JP2009220595A - Moving agricultural machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a moving agricultural machine having a large adjustment width of a tread and capable of being widely used in various field circumstances. <P>SOLUTION: A riding management machine is constituted so as to perform the adjustment of the tread by moving a front axle case 29 and a rear axle case in a vehicle body width direction by an expansion/contraction mechanism 31, and the front axle case 29 and the rear axle case rotatably and pivotally support an expandable/contractible input shaft 41. The input shaft 41 is constituted of a hollow cylindrical fixed cylindrical shaft 41a; and a movable shaft 41b spline-fitted to the fixed cylindrical shaft 41a, and the movable shaft 41b is provided slidably in a vehicle body width direction. A differential device 39 for distributing motive power to the left and right input shaft 41 is provided on a side gear shaft 40 in the upstream side of transmission. Thereby, the movable shaft 41b can be slid to a central part S of front and rear transmission cases without causing the interference to the differential device 39 at the adjustment of the tread. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a mobile agricultural machine such as a riding management machine, and more particularly to a tread adjusting mechanism thereof.

  Conventionally, a mobile farm machine that adjusts the tread by providing a differential device on the input shaft (axle, slide shaft) built in the axle case (axle case), and expanding and contracting the axle case and input shaft in the body width direction. Car) has been devised (see Patent Document 1).

JP 2003-94907 A

  Generally, a mobile agricultural machine that can adjust the tread performs operations such as middle tillage, cultivation, or harvesting across various sizes and numbers of straws depending on the field and work content, so it is desirable that the tread adjustment range be large. As described in Document 1, a mobile agricultural machine that transmits power to the left and right front wheels or rear wheels by an input shaft is provided with a differential device on the shaft, and when the tread is adjusted, the differential device and the input shaft Interfered, and the adjustment width of the tread was narrowed by that width.

  Then, this invention aims at providing the mobile farm machine which solved the said subject by providing a differential gear in the transmission upstream rather than an input shaft, distributing motive power, and outputting each to a left and right input shaft. .

The invention according to claim 1 includes a pair of left and right front wheels (2, 2) and a rear wheel (3, 3) supported by an axle case (29, 30), respectively, the front wheel (2, 2) and the rear wheel. Power from the engine (11) is transmitted to at least one of (3, 3) via the differential (39, 67), and the axle case (29, 30) is connected to the fuselage (5). In the movable agricultural machine (1) which is configured to be movable in the width direction and can adjust the treads (W, N) of the front wheels (2, 2) and the rear wheels (3, 3),
Left and right side gear shafts (40, 69) projecting left and right from the differential (39, 67);
The left and right side gear shafts (40, 69) are arranged in parallel to each other and supported by the axle case (29, 30) which is linked to the left and right side gear shafts (40, 69) on the downstream side of transmission. Left and right input shafts (41, 71),
When adjusting the tread, the left and right input shafts (41, 71) can be moved in the body width direction without interfering with the differential (39, 67) together with the axle case (29, 30).
It is in a mobile agricultural machine characterized by this.

In the invention according to claim 2, power from the engine (11) is transmitted to the front wheels (2, 2) and the rear wheels (3, 3) via the differentials (39, 67), respectively.
The left and right input shafts (41, 71) are respectively supported by a front axle and a rear axle case (29, 30).
It exists in the mobile agricultural machine of Claim 1.

  In addition, although the code | symbol etc. in a parenthesis is for contrast with drawing, it does not have any influence on a claim by this.

  According to the first aspect of the present invention, the differential device is provided on the side gear shaft, and the power is transmitted to the input shaft on the downstream side of the transmission through the left and right side gear shafts, so that the differential device has an extra width. The input shaft can be moved in the left-right direction of the machine body, the tread adjustment range can be increased, and the minimum tread can also be reduced.

  According to the second aspect of the invention, even in a four-wheel drive type mobile farm machine that drives the front wheels and the rear wheels, the input shaft can move in the body width direction without interfering with the differential device, and the tread can be adjusted. As the width increases, the minimum tread can also be reduced.

