KR100399705B1 - Working apparatus - Google Patents

Abstract

In a work machine such as a combine, the configuration of the mechanical linkage mechanism 27 for linking the speed change control tool 24 and the steering control tool 26 to a pair of continuously variable transmissions 11 is simplified, and assembling and maintenance are possible. To improve the performance and reduce the manufacturing cost. In order to achieve this object, the mechanical linkage mechanism includes a first swinging member 28 that is capable of swinging around a first shaft center and a second swinging member 29 that can swing around a second shaft center different from the first shaft center. The shifting mechanism 24 is interlocked with the first swinging member 28, and the first swinging member swings around the first shaft center in conjunction with the operation of the shifting operation. And the steering manipulation tool 26 is interlocked with the second swinging member 29 and configured to swing the second swinging member about the second shaft center in conjunction with the operation of the steering manipulation tool. When the shift operation tool 24 is in the neutral position, even when the second swinging member 29 is interlocked by the steering operation tool 26, the continuously variable transmission device 11 is not shifted. When shift control tool 24 is in a position other than the said neutral position The continuously variable transmission device 11 is configured such that the stepless speed change device 11 is shifted while the second swinging member 29 is interlocked by the steering operation tool 26.

Description

WORKING APPARATUS}

The present invention relates to work machines such as combines. More specifically, the speed change control tool for performing the increase-deceleration operation in the forward direction or the reverse direction; A steering control section for turning in the left or right direction; A pair of left and right traveling devices; A pair of continuously variable transmissions that are electrically transmitted to each of the traveling devices; A mechanical linkage mechanism for linking the speed change control tool and the steering control tool to the pair of continuously variable transmissions; It relates to a work machine having a, and particularly relates to the operating structure of such a work machine.

As such a working machine, it is known that it is disclosed by Unexamined-Japanese-Patent No. 8-331972, for example. The operation structure of this work machine is comprised with the following mechanical linkage mechanisms.

That is, a pair of first drive rocking arms which swing around the axis of the shaft in the left and right directions, rotate about the axis of the shaft in the left and right directions, and which are relatively slidable relative to the drive shaft, and which can be rotated relative to the drive shaft. It is also equipped with a pair of support arms capable of sliding relative. The shift operation tool and the drive shaft are connected via a rod, and are linked with the operation of the shift operation tool so that the drive shaft rotates around the axis in the left and right directions. Further, the steering operation tool and the pair of first driving rocking arms and the support arms are connected through the pair of wire mechanisms and the pair of second driving rocking arms swinging around the longitudinal axis, and in conjunction with the operation of the steering control tools, The first driving rocking arm and the supporting arm on the side corresponding to the operation area are made to slide. In addition, the continuously variable transmission corresponding to the pair of the first driving rocking arm and the support arm is linked to the sliding motion of the first driving rocking arm and the support arm, and furthermore, the continuously variable transmission is linked to the sliding motion of the first driving rocking arm. An input rocking slide arm which slides integrally with the first drive rocking arm and the support arm so as to operate, and which swings around the first axis in the front-rear direction in conjunction with the rocking of the first drive rocking arm, and the slide of the input rocking slide arm. The output rocking arm swings around the second axis in the front-rear direction in association with the motion and rocking motion, and a wire mechanism extending from the output rocking arm to the continuously variable transmission. When the shift operation tool is located at the neutral position, the output rocking arm is set so as not to rock in accordance with the sliding motion of the input rocking slide arm. As a result, in the operation of the shift operation tool, it is possible to shift the pair of continuously variable transmissions with the same operation amount and to indicate the straight running state in which the right and left traveling devices are driven at constant speed, and the steering operation in the straight running state is also possible. By the operation of the sphere, the operation amount of the continuously variable transmission shifted at the same operation amount was made different, thereby making it possible to represent the turning driving state in which the left and right traveling devices were differentially made.

