JP2017099350A - Tending machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an operation device enabling a work clutch and differential lock mechanism to be operated with rotation operation of a work lever and to enable the work clutch to be turned "off" and the differential lock to be released subsequently when the work clutch lever is operated to the "off" side even in a large load state, thereby reducing operation force.SOLUTION: In a tending machine 1, a work clutch 79 and a differential lock mechanism 90 are arranged in a transmission case 10 and an operation mechanism of the work clutch 79 and an operation mechanism of the differential lock mechanism 90 are linked with a link mechanism 50 in the transmission case 10. With the link mechanism 50, when operation is made so that the work clutch is turned off and the differential lock is released, the work clutch 79 is brought into the "off" state and then the differential lock mechanism 90 is released.SELECTED DRAWING: Figure 6

Description

  The present invention relates to a technique for interlocking a work clutch for turning on and off work of a tilling device of a management machine and a differential lock mechanism for releasing left and right connection of an axle supporting left and right traveling wheels.

  Conventionally, an engine is mounted on the front of the management machine, and the power from the engine is transmitted to the input shaft of the transmission case via a belt transmission mechanism, and the transmission is housed in the transmission case from the input shaft, Power is transmitted to an axle with fixed wheels via a differential lock mechanism, and power can be transmitted from an input shaft to a tilling shaft via a work clutch. The working clutch can be turned on and off by sliding a sliding body on the PTO shaft, and the sliding body is slid by a shifter. The differential lock mechanism has an engaging claw formed on the differential case, supports the sliding body on one side of the axle by spline, and engages the engaged claw formed on the sliding body with the engaging claw of the differential case. A technique that enables an axle to rotate integrally is known (for example, see Patent Document 1).

JP 2014-103941 A

  The conventional work clutch and differential lock mechanism can be turned on and off by operating an operation lever disposed on the side of the mission case, and the operation lever, shifter, and sliding body are linked via an operation wire. That is, an operation lever is provided at the rear part of the handle that extends rearward from the mission case, and one end of the operation wire is connected to the operation lever, and the other end of the operation wire is connected to the two sub operation wires via a bifurcated fitting. And one of the two sub operation wires is linked to the work clutch, and the other is linked to the differential lock mechanism.

The diff lock arm of the diff mechanism is biased to the release side by the spring, and the work clutch is also urged to the “off” side by the spring. When operating the diff lock and the work clutch “on”, it operates against the spring force. I was operating the lever.
With such a configuration, when working in the differential lock state, when the aircraft tilts and wants to stop running and work, when the operation lever is operated to the “OFF” side, the load is large and the clutch is The “ON” position and the differential mechanism could not be released while being bitten. In addition, even if it has a mechanism that interlocks the work clutch and differential mechanism and does not have a spring that biases in the release direction, when the operation lever is “turned off” due to an abnormality, the wheels and the tilling device are greatly damaged. In a state where a load is applied, a large operating force is required, and it may not be possible to stop immediately.
The present invention has been made in view of the situation as described above. The work clutch and the diff lock mechanism can be operated with a single wire, and the work clutch lever is operated to the “off” side even under a heavy load. Then, after the work clutch is “disengaged”, an operation device that can be operated in order of releasing the diff lock and reducing the operation force is provided.

The problem to be solved by the present invention is as described above. Next, means for solving the problem will be described.
That is, in the first aspect of the present invention, the management machine includes a work clutch and a diff lock mechanism in the mission case, and the operation mechanism of the work clutch and the operation mechanism of the diff lock mechanism are linked by a linkage mechanism in the mission case. The linkage mechanism is configured such that when the operation clutch is turned off and the diff lock is released, the diff lock is released after the work clutch is turned off.