  Hereinafter, a riding management machine 1 as a mobile agricultural machine according to an embodiment of the present invention will be described with reference to the drawings. As shown in FIG. 1 to FIG. 3, the passenger management machine 1 has a body 5 supported by front wheels 2, 2 and rear wheels 3, 3 having substantially the same diameter as a pair of left and right sides. A driving operation unit 6 is provided. In addition, an elevator link 7 including an upper link 7 a and a lower link 7 b is provided behind the machine body 5, and the rotary work machine 10 is attached to the hydraulic cylinder 9 via the elevator link 7 so as to be movable up and down.

  The airframe 5 is arranged with heavy objects such as the engine 11 and the fuel tank 12 concentrated between the front wheels 2 and the rear wheels 3 which are the center portions in the front-rear direction, and above the front wheels 2 is operated. A driver's seat 13 on which a person sits is disposed, and a hydraulic continuously variable transmission (HST) 16 is disposed above the rear wheel 3.

  As shown in FIG. 2, in order to improve the balance of the fuselage, the heavy object is arranged such that the heaviest engine 11 is also centered in the fuselage width direction. A tank 12 is attached to the lower side of the fuselage frame 17, and a battery 15 is attached to the upper side of the fuel tank 12. A muffler 19 extends from the left side of the engine 11.

  On the other hand, the above-described driving operation unit 6 is provided with a steering handle 20 in addition to the driving seat 13, and the steering handle 20 is an upper end portion of a steering shaft 24 (see FIG. 10) covered with a steering column 21. Installed on. As shown in FIG. 4, the rotation from the steering handle 20 is input to a front mission case (traveling system transmission) 23 via an intermediate shaft 22 provided below the steering shaft 24. The front wheels 2 and 2 are steered via a steering mechanism 25 described later.

  Next, the structure around the front axle and the rear axle of the riding management machine 1 will be described. As shown in FIGS. 4 and 7, the front axle mechanism 26 and the rear axle mechanism 27 each include a front axle case 29, a rear axle case 30, and axle support cases 38 and 74 provided outside the fuselage, which are divided. By moving the axle support cases 38 and 74 and the axle cases 29 and 30 in the lateral direction of the vehicle body according to the expansion and contraction of the mechanisms (tread adjusting mechanisms) 31 and 32, the front wheels 2 and 2 and the rear wheels 3 and 3 are moved. The treads W and N are provided to be adjustable.

  As shown in FIGS. 4 to 6, the front axle mechanism 26 includes a front mission (case) 23, a telescopic mechanism 31, a front axle case 29, and an axle support case 38 that supports the front wheels 2 and 2 in a freely steerable manner. The front axle case 29 is composed of a cylindrical portion 23a of the front mission case 23 and a horizontal cylindrical portion 36a of the upper case 36, and the axle support case 38 is formed of the upper case 36 that houses the kingpin shaft 35. It is composed of a vertical cylinder portion 36b and a final case 34. Note that the space between the cylindrical portion 23a of the front mission case 23 and the horizontal cylindrical portion 36a of the upper case 36 is covered with a bellows member 37, and even in the separated state, the cylindrical portion 23a and the horizontal cylindrical portion 36a The input shaft 41 that is rotatably supported is not exposed to the outside.

  The front mission case 23 is supplied with power branched from a rear transmission case (travel system transmission device) 33 via a transmission shaft 43, and a bevel gear 43a provided at the tip of the transmission shaft 43 is The gear 45a of the distribution shaft 45 that distributes power to the traveling transmission system and the tread adjusting transmission system is engaged. A gear 45b provided on the distribution shaft 45 meshes with the differential device 39 to transmit power to the traveling transmission system. From the differential device 39 located at the center of the case, left and right side gear shafts 40, 40 are provided. Is protruding.

  The gears 40a and 40a provided on the left and right side gear shafts 40 and 40 are respectively provided in the left and right fixed cylinder shafts 41a and 41a formed in the hollow cylindrical shape inside the cylindrical portions 23a and 23a of the front mission case 23. The fixed cylindrical shafts 41a and 41a are spline-fitted to the fixed cylindrical shafts 41a and 41a, and the left and right movable shafts 41b and 41b are provided so as to be movable in the body width direction. At the same time, left and right input shafts 41, 41 provided in parallel to the side gear shafts 40, 40 are formed.