However, in the above-described prior art, the operation of the shift operation tool is first converted into swing around the axial center in the left and right directions of the first drive swing arm through the rod and the drive shaft, and then the front and rear directions of the input swing slide arm through the linkage rod. Is converted to swing around the first shaft center, and further converted to swing around the second shaft center in the front-rear direction of the output swing arm via a cam follower, and then transmitted to the continuously variable transmission through a wire mechanism. Further, operation of the steering operation tool is first converted into a longitudinal circumferential rocking of the second driving rocking arm via a wire mechanism, and then inputted according to the sliding motion of the first driving rocking arm and the supporting arm through the manual arm. The rocking slide arm is converted into a sliding motion, and further, through a cam follower, the rocking slide arm is converted to a rocking around the second axis in the front-rear direction of the output rocking arm, and then transmitted to the continuously variable transmission through a wire mechanism. In these prior arts, the structure of the mechanical linkage mechanism is complicated, resulting in irrationality and poor manufacturing cost, and inferior assembly and maintenance.

Accordingly, an object of the present invention is to solve the above problems, to simplify the configuration of the mechanical linkage mechanism, to improve the assemblability and maintainability, and to further reduce the manufacturing cost.

1 is an overall side view of a combine that is an example of a working machine according to the present invention;

2 is a schematic longitudinal rear view showing a transmission structure;

3 is a schematic longitudinal side view showing a transmission structure;

Figure 4 is a longitudinal rear view of the mission case.

Fig. 5 is a longitudinal sectional side view showing the configuration of the mechanical linkage mechanism in the first embodiment.

FIG. 6 is a plan view showing a configuration of a mechanical linkage mechanism in the first embodiment. FIG.

FIG. 7 is a longitudinal sectional view of a main portion showing the configuration of the mechanical linkage mechanism in the first embodiment; FIG.

FIG. 8 is an operation explanatory diagram showing a state of the mechanical linkage mechanism at the time of driving stop in the first embodiment; FIG.

FIG. 9 is an operation explanatory diagram showing a state of the mechanical linkage mechanism during straight traveling in the first embodiment. FIG.

FIG. 10 is an operation explanatory diagram showing a state of the mechanical linkage mechanism at the time of turning driving in the first embodiment. FIG.

FIG. 11 is an operation explanatory diagram showing a state of the mechanical linkage mechanism at the time of driving stop in the second embodiment; FIG.

12 is an operation explanatory diagram showing a state of the mechanical linkage mechanism at the time of straight running in the second embodiment.

FIG. 13 is an operation explanatory diagram showing a state of the mechanical linkage mechanism at the time of turning driving in the second embodiment; FIG.

(Explanation of symbols for the main parts of the drawing)

One; Traveling device 11; Continuously variable transmission

24; Shift control section 26; Steering Control

27; Mechanical linkages 28; Rotating member (first rocking member)

29; Rocking arm (second rocking member) 48; Rocking arm (first rocking member)

56; Upper link (second rocking member) P1; 1st core

P2; Second shaft center P4; 1st core

P5; 2nd core

In order to achieve the above object, the present invention provides the mechanical linkage mechanism comprising: a first swinging member capable of swinging around a first shaft center; and a second swinging member swingable around a second shaft center different from the first shaft center. And the shift operation tool is interlocked with the first swing member, the first swing member is oscillated around the first axis in response to the operation of the shift operator, and the steering operation tool is Interlocked with a second swinging member, the second swinging member swinging around the second shaft in cooperation with the steering operation, and the steering operation when the shifting operation tool is in a neutral position. Even when the second swinging member is interlocked by the operation of the sphere, the continuously variable transmission is not shifted, and when the shift operation tool is at a position other than the neutral position, the operation The stepless speed shifting device is characterized in that the stepless speed shifting device is operated by interlocking the second swinging member by the operation of the incense control tool.

If comprised in this way, operation of a shift operation tool will be transmitted to each continuously variable transmission via a 1st swinging member. However, when the shift control tool is in the neutral position (i.e., the driving stop position where the traveling speed of the aircraft becomes zero), the operation of the steering control tool is only converted to the swing around the second shaft center of the second swing member. It is not delivered to each CVT. On the other hand, when the speed change control tool is in a position other than the neutral position, the operation of the steering control tool is transferred to the corresponding continuously variable transmission after the operation of the steering control tool is converted to the swing around the second shaft center of the second swing member.