According to a second aspect of the present invention, the linkage mechanism includes a link mechanism that connects the work clutch operating mechanism and the differential lock mechanism, and the link mechanism includes a timing for releasing the differential lock after the work clutch is in the “disengaged” state. It has an adjustment mechanism.
According to a third aspect of the present invention, the linkage mechanism includes a link mechanism that connects a work clutch operation mechanism and a diff lock mechanism, and the diff lock is released after the work clutch is in the “disengaged” state. And a timing adjustment mechanism.

  With the above-described configuration, the present invention is abnormal when a large load is applied when working while the differential lock is in an operating state, and the work lever is operated to the “OFF” side in order to stop the work. The operating force at the time is reduced compared to the prior art, and the work clutch and the differential mechanism can be released in order during the “off” operation, and the impact on the “off” operation of the aircraft can be reduced.

The side view of a management machine. A side view of a mission case. The side view which shows the inside of a mission case. Front sectional drawing of a mission case traveling part. Front sectional view of the tillage part of the mission case. The perspective view which shows a linkage mechanism. The enlarged view of a timing adjustment mechanism. The perspective view which shows other embodiment of a timing adjustment mechanism.

  Below, one Embodiment of the management machine 1 provided with the linkage mechanism of the working clutch and differential lock mechanism which concerns on this invention is described. In the following description, the direction of the arrow F in the figure is defined as the forward direction.

  A management machine 1 shown in FIG. 1 includes a mission case 10 arranged at the front and rear center of the machine, an engine 20 arranged on the front part of the machine, wheels 30 and 30 supported on the lower part of the mission case 10, and a rear part of the machine. The rotary cultivating device 4 that is disposed and enables the cultivating work, the control unit 60 disposed above the rotary cultivating device 4 at the rear of the machine, and the like are provided.

  The engine 20 is a drive source. The engine 20 is fixed on an engine frame 21 fixed to the front portion of the mission case 10. Power from the engine 20 is transmitted to the transmission case 10 via the belt transmission mechanism 2. The belt transmission mechanism 2 includes an output pulley 26 fixed on the output shaft of the engine 20, an input pulley 27 fixed on the input shaft 13 protruding from the upper portion of the transmission case 11, the input pulley 27, and the output A belt 28 wound between the pulley 26 and a tension pulley 29 that tensions or relaxes the belt 28. The tension pulley 29 is interlocked with the main clutch lever 63 to perform an "on" operation of the main clutch lever 63. Thus, the belt 28 is tensioned so that power can be transmitted from the engine 20 to the transmission case 10, and the belt 28 is relaxed by the “disengagement” operation of the main clutch lever 63 to cut off power transmission.

The transmission case 10 is formed in a “h” shape when viewed from the side, and is arranged at the center of the left and right sides of the management machine 1. An axle 31 (31 L / 31 R) is provided at the front lower portion of the traveling case 11 (FIG. 2) extending forward and downward. The wheels 30 and 30 are fixed to both sides of the axles 31L and 31R. A rotary tiller 4 is provided at the rear of the mission case 10, and the rotary tiller 4 has a tiller shaft 41 horizontally mounted on the rear lower part of the tiller case 12 (FIG. 2) extending rearward and downward of the mission case 10. The tilling claws 42, 42,... Are fixed on the tilling shaft 41 at appropriate intervals. The upper part of the rotation trajectory of the cultivation claws 42, 42... Is covered with a cultivation cover 43. A resistance rod 44 and a tail wheel 45 are provided at the rear of the tillage cover 43.
A transmission, a clutch, and the like, which will be described later, are housed in the upper part of the mission case 10, and the power from the engine 20 is shifted and transmitted to the wheels 30 and the rotary tiller 4.

  The control unit 60 is for performing various operations for causing the management machine 1 to travel and work. The steering unit 60 has a handle 61 and a shift lever 62 projecting upward and backward from the upper part of the mission case 10. The rear part of the handle 61 is a control part 60, and a main clutch lever 63, a work lever 64, an accelerator lever and the like are arranged at the rear part of the handle 61.