  The distal ends of the movable shafts 41b and 41b are respectively provided in the horizontal cylindrical portions 36a and 36a of the left and right upper cases 36 and 36, and a gear 46 provided at the distal ends thereof is a gear provided on the kingpin shaft 35. Meshes with 35a. The gear 35b provided at the lower end of the kingpin shaft 35 meshes with the gear 47a of the front axle 47 that is rotatably supported by the final case 34, and is connected to the front wheel 2 via the front axle 47. Power is transmitted.

  As described above, in the traveling transmission system, the front mission case 23 is provided with the differential gear 39 on the side gear shaft on the upstream side of the transmission instead of the input shaft 41. A constant space in which no members are arranged is formed in the central portion S of the front mission case 23 between 41 and 41, and the left and right movable shafts 41b and 41b are arranged in the center of the front mission case 23. It can slide to the part S.

  Further, in the central portion S of the front mission case 23, a partition wall 44 is formed between the front mission case 23 and the movable shafts 41b and 41b and the differential device 39 are not in contact with each other.

  On the other hand, in the tread adjustment transmission system, the gear 45c of the distribution shaft 45 and the gear 55a of the clutch shaft 55 are engaged with each other, and the power is transmitted to the clutch shaft 55. A claw-type clutch 56 is provided as a clutch for connecting / disconnecting the power. The claw-type clutch 56 includes a claw clutch body 57 that is spline-fitted to the clutch shaft 55, and a claw gear 59 that is loosely fitted to the clutch shaft 55. The left and right screw shafts 53, 53 forming the expansion / contraction mechanism 31 mesh with gears 54.

  The telescopic mechanism 31 is a hollow having a pair of left and right screw shafts 53, 53 having a male screw 53a formed on the outer periphery, and a female screw 52a screwed to the male screw 53a of the screw shaft 53 formed on the inner periphery thereof. It is comprised from the cylindrical expansion-contraction cylinders 52 and 52, and is supported so that expansion-contraction is possible by the support case 23b provided protruding from the front mission case 23 right and left. Further, a flange portion 52 b is formed at the outer end of the telescopic cylinder 52, and the flange portion 52 b is fixed to a pressing plate 51 configured integrally with the upper case 36 by bolts.

  Further, the telescopic mechanism 31 has a stopper mechanism 60 comprising a stopper shaft 61 provided on the flange portion 52b of the telescopic cylinder 52 and a pair of stopper plates 62, 62 provided on the support case 23b. Of these stopper plates 62, 62, a stopper shaft 61 is inserted into a guide hole formed in the stopper plate 62 on the outside of the machine body, and the stopper shaft 61 located between the stopper plates 62, 62 is inserted. A detachment preventing member 61a having a diameter larger than that of the guide hole is attached to the distal end portion. For this reason, the upper and lower limits of expansion and contraction of the expansion / contraction mechanism 31 are restricted by the tip of the stopper shaft 61 coming into contact with the stopper plates 62 and 62.

  A coil spring 49 is interposed between the vertical cylindrical portion 36b of the upper case 36 and the final case 34, and the front suspension 50 that cushions an impact from the front wheel 2 is configured by the coil spring 49 and the like. .

  As shown in FIGS. 7 and 8, the rear axle mechanism 27 is also configured in substantially the same manner as the front axle mechanism 26, and the distribution shaft 63 of the rear mission (case) 33 has a hydraulic continuously variable transmission. Power from the engine 11 is input via 16. The gear 63a provided on the distribution shaft 63 meshes with the gear 65a of the branch shaft 65 and the gear 66a of the clutch shaft 66, and distributes power to the traveling transmission system and the tread adjusting transmission system.

  The power output to the branch shaft 65 is transmitted to the differential device 67 and also branched to the above-described front mission case 23 via the transmission shaft 43, and side gears projecting left and right from the differential device 67. The shafts 69 and 69 are provided with multi-plate brake mechanisms 70 and 70 as side brakes, respectively.