In other words, the operation of the shift control tool is simply converted to the swing around the first axial center of both rocking arms and transmitted to each continuously variable transmission. The pair of continuously variable transmissions are shifted at the same operation amount to shift the left and right traveling devices. It can represent the straight driving state to drive the constant speed. In addition, the operation of the steering operation tool in the straight traveling state is converted only to the swing around the second shaft center of the second swinging member and transmitted to the corresponding continuously variable transmission, and the operation amount of each continuously variable transmission is different. It is possible to indicate the turning driving state in which the left and right traveling devices are differentially given. In addition, in the traveling stop state in which the shift control tool is positioned at the neutral position, even if the steering control tool is operated, the rocking arm of the side corresponding to the operating area only swings around the second axis, and the continuously variable transmission is shifted. Therefore, the driving stop state can be maintained.

Therefore, the configuration of the mechanical linkage mechanism can be simplified, so that the desired straight driving state can be indicated by the operation of the shift control tool, and the desired turning driving state can be indicated by the operation of the steering control tool. It is possible to improve the assemblability and maintenance of the mechanism, and to further reduce the manufacturing cost. In addition, malfunctions of the steering control tool in the driving stop state in which the shift control tool is positioned at the neutral position prevent the occurrence of a disadvantage that the aircraft turns unpredictably.

In the above configuration, for example, as described in claim 2, the second oscillating member is connected to the first oscillating member, and the first shaft core and the second shaft core extend in different directions, and the second oscillation The member swings around the first shaft center when the first swing member swings around the first shaft center in conjunction with the operation of the shift operation tool, and independently of the swing, the member swings around the first shaft center. It is preferable to be able to oscillate about the said 2nd shaft center in interlock | cooperation.

In this configuration, the operation of the shift operation tool is transferred to each continuously variable transmission after being converted into a swing around the first axial center of the second swing member through the first swing member. Therefore, the transmission system of the operating force of the shift control tool and the transmission system of the operating force of the steering control tool are partially used in common, and the structure of the mechanical linkage mechanism can be further simplified.

Moreover, since the operation of the steering operation tool is performed by swinging the second swing member around the second axis center independently of the swing of the first swing member based on the operation of the shift operator, the shift control tool is moved to the neutral position. When located in the above position, it is possible to reliably avoid the disadvantage that the gas turns unpredictably due to the malfunction of the steering operation tool.

In addition to the above configuration, as described in claim 3, the second swinging member is interlocked with the continuously variable transmission device through a sliding member that is pushed and pulled in a straight line, and the shifting operation member is connected to the sliding member. If an engaging groove is formed along the swinging direction of the second swinging member on the basis of the operation of the steering operation tool in the neutral position, it is advantageous in the following points.

With this arrangement, in the driving stop state in which the shift control tool is located at the neutral position, even if the steering control tool is operated, the second swing member only swings along the engaging groove of the swing member, and the sliding member is pushed and pulled. It doesn't work. That is, the operation of the steering operation tool is resonant, and the continuously variable transmission cannot be shifted. As a result, the driving stop state can be maintained despite the operation of the steering control tool.

On the other hand, in the straight driving state in which the shift control tool is positioned at a position other than the neutral position, when the steering control tool is operated, the second swinging member presses the side wall of the engaging groove to push and pull the swinging member, so that the corresponding stepless operation is performed. It is possible to shift the gearbox. As a result, it is possible to indicate the turning driving state according to the operation of the steering control tool.

That is, with the simple configuration of simply engaging the second swinging member with the engaging groove of the sliding member, in the driving stop state, the driving stop state can be maintained in spite of the operation of the steering operation tool, and also the straight running state In this case, the turning driving state according to the operation of the steering control tool can be indicated.

Therefore, it is possible to easily and reliably avoid the occurrence of the disadvantage that the aircraft turns by the misoperation of the steering control tool in the running stop state in which the shift control tool is positioned at the neutral position.

Further, as described in claim 4, when the spherical body is equipped at the engaging position with the sliding member in the second rocking member, the second rocking member with respect to the sliding member in the engaging groove of the sliding member is provided. The relative movement can be made smooth, and it can be advantageous in view of the operability to perform the light-pushing operation of the sliding member by the swinging of the second swinging member and the steering operation by the steering operation tool more lightly.