Next, the configuration within the mission case 10 will be described with reference to FIGS.
In the transmission case 10, an input shaft 13, a transmission shaft 14, an intermediate shaft 15, a travel output shaft 16, a PTO shaft 17, a shifter shaft 18, a diff-lock shifter shaft 19, an axle 31, a tilling shaft 41, etc. are horizontally mounted, via bearings. And is supported rotatably.

  One end of the input shaft 13 protrudes laterally (leftward), and an input pulley 27 that constitutes a belt transmission mechanism is fixed. An input gear 70 is slidably fitted on the input shaft 13 in the mission case 10, and the input gear 70 is connected to a first transmission gear 71, a second transmission gear 72, a transmission gear 73 and a counter gear 74, which will be described later. It is arranged so that it can be engaged.

  A first transmission gear 71 and a second transmission gear 72 are slidably fitted on the transmission shaft 14 in a splined manner. A shifter fork is fitted to each of the input gear 70, the first transmission gear 71, and the second transmission gear 72. The shifter forks are respectively fixed to a shifter shaft (not shown), and the shifter shaft is slid by the operation of the transmission lever 62. Is done. The first transmission gear 71 is disposed so as to be able to mesh with the input gear 70, the transmission gear 73, and a travel input gear 75 described later, and the second transmission gear 72 can be engaged with the input gear 70 and a counter gear 74 described later. It is arranged.

  A transmission gear 73, a counter gear 74, and a tooth portion 15a are disposed on the intermediate shaft 15. The transmission gear 73 is fixed on the intermediate shaft 15, and the counter gear 74 is rotatably supported via a bearing. The part 15 a is formed on the intermediate shaft 15. The transmission gear 73 is disposed so as to be able to mesh with the input gear 70 and the first transmission gear 71. The counter gear 74 is always meshed with the input gear 70 and a PTO input gear 77 described later. The tooth portion 15a is always meshed with the traveling input gear 75. Thus, the transmission is configured.

  A travel input gear 75 and a travel output sprocket 76 are fixed on the travel output shaft 16. The travel input gear 75 can be meshed with the first transmission gear 71, and is always meshed with the tooth portion 15a. The traveling output sprocket 76 is wound around one side of the traveling transmission chain 80. The other side of the traveling transmission chain 80 is wound around a sprocket 33 formed on the outer periphery of the differential case 32a of the differential device 32 provided on the axles 31L and 31R.

  As shown in FIG. 5, a PTO input gear 77 is rotatably supported on the PTO shaft 17, a PTO output sprocket 78 is fixed, and a work clutch 79 is further provided. The working clutch 79 is provided with an engaging claw on a sliding body that is spline-fitted so as to be slidable on the PTO shaft 17, and the engaging claw is configured to be engageable with an engaging claw formed on the PTO input gear 77. Yes. The PTO input gear 77 is always meshed with the counter gear 74. The tillage transmission chain 81 is wound around the PTO output sprocket 78. The other side of the tillage transmission chain 81 is wound around a sprocket 46 fixed on the tillage shaft 41.

In such a configuration, by operating the speed change lever 62, the speed is changed at the high speed stage, the low speed stage, the reverse speed stage, and the work stage. In the high speed stage, the power transmitted to the input shaft 13 is input gear 70 → first transmission gear 71 → travel input gear 75 → travel output shaft 16 → travel output sprocket 76 → travel transmission chain 80 → sprocket 33 → diff device 32. → It is reported as axle 31L / 31R.
At the low speed stage, the input gear 70 → the transmission gear 73 → the intermediate shaft 15 → the tooth portion 15a → the traveling input gear 75 → the traveling input gear 75 → the traveling output shaft 16 → the traveling output sprocket 76 → the traveling transmission chain 80 → the sprocket 33 → the differential device. 32 → Axle 31L / 31R.
In the reverse gear, the input gear 70 → the first transmission gear 71 → the transmission gear 73 → the intermediate shaft 15 → the tooth portion 15a → the traveling input gear 75 → the traveling output shaft 16 → the traveling output sprocket 76 → the traveling transmission chain 80 → the sprocket 33 → the differential Device 32 → axes 31L and 31R are transmitted.
In the working stage, the input gear 70, the counter gear 74, the PTO input gear 77, the PTO shaft 17, the PTO output sprocket 78, the tilling transmission chain 81, the sprocket 46, and the tilling shaft 41 are transmitted.