  The power transmitted to the left and right side gear shafts 69 and 69 is transmitted to the left and right fixed cylinder shafts 71a and 71a, respectively. The fixed cylinder shafts 71a and 71a formed in a hollow cylindrical shape are arranged in the body width direction. The left and right movable shafts 71b, 71b that are movably provided are spline-fitted. These fixed shafts 71a, 71a and movable shafts 71b, 71b constitute left and right input shafts 71, 71, which are rotatably supported by the rear axle case 30 and arranged in parallel to the side gear shaft 69. ing.

  The rear axle case 30 includes a cylindrical portion 23a of the rear transmission case 33 and a horizontal cylindrical portion 72a of the upper case 72. The cylindrical portion 23a and the horizontal cylindrical portion 72a are formed by the rear wheels 3 and 3. The treads W and N are configured to be separable, and the space between them is covered with a bellows member 73.

  The distal end portion of the movable shaft 71 b is rotatably mounted in the horizontal cylindrical portion 72 a of the upper case 72 and transmits power to the kingpin shaft 75 in the upper case 72. The kingpin shaft 75 is rotatably supported by an axle support case 74 including a vertical cylindrical portion 72b of the upper case 72 and a final case 76, and transmits power to the rear axle 77 in the final case 76. Power is output to the rear wheel 3 via the rear axle 77.

  As described above, the rear mission case 33 is also provided with the differential device 67 on the side gear shaft in the same manner as the front mission case 23, and the rear mission case 33 between the left and right input shafts 71 and 71 disposed to face each other. Since a fixed space is formed in the central portion S, the left and right movable shafts 71b and 71b are configured to be slidable to the central portion S of the rear mission case 33.

  In the central portion S of the rear mission case 33, a partition wall 68 is formed between the differential device 67 and the movable shafts 71b and 71b and the differential device 67 are not in contact with each other.

  On the other hand, the clutch shaft 66 of the tread adjustment transmission system is provided with a claw clutch 79 which is a clutch for connecting and disconnecting power to the telescopic mechanism 32 as a torque limiter, and the claw clutch 79 is connected to the clutch shaft 66. The claw clutch body 80 is spline-fitted and the claw gear 81 is loosely fitted to the clutch shaft 66. The claw gear 81 meshes with a gear 82 a provided on the left and right screw shafts 82, 82 forming the expansion / contraction mechanism 32, and transmits power to the expansion / contraction mechanism 32.

  The expansion / contraction mechanism 32 is configured by screwing a male screw provided on the outer periphery of the pair of left and right screw shafts 82 and 82 and a female screw provided on the inner periphery of the expansion / contraction cylinders 83 and 83. The flange portion 83 a of the cylinder 83 is fixed to a pressing plate 85 configured integrally with the upper case 72 by bolts. Further, a stopper shaft 86 is attached to the flange portion 83a, and a stopper mechanism 89 is configured by disposing the tip of the stopper shaft 86 between a pair of stopper plates 87, 87 provided on the support case 33b. Has been.

  The expansion and contraction mechanisms 31 and 32 described above are not screw-type but may use racks and pinions, hydraulic pressures, springs, or the like, or may be attached to the front and rear axle cases 29 and 30.

  Next, the front axle and rear axle pawl clutches 56 and 79 will be described.

  The front and rear claw clutches 56 and 79 described above are connected and disconnected by operating a front / rear interlocking operation lever (not shown) provided in the driving operation unit 6. The tread adjustment operation mechanism for operating the connection / disconnection of the front and rear is composed of the front / rear interlocking operation lever and the shifter mechanisms 95 provided in the front mission case 23 and the rear mission case 33, respectively.

  As shown in FIG. 9, the shifter mechanism 95 includes a shifter 106 that connects and disconnects the claw clutches 56 and 79 by the rotation of the cam member, a shifter shaft 96, a shifter arm 97 that rotates the shifter shaft 96, and a support. An auxiliary arm 100 that is rotatable about a shaft 99 and a shifter arm 97 and a spring 101 spanned between the auxiliary arm 100 are configured as shown in FIGS. 9A and 9B. In response to the rotation of the shifter arm 97, the spring 101 exceeds the fulcrum, and can be switched between a cut state (the state shown in FIG. 9A) and an engaged state (the state shown in FIG. 9B).