Other features of the present invention, and effects and advantages of the present invention will become apparent by reading the following description with reference to the drawings.

(Embodiment of invention)

Hereinafter, two examples of the working machine according to the present invention will be described. In either embodiment, the combine is an example of the work machine.

(1st embodiment)

In Fig. 1 the whole side of the combine is shown. The combine harvests the planting grain stem in front of the traveling body 2 traveling by the drive of a pair of right and left crawler-type traveling devices (an example of the traveling device) 1 and conveys it toward the rear. Threshing device 4 and threshing device 4 which connect the conveying apparatus 3 so that relative lift is possible and receive threshing and selection process by the cutting conveying apparatus 3 to the traveling body 2, and threshing apparatus 4 In addition to mounting the grain tank (5) for storing the grains in the (6), it is configured to form a boarding driver (6) in the front position of the grain tank (5).

2 to 4, in this combine, power from the engine 7 is transmitted to the input shaft 10 of the mission case 9 via the belt tension main clutch 8. On the input shaft 10, a pair of hydrostatic continuously variable transmissions 11 for driving (an example of the continuously variable transmission, hereinafter referred to as a traveling HST) and a hydrostatic continuously variable transmission for working (hereinafter referred to as a working HST) To 12. Thereafter, the power after the shift is transmitted to the crawler-type traveling device 1 on the left side through the gear transmission 13 on the left side by one driving HST 11, and the other traveling HST 11 on the other side. Is transmitted to the crawler-type traveling device 1 on the right side via the gear-type transmission device 13 on the right side. Further, the power after the shift is transmitted to the cutting transfer device 3 through the belt tensioning type clutch 14 by the working HST 12. That is, the left and right crawler type traveling apparatus 1 is driven individually by the power from the engine 7 transmitted through the reacting traveling HST 11.

Between the left and right gear transmissions 13, these electric shafts 15 are intermittently intermittently driven to uniformly drive the left and right crawler type traveling devices 1 and the right and left crawler type traveling devices 1. A multi-plate hydraulic clutch 16 for switching to a state that allows operation of the device is provided.

As shown in Fig. 4, the mission case 9 has a two-part structure that can be separated from right to left, and includes a left-right gear type transmission 13, a hydraulic clutch 16, and the like, and at the left side wall thereof. As a part of 17 swells outward, it is formed so that it may have the recessed part 18 which accommodates each traveling HST 11 and the HST 12 for a job. Each driving HST 11 and work HST 12 accommodates two axle-type piston pumps 19 and piston motors 20 for driving in the recesses 18 of the mission case 9. And a port block in which a flow path for accommodating axle-type piston pumps 21 and piston motors 22 for work and connecting their corresponding piston pumps 19 and 21 and piston motors 20 and 22 is formed. It is comprised by connecting 23 to the side wall 17 of the left side, and closing the recessed part 18. FIG.

In other words, the side wall 17 of the mission case 9 is effectively used for the casings of the HSTs 11 and 12, thereby reducing the number of parts and the manufacturing cost. Moreover, since each HST 11 and 12 is comprised using the recessed part 18 of the side wall 17, each HST 11 and 12 will go into the inside of the mission case 9 largely, and it is necessary to install them. The space to be made small and the overall combine are miniaturized.

As shown in FIG. 1, the boarding and driving part 6 has a single peripheral speed lever 24 (an example of the shift operation tool) 24 that can swing in the front-rear direction, and a single sub-speed lever 25 that can swing in the front-rear direction. ), And a single steering lever (an example of steering control tool) 26 capable of oscillating in the left-right direction and the like.

As shown in FIGS. 5-10, the peripheral speed lever 24 and the steering lever 26 are connected to each running HST 11 through the mechanical linkage mechanism 27. As shown in FIG. This mechanical linkage mechanism 27 is comprised as follows.

That is, the rotating member (an example of the first rocking member) 28 that rotates around the first shaft center P1 swings around the first shaft center P1 in the rotation, and is independent of the rocking, A pair of rocking arms (an example of the second rocking member) 29 that is swingable around the second shaft center P2 perpendicular to the first shaft center P1 is connected.