Next, the interlocking structure of the work clutch mechanism 9 and the differential lock mechanism 90 will be described with reference to FIGS.
The work clutch mechanism 9 includes a work shifter 5 for “turning on” and “off” the work clutch 79, and a connecting member for connecting the work shifter 5 and the work lever 64.
The work shifter 5 is provided on the shifter shaft 18 in the mission case 10. The shifter shaft 18 is disposed below the intermediate shaft 15 and substantially at the center of the transmission case 10 between the traveling output shaft 16 and the PTO shaft 17 in the front, rear, top and bottom. The work shifter 5 includes a shifter shaft 18, a shift fork 82, a cam 83, a spring 84, and a pin 85, and one end of the first link 51 constituting the linkage mechanism 50 is fixed on the shifter shaft 18. The cam 83 is slidably fitted on the shifter shaft 18, and a cam profile is formed at one end (left side) of the cam 83 and abuts on a pin 85 inserted and fixed in the diameter direction of the shifter shaft 18. A shift fork 82 is fitted and fixed on the other side of the cam 83 and is urged by a spring 84 so as to slide toward the pin 85 side. The front end of the shift fork 82 is fitted into the fork groove of the work clutch 79 and is biased toward the clutch “on” side by the biasing force of the spring 84.

One side (right side) of the shifter shaft 18 protrudes laterally from the mission case 10, and one end of the operation arm 67 is fixed on one end (right end) of the shifter shaft 18. A wire 68 is connected to the other end of the operation arm 67, and the other end of the wire 68 is connected to the work lever 64 of the control unit 60 to constitute a connecting member.
Thus, the work clutch operation mechanism 9 is configured, and by operating the work lever 64, the work clutch 79 is "on" via the wire 68, the operation arm 67, the shifter shaft 18, the pin 85, the cam 83, and the shift fork 82. “Off” operation is possible.

The linkage mechanism 50 includes a link mechanism including a first link 51, a second link 52, and a third link 53, and the timing adjustment mechanism 7 is provided in the link mechanism. The timing adjusting mechanism 7 is constituted by a long hole in this embodiment.
The first link 51 extends downward from between the travel output shaft 16 and the PTO shaft 17, and a long hole 51a is formed at the tip. A pivot shaft 54 fixed to one end of the second link 52 is inserted into the elongated hole 51a and pivotally supported. The other end of the second link 52 extends forward, and one end of the third link 53 is connected to the tip end via a pivot shaft 55. The other end of the third link 53 extends downward and is fixed to the differential lock shifter shaft 19. Thus, the linkage mechanism 50 is disposed in the space divided from the upper part of the mission case 10 into the traveling case 11 and the tilling case 12, and the linkage mechanism 50 includes the timing adjustment mechanism 7. However, the arrangement of the long holes constituting the timing adjustment mechanism 7 is not limited to the first link 51, and it may be configured to be provided at a connecting portion with the shaft of the second link 52 or the third link 53. is there.

  A diff lock shifter 6 is provided on the diff lock shifter shaft 19 in the mission case 10. The diff lock shifter 6 includes a cam 86, a shift fork 87, a spring 88, a pin 89, and a diff lock shifter shaft 19, and the third link 53 is fixed on the diff lock shifter shaft 19. The cam 86 is slidably fitted onto the diff lock shifter shaft 19, and a cam profile 86 a is formed on one end (left side) of the cam 86 and abuts against a pin 89 inserted and fixed in the diametrical direction of the diff lock shifter shaft 19. A shift fork 87 is fitted on the other side of the cam 86 and is urged by a spring 88 so as to slide toward the pin 89 side. The third link 53 and the shift fork 87 are disposed on opposite sides of the traveling transmission chain 80.

