B and further swing is controlled. in, and is configured to be able to position held at the neutral position N to close the interlocking operation member 107 in the neutral position N.
Further, when the interlocking operation member 107 is moved rightward or leftward from the neutral position N, the interlocking operation member 107 is urged to return to the neutral position N by the urging force of the coil spring 129. However, the biasing force of the coil spring 129 is set to be small enough to manually operate the shift lever 99 in the left-right direction against the biasing force.

And in the state where the interlocking operation member 107 is at the neutral position N , the first linkage member 109 and the second linkage member 109 are inserted into the upper and lower middle portions of the left and right swing arms 127 through the insertion holes 130 formed in the support member 100. The first engaging member 109 and the second connecting member 108 are restrained from swinging in the front-rear direction by engaging and engaging with engaging recesses 119, 120 formed in the engaging action portions 108B, 109B of the connecting member 108, respectively. The movement restricting member 124 is provided in a state of being integrally fixed.

As described above, since the movement restricting member 124 is fixed to the swing arm 127, the interlocking operation member 107 resists the urging force of the neutral urging mechanism 125 so that the interlocking operation member 107 is located at the left end position or the right end of the left / right moving path L1. When it is operated to the position, it swings in conjunction with it, the fitting engagement with the engaging recesses 119 , 120 is released, and one of the first linkage member 109 and the second linkage member 108 corresponds. It will switch to the non-operation state which permits the rocking | fluctuation of the front-back direction.

Therefore, the movement restricting member 124 is switched to the operating state when the shift lever 99 is returned to the neutral position N , and the shift lever 99 is operated against the biasing force of the neutral biasing mechanism 125. It is configured to be switched in conjunction with the neutral urging mechanism 125 so that when it is operated to the left end position or the right end position of the left and right movement path L1 , it is switched to the non-actuated state.

The main clutch 72 is connected to the upper first gear 77 located on one end side in the axial direction of the two first and second upper gears 77, 78 lining the power of the drive shaft 71 along the axial direction. It is composed of a multi-plate friction clutch that can be switched between a transmission state for transmission and a cutoff state for interrupting power transmission.

In other words, the main clutch 72 includes a plurality of drive-side friction plates 72b that can rotate integrally with the drive-side member 72a that rotates integrally with the drive shaft 71 and that can move in the axial direction of the drive shaft 71. Is provided. Further, a driven-side member 72c is provided by being spline-fitted to the upper-side first gear 77 so as to be integrally rotatable and movable in the axial direction of the drive shaft 71. The driven-side member 72c is integrally rotatable. In addition, a plurality of driven friction plates 72d are provided so as to be movable in the axial direction of the drive shaft 71. And these drive side friction plates 72b and driven side friction plates 72d are arranged in an alternately overlapping state, and the driven side member 72c is moved and urged in the axial direction by the urging force of the compression spring 131, The drive side and driven side friction plates 72b and 72d are brought into pressure contact with each other to switch to the transmission state. That is, the clutch is biased by the biasing force of the compression spring 131.

  The drive-side member 72a of the main clutch 72 has a conical portion 72aT whose apex is the axis of the drive shaft 71 on the outer portion of the main clutch 72 in a state of facing the conical portion 17BT of the outer case portion 17Ba with a predetermined gap. Is formed.

Then, the clutch is switched to the clutch disengaged state by the stepping operation of the operation pedal 132 provided in the body control unit 96 of the traveling body A, and the clutch is engaged when the stepping operation of the operation pedal 132 is released.

That is, as shown in FIGS. 6, 8, and 9, a laterally rotating support shaft 133 that supports the operation pedal 132 so as to freely rotate is extended in the left-right direction, and the swing provided on the rotating support shaft 133 is provided. The moving arm 134 and the clutch operating arm 135 are linked and linked by a push-pull rod 136 that is pivotally connected. The clutch operation arm 135 is rotatably supported by a rotation support shaft 150 that is rotatably supported around the longitudinal axis inside the mission case 17A, and by depressing the operation pedal 132, When the clutch operation arm 135 is rotated, the driven member 72c is operated to move in the opposite direction against the urging force of the compression spring 131 by the operation tool 151 provided on the rotation support shaft 150, and the main clutch 72 is configured to be able to cut and operate.

  Further, when the operation pedal 132 is released, the operation pedal 132 is configured to return to the original position by the urging force of the return spring 137, and the main clutch 72 is engaged with the clutch by the urging force of the compression spring 131. Will return to.