The first linkage of the push-pull type, such that the peripheral speed lever 24 and the rotational member 28 rotate with respect to the operation of the peripheral speed lever 24 so that the rotational member 28 rotates around the first axis P1. It is connected via (30). A pair of steering lever 26 and each rocking arm 29 are interlocked with the steering lever 26 to operate so that the rocking arm 29 on the side corresponding to the operating area swings around the second axis P2. It is connected via the second linkage 31 of the push-pull type. Each swing arm 29 and the trunnion shaft 32 of the HST 11 corresponding to the swing arm 29 are rotated in conjunction with the swing of the swing arm 29 so that the trunnion shaft 32 rotates around the axis P3. It is connected via the 3rd linkage tool 33 of a push pull type so that it may operate.

The rotation member 28 includes a rotation shaft 35 supported by a rotational freedom path around the first shaft center P1 on the support frame 34 adjacent to the mission case 9, and around the first shaft center P1 at both ends thereof. It is comprised by the bracket 36 connected etc. so that it may rotate integrally. The rocking arm 29 corresponding to each bracket 36 is rotatably supported around the 2nd shaft center P2.

The first linkage 30 causes the rotational member 28 to rotate forwardly around the first shaft center P1 in response to an oscillating operation in the forward acceleration direction (reverse deceleration direction) of the peripheral speed lever 24. The rotation member 28 is moved around the first shaft center P1 in accordance with the first release wire 37 for the forward acceleration and the swinging operation in the backward acceleration direction (the forward deceleration direction) of the peripheral speed lever 24. It consists of the 2nd release wire 38 for reverse acceleration which reverses with a.

Each of the second linkages 31 is a release wire 39 for rocking the corresponding rocking arm 29 in accordance with an operation in a direction away from the neutral position of the steering lever 26, the rocking arm 29, It consists of a spring 40 which presses the steering lever 26 toward the neutral direction through the release wire 39.

Each third linkage 33 includes a pair of rollers 42 guided by the rails 41 of the support frame 34 and engages with the operation ends of the corresponding swinging arms 29. The sliding member 44 in which the groove | channel 43 was formed is comprised, and the rod 46 hypothesized from the sliding member 44 to the operating arm 45 of the trunnion shaft 32 is comprised. Each 3rd linking tool 33 can interlock | pulse and operate the rod 46 in a straight line according to the rail 41 in conjunction with the rocking | fluctuation of the rocking arm 29. As shown in FIG. The operation end of each rocking arm 29 engaged with the engaging groove 43 of the sliding member 44 is a relative of the operating end of the rocking arm 29 with respect to the sliding member 44 in the engaging groove 43. The spherical body 47 which equips the smooth movement of the pushing-pull operation | movement on the straight line of the sliding member 44 by the oscillation of the rocking arm 29 is equipped with the smooth movement.

In this embodiment, when the trunnion shaft 32 of each traveling HST 11 pushes the corresponding 3rd linkage 33 to the HST 11 side by the rocking arm 29, the shaft center (P3) The forward rotation operation is performed in the forward acceleration speed (reverse deceleration direction) to the surroundings. Conversely, when the corresponding third linkage 33 is pulled toward the side away from the HST 11 by the rocking arm 29, the reverse operation is performed in the reverse acceleration direction (forward / deceleration direction) around the axis P3. It becomes.

The engagement groove 43 is formed to conform to the swinging direction of the swinging arm 29 based on the operation of the steering lever 26 when the peripheral speed lever 24 is positioned at the neutral position. In other words, when the peripheral speed lever 24 is positioned at the neutral position, the second shaft center P2 of the swinging arm 29 is set in accordance with the operation direction of the third linkage 33. Therefore, in the neutral position of the peripheral speed lever 24, even if the rocking arm 29 oscillates around the 2nd shaft center P2 by the steering lever 26, the sphere formed in the operation end of the rocking arm 29 will be carried out. Since the upper body 47 only swings the inside of the engagement groove 43 and does not come into contact with the sliding member 44, the swinging of the swinging arm 29 is caused by the sliding member 44 (and further, the third linkage). It is not converted to the pushing and pulling operation of the rod 46 of (33). Therefore, the operation of the steering lever 26 is not transmitted to the trunnion shaft 32 of the traveling HST 11, and the resonance is performed.