  The shifter arm 97 and the auxiliary arm 100 are substantially rectangular plate-like members, and a boss portion 97 a of the shifter arm 97 is fitted with a key 96 a provided on the shifter shaft 96. Further, a contactor 97b is provided at the shifter shaft side end of the shifter arm 97, and one end of the connecting link 102 and the spring 101 from the front / rear interlocking operation lever is attached to the other end.

  On the other hand, the auxiliary arm 100 extends substantially perpendicularly to the longitudinal direction of the shifter arm 97, and its boss portion 100a extends laterally from the holder 103 that rotatably supports the shifter shaft 96. It is rotatably fitted to a support shaft 99 projecting from the extended bracket 105. The boss portion 100a is provided with an abutment element 100b that abuts against the abutment element 97b of the shifter arm 97. The abutment elements 97b and 100b cause the shifter arm 97 and the auxiliary arm 100 to rotate in conjunction with each other. .

  Further, the other end of the spring 101 is attached to the end of the auxiliary arm 100 opposite to the support shaft 99, so that the spring 101 has not only the attachment base on the shifter arm 97 side but also the other attachment base. It can be moved, and it is constructed so that even a small amount of movement can exceed the fulcrum.

  A shifter 106 including a cam member 106a and an attachment member 106b is provided below the shifter shaft 96, and the cam member 106a is in contact with the contact bodies 57b and 80b of the pawl clutch bodies 57 and 80. The claw clutch bodies 57 and 80 are composed of contact bodies 57b and 80b and sliding bodies 57a and 80a that are spline-fitted to the clutch shafts 55 and 66. The claw clutches 56 and 79 are rotated by the shifter 106. Then, the engagement is maintained by moving the pawl clutch bodies 57 and 80 from the cutting position to the engaging position against the spring 107.

  Next, the steering mechanism 25 that steers the front wheels 2 and 2 will be described.

  The steering mechanism 25 is configured such that the front wheels 2 and 2 are steered in accordance with the rotation of the steering handle 20 and that it is not necessary for the operator to adjust the steer mechanism when the treads W and N are changed. The steering transmission shaft 90 that expands and contracts in conjunction with the expansion and contraction mechanism 31, the steering case 91 that is integrally connected to the upper case 36, and the steering shaft that is rotatably mounted in the steering case 91. 92, and a link mechanism 93 for connecting the steering shaft 92 and the knuckle arm 34a of the final case 34 are provided.

  As shown in FIGS. 4 and 5, the rotation from the steering handle 20 is input to the front mission case 23 by the input shaft 22, and the steering transmission shaft 90 is configured by meshing the gears 22 a and 94. Is output to the direction-fixed cylinder shaft 90a.

  The steering transmission shaft 90 is rotatably supported over the entire length of the front mission case 23 in the body width direction, and the steering fixed cylindrical shaft 90a formed in a hollow cylindrical shape is splined to the steering fixed cylindrical shaft 90a. The left and right steering movable shafts 90b and 90b are configured to be movable in the body width direction.

  The left and right steering movable shafts 90b and 90b are respectively supported at their outer ends by left and right steering cases 91 and 91, respectively, and a gear 95 provided at the tip of the steering case 91 is provided. And a gear 92a provided at the lower end of the steering shaft 92 extending substantially perpendicularly to the upper side of the machine body with respect to the steering movable shaft 90b.

  The steering shaft 92 extends in the vertical direction of the machine body, and is disposed in parallel with the kingpin shaft 35. A steering arm 93 a constituting the link mechanism 93 is provided at the upper end of the steering shaft 92. . The steering arm 93a is connected to the knuckle arm 34a of the final case 34 by a link 93b, and is linked to the rotation of the steering shaft 92 to rotate the final case 34 about the kingpin shaft 35. .

  Since the steering case 91 is configured integrally with the upper case 36, when the telescopic mechanism 31 is expanded or contracted during tread adjustment, the steering case 91 is operated in conjunction with the axle support case 38 including the upper case 36 and the final case 34. The direction transmission shaft 90 expands and contracts, and is configured to move in the body width direction. Thus, the steering mechanism 25 determines the relative positional relationship between the steering shaft 92 of the steering case 91 and the final case 34. Always kept roughly constant.