Next, a structure for transmitting the output of the main transmission 21 to the front wheels 1 and the rear wheels 2 will be described.
As shown in FIG. 4, the transmission shaft 22 on the upper side of the transmission is rotatably supported by the transmission case 17A via the bearing 23, and the transmission output shaft 75 of the main transmission 21 and the transmission shaft 22 on the upper side of the transmission are connected. They are connected by a spline structure.
A low-speed gear 25 and a high-speed gear 24 are fixed to the transmission shaft on the upper side of the transmission, and a shift gear 27 is externally fitted to the transmission shaft 26 on the lower side of the transmission by a spline structure so as to be integrally rotatable and slidable. When the shift gear 27 is slid and engaged with the low-speed gear 25 and the high-speed gear 24, the power of the transmission shaft 22 on the upper shift side is shifted in two steps to be transmitted to the transmission shaft 26 on the lower shift side. As a result, a sub-transmission device 74 is configured that is capable of shifting the output of the main transmission 21 in two steps of high and low.
The sub-transmission device 74 is configured to be switched between a high speed and a low speed by operating a switching lever (not shown) for the sub-transmission device.

  As shown in FIG. 4, a pair of transmission shafts 28 are arranged to face each other across the right and left front axle cases 20, and a differential mechanism 29 is provided between the pair of transmission shafts 28. The case 29a is supported by the mission case 17A via a bearing 33 so as to be rotatable. A transmission gear 30 is fixed to the transmission shaft 26 on the lower shift side, and a transmission gear 31 fixed to the case 29 a of the differential mechanism 29 is engaged with the transmission gear 30.

  A cylindrical member 32 is externally fitted to one transmission shaft 28 so as to be integrally rotatable and slidable by a key structure, and an operation shaft 41 that slides the cylindrical member 32 and a differential lock pedal (see FIG. Not shown). When the differential lock pedal is stepped on, the operation shaft 41 is rotated, the cylindrical member 32 is slid to be engaged with the end of the case 29a of the differential mechanism 29, and the cylindrical member 32 is engaged with the end of the case 29a of the differential mechanism 29. The differential mechanism 29 can be brought into a locked state by being engaged with the portion.

  Further, the traveling output shaft 34 is provided at the rear portion of the mission case 17A so as to protrude rearward, and the bevel gear 35 fixed to the case 29a of the differential mechanism 29 is engaged with the bevel gear 36 provided on the traveling output shaft 34. Yes. As shown in FIG. 1, a rear axle case 37 that supports the rear wheel 2 is provided, and a transmission shaft 38 is connected across a travel output shaft 34 and an input shaft (not shown) of the rear axle case 37. Yes.

  That is, the power of the transmission output shaft 75 of the main transmission 21 is transmitted to the front wheels 1 through the auxiliary transmission 74, the differential mechanism 29, and the transmission shaft 28, and the case 29a, the travel output shaft 34, and the transmission shaft of the differential mechanism 29 are transmitted. A traveling transmission system is configured to be transmitted to the rear wheel 2 via 38.

As shown in FIG. 4, a plurality of friction plates 39 are provided between the inner wall of the mission case 17 </ b> A and the travel output shaft 34, and the disk-shaped operation member 40 is rotatable relative to the travel output shaft 34. And an operation shaft 42 for sliding the operation member 40 is provided.
Then, the rotation support shaft 133 of the operation pedal 132 and the operation shaft 42 are linked and linked through a link mechanism (not shown), and when the operation pedal 132 is stepped on, the main clutch 72 is operated in a disengaged state, and the operation The shaft 42 is rotated, the operation member 40 is slid, the operation member 40 presses the friction plate 39, and the travel output shaft 34 is braked. When the travel output shaft 34 is braked, the front wheel 1 is braked via the differential mechanism 29 and the transmission shaft 28, and the rear wheel 2 is braked via the travel output shaft 34 and the transmission shaft 38.

Next, the transmission structure to the seedling planting device 5 will be described.
As shown in FIG. 4, a cylindrical upper transmission gear 43 is externally fitted to the transmission upper transmission shaft 22 via a one-way clutch 44, and the one-way clutch 44 moves forward power of the transmission output shaft 75. Is transmitted to the upper transmission gear 43, and the reverse power is not transmitted to the upper transmission gear 43.

  The lower transmission gear 45 and the six shifting upper transmission gears 46 are connected to each other so as to rotate integrally, and the lower driven gear 45 and the six shifting transmission gears 46 are connected to the lower transmission shaft. 26, the upper transmission gear 43 and the lower driven gear 45 are engaged and interlocked with each other.