Although not shown, the steering lever 26 has a switching valve for switching the flow state of the hydraulic oil with respect to the hydraulic clutch 16 based on the operation position thereof through a mechanical or electric linkage mechanism. When the steering lever 26 is in the neutral position, hydraulic oil is supplied to the hydraulic clutch 16 so that the hydraulic clutch 16 which connects the transmission shafts 15 of the left and right gear transmissions 13 cannot be turned. Status appears. On the other hand, when the steering lever 26 is not in the neutral position, the hydraulic oil is discharged from the hydraulic clutch 16, and the hydraulic clutch 16 intermittently interlocks the transmission shafts 15 of the left and right gear type transmissions 13 with each other. Turnable state is indicated.

8 and 9, when the peripheral speed lever 24 swings back and forth, the rotating member 28 rotates around the first shaft center P1 in conjunction with the operation. At the same time, both rocking arms 29 swing together around the first axis P1. Due to the swing, both third linkages 33 are pushed and pulled in the same direction at the same operation amount, and the trunnion shaft 32 of both HST 11 is moved in accordance with the operation position of the peripheral speed lever 24. It is located at the same operation position. As a result, when the peripheral speed lever 24 is oscillated to the forward operation area on the front side than the neutral position, the crawler type traveling device 1 on the left and right is moved at a driving speed corresponding to the operation position of the peripheral speed lever 24. It can represent a forward straight state of constant velocity electrostatic driving. On the contrary, when the peripheral speed lever 24 is oscillated in the backward operation area on the rear side of the neutral position, the crawler type traveling device 1 on the left and right sides at the driving speed according to the operation position of the peripheral speed lever 24 is constant. Reverse driving may indicate the rear straight state. Moreover, when the peripheral speed lever 24 is rocked and operated to a neutral position, it becomes possible to show the traveling stop state which stops the crawler-type traveling apparatus 1 on either side.

In other words, by operating the peripheral speed lever 24, it is possible to switch between forward and backward steps and stepless speed shift operation, and to easily display the front straight state and the rear straight state at a desired speed.

In the front straight state or the rear straight state described above, as shown in FIG. 10, when the steering lever 26 is swung in the left and right direction, the swing arm 29 corresponding to the operation direction is moved to the second axis P2. Rocking around, the third linkage (33) connected to the rocking arm (29) is pushed and pulled, and the trunnion shaft (32) of the corresponding HST (11) is moved by the peripheral speed lever (24). From the operation position corresponding to the operation position, the steering lever 26 is operated in the deceleration direction by the operation amount corresponding to the operation amount at the neutral position.

Thus, when the steering lever 26 is rocked to the operation area on the left side than the neutral position, the driving speed of the left crawler traveling device 1 corresponding to the operation direction is set from the neutral position of the steering lever 26. It can decelerate by the speed | rate in accordance with the operation amount of, and can show the left turning state which differentials the crawler-type traveling apparatus 1 on either side. On the contrary, when the steering lever 26 is rocked to the operation area on the right side rather than the neutral position, the driving speed of the crawler type traveling device 1 on the right side corresponding to the operation direction is set at the neutral position of the steering lever 26. By decelerating by the speed corresponding to the operation amount, it is possible to indicate a priority state in which the right and left crawler-type traveling devices 1 are differential.

That is, in each of the left and right swing states, since the crawler-type traveling device 1 on the inside of the swing is decelerated, compared to the case where the crawler-type traveling device 1 on the outside of the swing is increased, the gas can be smoothly turned. have.

The mechanical linkage mechanism 27 moves the trunnion shaft 32 of the corresponding HST 11 from the operation position corresponding to the operation position of the peripheral speed lever 24 by the rocking operation of the steering lever 26. It is designed to be operated up to the operating area on the opposite side beyond the neutral position.

As a result, in the left and right swinging states, the normal turning state for giving the speed difference while driving the right and left crawler type traveling devices 1 in the same direction by the operation of the steering lever 26, and one crawler type traveling device ( The pivot swing state for driving stop 1) and the spin swing state for driving the crawler-type traveling device 1 on the right and left in the reverse direction can be easily shown.