  Next, power transmission of the passenger management machine 1 will be described.

  As shown in FIG. 10, two pulleys 109a and 109b are fixed to the output shaft 109 of the engine 11, and are respectively provided on the input shafts 111 and 112 of the hydraulic pump 110 and the hydraulic continuously variable transmission 16. The belts 113 and 115 are wound around the pulleys 111a and 112a via tension clutch pulleys 113a and 115a. The power input to the hydraulic continuously variable transmission 16 is output to the rear mission (case) 33 by the distribution shaft 63 and transmitted to the rear wheels 3 and 3.

  The power input to the rear mission case 33 is branched to the front mission (case) 23 via the transmission shaft 43, and the power is supplied to the front wheels 2 and 2 via the front mission (case) 23. Has been communicated.

  On the other hand, the input shaft 111 of the hydraulic pump 110 described above is provided with a gear 111b for branching power to the rotary work machine 10, and the gear 111b is a work machine PTO shaft 116 provided with a work machine clutch 117. Is engaged with the gear 116a. The work implement PTO shaft 116 is input to the work implement gear case 119 and meshes with forward / reverse switching gears 121a and 121b loosely fitted to the input shaft 120 of the work implement gear case 119.

  The input shaft 120 is provided with gears 122 a and 122 b having different numbers of teeth, and meshes with gears 125 a and 125 b that are loosely fitted to the rotary drive shaft 123, respectively. The work machine gear case 119 operates the forward / reverse rotation by selectively engaging one of the forward / reverse switching gears 121a and 121b, which is loosely fitted, with the rotary drive shaft 123. The gears are shifted in two stages by selectively engaging one of the gears 125a and 125b. The rotary drive shaft 123 is provided with two rotary units 129 and 129 movably in the machine body width direction. The power input to the rotary drive shaft 123 is transmitted through the transmission chain 126 of the rotary unit 129. It is transmitted to the nail 127.

  Next, the operation of the passenger management machine 1 according to the embodiment of the present invention will be described.

  An operator plows the field with the rotary claws 127 when the two rotary units 129 and 129 are joined and arranged, and the two joined rotary units 129 and 129 are driven. .

  On the other hand, when the work requires changing the treads W and N in accordance with the sizes of the straws A and B in the field, such as middle tillage, cultivating or harvesting, the operator first has a front / rear interlocking operation lever ( Operate (not shown) to the entry side. When the front / rear interlocking operation lever is operated to the entry side, as shown in FIG. 9, the shifter arm 97 rotates and the spring 101 exceeds the fulcrum, and the shifter mechanism 95 is engaged (state shown in FIG. 9B). The claw clutch bodies 57 and 80 move against the urging force of the spring 107 and the claw clutches 56 and 79 are engaged.

  When the claw-type clutches 56 and 79 are engaged and power is transmitted to the expansion and contraction mechanisms 31 and 32, the operator moves the airframe back and forth and expands and contracts the expansion and contraction mechanisms 31 and 32, and the front wheels 2 and 2 and The treads W and N of the rear wheels 3 and 3 are adjusted, and the claw clutches 56 and 79 are disconnected by operating the front / rear interlocking operation lever at the right position. At this time, as the axle support case 38 moves in the body width direction, the steering transmission shaft 90 expands and contracts and the steering case 91 also moves, and the steering mechanism 25 is adjusted simultaneously with the treads W and N.

  When adjusting the tread, if the airframe is moved too much, the stopper mechanisms 60 and 89 are operated, and the claw clutch bodies 57 and 80 get over the inclination of the claw of the claw gears 59 and 81 and the urging force of the spring 107 The shifter shaft 96 is rotated by pressing the shifter 106. As the shifter shaft 96 rotates, the shifter arm 97 rotates, causing the spring 101 to exceed the fulcrum, and forcibly bringing the shifter mechanism 95 into a disconnected state (position in FIG. 9A), thereby disconnecting the claw clutches 56 and 79. Hold in position.