Then, as shown in FIG. 5, six shifting lower transmission gears 48 are externally fitted on the selected power output shaft 47 arranged in parallel with the lower transmission shaft 26 so as to be relatively rotatable, so that six shifting gears are provided. Each of the upper transmission gear 46 and the lower shift transmission gear 48 is engaged, and one of the six lower shift transmission gears 48 can be selected to be connected to and disconnected from the selected power output shaft 47. An operating rod 49 is provided.
The six speed upper side transmission gear 46 and the gear downstream side transmission gear 48 and the operating rod 49, etc., are configured strains among speed change device 50, among the six transmission downstream side transmission gear 48 by the operating rod 49 By selecting one of these and connecting it to the selected power output shaft 47, the forward power of the speed change output shaft 75 is shifted to six stages and transmitted to the selected power output shaft 47.

An output shaft 51 is provided at the upper part of the rear portion of the transmission case 17A and protrudes rearward. A bevel gear 52 externally fitted to the output shaft 51 so as to be relatively rotatable is engaged with a bevel gear 53 fixed to the transmission shaft 47. Yes. The shift member 54 is externally fitted to the output shaft 51 so as to be rotatable and slidable integrally with the output shaft 51 by a spline structure, and a spring 55 is provided to bias the shift member 54 to the occlusal side with the bevel gear 52, and the shift member 54 is separated from the bevel gear 52. An operation rod 56 for operation is provided, and a planting clutch 57 that can transmit and shut the power of the speed change output shaft 75 to and from the output shaft 51 is configured. As shown in FIG. 1, a transmission shaft 58 is connected across the output shaft 51 and an input shaft (not shown) of the seedling planting device 5.
Thus, the power of the transmission shaft 26, strain between the speed change device 50, the bevel gear 52 and 53, the planting clutch 57, it is configured to be transmitted to the seedling planting apparatus 5 via the output shaft 51 and the transmission shaft 58 Yes.

Next, the transmission structure of the hydraulic pump 59 will be described.
As shown in FIGS. 3 and 4, the mission case 17 </ b> A is provided with a driven gear 138 that can rotate integrally with the reverse rotation relay shaft 76, and the drive shaft 71 is provided with a drive gear 139 that meshes with the driven gear 138. ing. Further, the pump output shaft 140 is provided in a state of being located on the side of the reverse rotation relay shaft 76, and the reverse rotation relay shaft 76 and the pump output shaft 140 are interlocked and connected via the speed increasing gear mechanism 141. Yes.

In the transmission case 17A, a pump drive shaft 60 is disposed across the pump output shaft 140 and the input shaft 59a of the hydraulic pump 59. The pump output shaft 140 and the pump drive shaft 60 are cylindrical. The spline structure is connected via a connecting member 61, and the input shaft 59 a of the hydraulic pump 59 and the pump drive shaft 60 are connected via a cylindrical connecting member 62.
In this way, the power of the engine 19 is transmitted to the pump drive shaft 60 via the drive shaft 71, the reverse rotation relay shaft 76, the speed increasing gear mechanism 141, and the pump output shaft 140, and the engine 19 is operating. The hydraulic pump 59 is always driven during the interval.

  As shown in FIG. 8, in a side view of the mission case 17A, the drive shaft 71 and the transmission output shaft 75 are connected to each other in a state where the drive shaft 71 is closer to the lower side on the front side than the transmission output shaft 75. Are arranged horizontally in the horizontal direction of the fuselage and the reverse rotation relay shaft 76 is positioned above the drive shaft 71, the drive shaft 71, the transmission output shaft 75, and the reverse rotation relay shaft 76 are each a transmission case. 17 is deployed.

[Another embodiment]
(1) In the above-described embodiment, the engaged portions k of the two first and second shift gears 86 and 87 are positioned at the end portions on the same side in the axial direction of the transmission output shaft 75. However, instead of such a configuration, each of the engaged portions k of the two first and second shift gears 86 and 87 are opposite to each other in the axial direction of the transmission output shaft 75. It may be located at the end of the side.

In the above embodiment, the engaged portion k with which the first and second shift operating members 92 and 93 are engaged is the end on the one side in the axial direction of the speed change output shaft 75 of the first and second shift gears 86 and 87. However, instead of such a configuration, the engaged portion k is provided in a state positioned between the first and second shift gears 86 and 87. It is good.