  The front end of the shift fork 87 is fitted to the sliding body 34 of the differential lock mechanism 90 provided on the axles 31L and 31R. The differential lock mechanism 90 fixes the differential device (differential device) 32 (so as not to make a differential) and integrally rotates the left and right axles 31L and 31R. The pinion 35 in 32a is fixed to the axle 31R. The differential device 32 inserts the inside of the left and right axles 31L and 31R into the differential case 32a, fixes the pinions 35 and 35 to the inner ends of the axles 31L and 31R, and can freely rotate to the differential case 32a on the left and right pinions 35 and 35 The pinions 36 and 36 pivoted on the teeth are engaged with each other. And the latching | locking part of the sliding body 34 spline-fitted on the axle shaft 31R is arrange | positioned at the latching | locking part of the right side pinion 35 so that engagement is possible. The shift fork 87 and the sliding body 34 are urged in the differential lock direction by the spring 88. However, the configurations of the work shifter 5 and the diff lock shifter 6 are not limited, and may be configured to slide the shaft and the shift fork. Further, the configuration of the differential lock mechanism 90 is not limited.

  In the above configuration, when the work clutch operating mechanism 9 is operated to “ON”, the operation arm 67 is rotated downward via the wire 68 by rotating the work lever 64 in the “ON” direction, and the shifter shaft 18 is rotated. Is also rotated. By this rotation, the cam 83 is rotated and the shift fork 82 is moved to the left by the urging force of the spring 84, the work clutch 79 is turned “on”, and the power of the engine 20 is transmitted to the rotary tiller 4. It is done.

  Simultaneously with the rotation of the shifter shaft 18, the diff lock shifter shaft 19 is rotated through the linkage mechanism 50 (first link 51, second link 52, third link 53), and the cam 86 is rotated by this rotation. The shift fork 87 is moved to the left by the biasing force of the spring 88, and the sliding body 34 of the differential lock mechanism 90 is moved to engage with the pinion 35 to be differentially locked. Due to this differential lock, the axles 31L and 31R are simultaneously driven in the same rotation, and the straight traveling performance during tillage work is improved.

  On the contrary, when the work lever 64 is rotated in the “cut” direction, the operation arm 67 and the shifter shaft 18 are rotated in the opposite direction via the wire 68, and the cam 83 is rotated by this rotation. Thus, the shift fork 82 is moved to the right, the work clutch 79 is turned off, the power from the engine 20 is cut off, and the drive of the rotary tiller 4 is stopped.

  The first link 51 is rotated simultaneously with the rotation of the shifter shaft 18 to transmit the operating force to the linkage mechanism 50. The timing adjustment mechanism 7 is provided between the first link 51 and the second link 52. Therefore, the second link 52 is not actuated until the pivot shaft 54 moves from one end to the other end of the long hole 51a. That is, the second link 52 is moved after the work clutch 79 is turned off, the shift fork 87 is moved to the right via the third link 53 and the diff lock shifter 6, and the diff lock is released.

  As described above, the work clutch 79 and the diff lock mechanism 90 are provided in the mission case 10, and the operation mechanism of the work clutch 79 and the operation mechanism of the diff lock mechanism 90 are linked by the linkage mechanism 50 in the mission case 10. In the management machine 1, the linkage mechanism 50 is configured to release the differential lock mechanism 90 after the work clutch 79 is in the "disengaged" state when the work clutch is turned off and the differential lock is released. When the operation is performed with the 90 in the activated state (diff lock state), an abnormality occurs when a large load is applied, and the operation force when operating the work lever 64 to the “OFF” side to stop the work is low. It is reduced. When the work lever 64 is turned “off”, the work clutch 79 and the diff lock mechanism 90 are sequentially released, so that the rotary tiller 4 is stopped and the driving force in the forward direction is stopped. Once released, the impact on the aircraft will be reduced.