  When the treads W and N of the front wheels 2 and 2 and the rear wheels 3 and 3 have been adjusted, the operator then arranges the two rotary units 129 and 129 in accordance with the grooves between the ribs, respectively, While driving, the machine body 5 is run along the fence, and the rotary claw 127 is used to dig up a groove between the ribs shallowly to weed or to bring soil to the plant stock.

  By configuring the riding management machine 1 as described above, the treads W and N can be changed according to the sizes of the baskets A and B in the field. In particular, by providing the differential devices 39 and 67 not on the input shafts 41 and 71 but on the side gear shafts 40 and 69 on the transmission upstream side, the movable shafts 41b and 71b are located at the center of the front and rear transmission cases 23 and 33. It is possible to slide to the portion S, the adjustment width of the treads W and N is increased, and the minimum tread N can be reduced.

  Further, when the steering transmission shaft 90 of the steering mechanism 25 extends and contracts in conjunction with the expansion and contraction mechanism 31, the operator adjusts the length of the link mechanism 93 corresponding to the drag link when adjusting the treads W and N. There is no need. Further, even if the treads W and N are adjusted, the relative positional relationship between the steering case 91 (steering shaft 92) and the final case 34 is constant, so that the tire turning angle is always constant even after the treads W and N are changed. Yes, a stable and good steering feeling can be maintained.

  Further, when the expansion / contraction of the expansion / contraction mechanisms 31 and 32 is restricted by the stopper mechanisms 60 and 89, the claw that operates as a torque limiter by setting the shifter mechanism 95 to the cutting position and automatically disconnecting the claw-type clutches 56 and 79. It is possible to eliminate the continuous torque jump of the clutches 56 and 79, and to prevent claw collision noise and wear generated at that time.

The side view of the passenger management machine which concerns on this invention. The top view of the passenger management machine which concerns on this invention. The front view of the passenger management machine which concerns on this invention. (A) Cross-sectional view of a front transmission case of a riding type management machine according to the present invention, (b) Cross-sectional view of a steering case of a steering mechanism according to the present invention, (c) Front axle of a riding management machine according to the present invention ( A developed view of the tread in a wide state. The expansion expanded view of the front axle (at the time of a narrow tread width | variety) of the passenger management machine which concerns on this invention. The top view of the front axle of the riding management machine which concerns on this invention. (A) Sectional drawing of the rear mission case of the riding type management machine concerning this invention, (b) The developed view of the rear axle (at the time of a tread wide state) of the riding management machine concerning this invention. The developed view of the rear axle (at the time of a narrow tread width | variety) of the passenger management machine which concerns on this invention. (A) Plan view showing the shifter mechanism in the cut state, (b) Plan view showing the shifter mechanism in the engaged state, (c) Side view of FIG. 9 (b). The transmission system figure of the passenger management machine which concerns on this invention.

Explanation of symbols

1 Passenger management machine (mobile farm machine)
2 Front wheel 3 Rear wheel 5 Airframe 11 Engine 29 Front axle case (axle case)
30 Rear axle case (axle case)
39 Differential gear 40 Side gear shaft 41 Input shaft 67 Differential gear 69 Side gear shaft 71 Input shaft W Tread when wide N tread when narrow

Claims (2)

Each has a pair of left and right front wheels and rear wheels supported by an axle case, and power from the engine is transmitted to at least one of the front wheels and rear wheels via a differential device, and the axle case is attached to the fuselage. In a mobile agricultural machine configured to be movable in the machine body width direction and capable of adjusting the tread of the front wheel and the rear wheel,
Left and right side gear shafts protruding left and right from the differential;
Left and right input shafts supported by the axle case, which are arranged in parallel to the left and right side gear shafts and interlock with the left and right side gear shafts on the downstream side of transmission, respectively.
The left and right input shafts can be moved in the body width direction without interfering with the differential device together with the axle case during tread adjustment.
A mobile agricultural machine characterized by that. The power from the engine is transmitted to the front wheels and the rear wheels via the differential, respectively.
The left and right input shafts are respectively supported by a front axle and a rear axle case.
The mobile agricultural machine according to claim 1.

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