(2) In the above embodiment, the first and second upper gears 77 and 78 are interlocked to rotate integrally by fitting and connecting the connecting pin 85 along the axial direction of the drive shaft 71 across the gear side walls. Although what is connected was shown, the 1st and 2nd upper side gears 77 and 78 may be interlocked so that it may rotate together by spline fitting, and the gear side wall part forms a nail, etc. But you can. In the above embodiment, the first and second upper gears 77 and 78 are externally fitted to the drive shaft 71 via the needle bearing 149. However, the needle bearing 149 is eliminated and the drive shaft is directly attached. 71 may be externally fitted.

(3) In the above embodiment, the main clutch 72 is shown as a multi-plate friction clutch. However, the main clutch 72 is a clutch having various configurations such as a single-plate friction clutch and an interlocking pawl clutch. Can be used.

(4) In the above-described embodiment, the drive shaft 71, the transmission output shaft 75, and the reverse rotation relay shaft 76 are each rotatably supported in a state where the rotation axis is aligned in the horizontal direction with the horizontal axis direction of the body. Although shown, instead of such a configuration, the drive shaft 71, the transmission output shaft 75, and the reverse relay shaft 76 are each rotatably supported in a direction in which the rotation shaft cores are aligned in the longitudinal direction of the machine body. It is good.

(5) In the above embodiment, the hydraulic cylinder 4 is shown as the hydraulic actuator, but various hydraulic actuators such as a hydraulic steering mechanism and a hydraulic motor may be used instead of or in addition to the hydraulic cylinder 4.

(6) Although the rice transplanter is shown as the work machine in the above embodiment, the present invention is not limited to the rice transplanter but can be applied to a direct seeding machine and other work machines.

  The present invention can be applied to, for example, a working machine equipped with an engine, a gear-type transmission, a hydraulic pump, or the like, such as a rice transplanter or a direct seeder.

DESCRIPTION OF SYMBOLS 1, 2 Traveling devices 4 Hydraulic actuator 17 Transmission case 19 Engine 21 Transmission 59 Hydraulic pump 60 Pump drive shaft 71 Drive shaft 72 Main clutch 75 Drive shaft 76 Relay shaft 77, 78 Upper gear 80, 81 Gear tooth portion 84 Power reversal Gear 85 connecting pin 86, 87 shift gear 92, 93 shift operation member k engaged portion

Claims (5)

With power from the engine is transmitted to the traveling device through the transmission of the main clutch and gear-type, the working machine hydraulic pump is provided for supplying the pressure oil to drive has been hydraulic actuator by the power from the engine a of the transmission structure,
Each of the plurality of upper side gear of the transmission upper side of the speed change device, the drive shaft that is driven to rotate by power of the engine, and each said upper side in a state arranged along the axial direction of the drive shaft with gear is fitted mounted in a state that is relatively rotatably supported with respect to the drive shaft is coupled for rotation the upstream side gears with each other that they adjacent integrally and, transmission downstream side in the transmission The plurality of shift gears are externally fitted to the driven shaft so as to be rotatable integrally with the driven shaft and slidably movable in the axial direction by operation of the shift operation member.
The drive shaft and the pump drive shaft of the hydraulic pump are interlocked and connected via a relay shaft, and a power reversing gear for reverse shift in the transmission is fitted on the relay shaft so as to be relatively rotatable.
In a state where the drive shaft is closer to the lower side than the driven shaft, the drive shaft and the driven shaft are aligned in the horizontal direction, and the relay shaft is located above the drive shaft, and the drive shaft Each of the driven shaft and the relay shaft is disposed in a transmission case,
Said main clutch is being fitted attached to the drive shaft, transmitting the upstream side gear is located in axial direction one end side of the plurality of the upstream side gears arranged along the power of the drive shaft in the axial direction A work machine transmission structure configured to be freely switchable between a transmission state and a cut-off state that interrupts power transmission.   The transmission structure for a working machine according to claim 1, wherein the main clutch is a multi-plate friction clutch.   3. The work machine according to claim 1, wherein the engaged portion to which the shift operation member is engaged is provided in a state where the engaged portion is positioned at an end portion on one side in the axial direction of the driven shaft of the shift gear. Transmission structure.   The transmission structure for a working machine according to claim 3, wherein each of the engaged portions in the plurality of shift gears is formed in a state of being positioned at an end portion on the same side in the axial direction of the driven shaft. Gear side wall pair of said upstream side gear adjacent in the transmission device, which is located between in a state of being close to the gear teeth portions, and a radially outer end and a radially inner end portion of the gear teeth The operation according to any one of claims 1 to 4, wherein the operation is configured to be interlocked and connected so as to rotate integrally by fitting and attaching a connecting pin along the axial direction of the drive shaft across the parts. Transmission structure of the machine.

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