  The linkage mechanism 50 includes a link mechanism that connects the work clutch operation mechanism 9 and the diff lock mechanism 90. The link mechanism includes a timing at which the diff lock is released after the work clutch 79 is in the “disengaged” state. Since the adjustment mechanism 7 is provided, the timing adjustment mechanism 7 is disposed in the mission case 10 and is not damaged from the outside, and a stable operation can be ensured. Further, the timing adjusting mechanism 7 can be realized by a long hole 51a that constitutes a part of the link mechanism, and the long hole 51a can be configured simply, inexpensively, and with few failures.

  Further, instead of providing the timing adjustment mechanism 7 in the link mechanism, it is also possible to provide the operation mechanism of the differential lock mechanism 90 with the timing adjustment mechanism 7 for releasing the differential lock after the work clutch 79 is in the “disengaged” state. . That is, as shown in FIG. 8, the linkage mechanism 50 and the diff lock shifter 6 are interposed between the work clutch operating mechanism 9 and the diff lock mechanism 90, and are formed on the cam 86 of the diff lock shifter 6. By changing the shape (inclination and circumferential length) of the cam profile 86a, the timing for releasing the diff lock can be changed. That is, when the operation lever 64 is operated to the “OFF” side, the diff lock shifter shaft 19 is rotated. At this time, the cam 86 pin 89 is pushed to slide and the differential lock is released, but the inclination of the cam profile 86a is gentle at the initial rotation of the differential lock shifter shaft 19 and becomes a steep angle at the end of the rotation. Thus, in the initial operation of the operation lever 64 to the “disengagement” side, the sliding amount of the shift fork 87 (cam 86) is small and the diff lock state continues. At this time, the operation clutch 79 is “disengaged”. Thereafter (at the end of rotation), the cam profile 86a has a steep inclination, so that the sliding amount of the shift fork 87 (cam 86) increases and the differential lock is released.

  Thus, the timing adjustment mechanism 7 is disposed in the mission case 10 by providing the operation mechanism of the differential lock mechanism 90 with the timing adjustment mechanism 7 for releasing the differential lock after the work clutch 79 is in the “disengaged” state. Therefore, it is possible to ensure a stable operation without being damaged from the outside. Further, the timing adjusting mechanism 7 can be easily obtained by changing the shape of the cam profile 86. By adjusting the shape of the cam profile 86, the operation feeling can be adjusted.

1 Control Machine 6 Differential Lock Shifter 7 Timing Adjustment Mechanism 10 Mission Case 50 Linkage Mechanism 64 Work Lever 79 Work Clutch 90 Differential Lock Mechanism

Claims (3)

  In a management machine comprising a work clutch and a differential lock mechanism in a mission case, wherein the operation mechanism of the work clutch and the operation mechanism of the differential lock mechanism are linked by a linkage mechanism in the mission case, the linkage mechanism includes a work clutch “ A management machine characterized in that the diff lock mechanism is released after the work clutch is in the “disengaged” state when operated to “disengage” / diff lock release.   The linkage mechanism includes a link mechanism that connects the work clutch operation mechanism and the differential lock mechanism, and the link mechanism includes a timing adjustment mechanism that releases the differential lock after the work clutch is in the “disengaged” state. The management machine according to claim 1, characterized in that:   The linkage mechanism includes a link mechanism that connects a work clutch operation mechanism and a diff lock operation mechanism, and a timing adjustment mechanism that releases the diff lock after the work clutch is in the “disengaged” state in the operation mechanism of the diff lock mechanism. The management machine according to claim 1, further comprising:

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