Further, as shown in Figs. 5, 6 and 8, even when the steering lever 26 is rocked in the traveling stop state in which the peripheral speed lever 24 is operated to the neutral position, as described above, Since the rocking arm 29 on the side corresponding to the operation area only swings along the engagement groove 43 of the sliding member 44, the sliding member 44 does not come into contact with the sliding member 44, so that each HST 11 The trunnion shaft 32 cannot be operated. As a result, despite the rocking operation of the steering lever 26, the driving stop state can be maintained, and the misalignment of the steering lever 26 in the driving stop state in which the peripheral speed lever 24 is positioned at the neutral position can be achieved. This makes it possible to avoid the disadvantage of the gas unpredictably turning.

In addition, although not shown, the peripheral speed lever 24 is connected to the trunnion shaft of the working HST 12 through a mechanical or electrical linkage mechanism. Then, in the state where the peripheral speed lever 24 is operated in the forward operation region, the trunnion shaft of the working HST 12 is operated from the neutral position corresponding to the operation position of the peripheral speed lever 24 (the transfer conveying apparatus ( 3) is located at the operation position on the side of conveying the grain stem toward the threshing apparatus 4 side. In the state where the peripheral speed lever 24 is operated in the reverse operation region, the trunnion shaft of the working HST 12 is positioned at the neutral position irrespective of the operating position of the peripheral speed lever 24. This makes it possible to shift the mowing conveyance speed between the grains by the mowing transport device 3 in synchronization with the traveling speed shifted by the respective HSTs 11 for traveling during the forward working run, and in spite of the traveling speed. The harvested crops can be harvested and transported in a preferable state.

In addition, the sub transmission lever 25 is operated by the gear transmission mechanism 13 to the gear transmission mechanism 13 via a mechanical or electric linkage mechanism, and the power after the shift by the respective traveling HSTs 11 is operated. It is linked to shift to two stages of high and low.

(2nd embodiment)

Next, a second embodiment of the present invention will be described. In addition, in 2nd Embodiment, only the structure of the mechanical linkage mechanism 27 differs from 1st Embodiment mentioned above. Therefore, below, only the structure of the mechanical linkage mechanism 27 is demonstrated.

11 to 13, in the second embodiment, the mechanical linkage mechanism 27 includes a pair of rocking arms (an example of the first rocking member) 48 that oscillates integrally around the first shaft center P4. And a pair of link mechanisms 49 in the form of parallel link links connected thereto. Each of the link mechanisms 49 includes a vertical link 50 that moves in parallel with a connection forming a pair of second shaft centers P5, and an upper link (second swing member) that swings around the second shaft center P5. 56 and a downlink 56a. Each rocking arm 48 is connected to the longitudinal link 50 via a coupling pin 51. When each rocking arm 48 swings, the longitudinal link 50 of the corresponding link mechanism 49 moves in parallel with the pair of second shaft centers P5 as a starting point. Longitudinal holes 52 and 53 are formed in each rocking arm 48 and each longitudinal link 50 to allow movement of the linking pins 51 in the longitudinal direction thereof.

The peripheral speed lever 24 and the pair of swinging arms 48 are connected through the first linkage 54 of the push-pull type, interlocked by the operation on the peripheral speed lever 24, and the pair of swinging arms 48. It is made to oscillate integrally around this 1st shaft center P4.

In addition, the steering lever 26 and the pair of linking pins 51 are connected through a pair of push-pull second linkages 55 and interlocked by the steering lever 26 to correspond to the operation area. The linking pin 51 on the side is moved along the long hole 52 of the corresponding swinging arm 48.

In addition, the upper link 56 of each link mechanism 49 and the trunnion shaft 32 of the HST 11 corresponding to them are connected via the third link mechanism 57 of the push-pull type. In conjunction with the swing of the link 56, the trunnion shaft 32 is pivotally operated around the shaft center P3. However, when the peripheral speed lever 24 is in a neutral position, the long hole 52 of each rocking arm 48 and the long hole 53 of each longitudinal link 50 are set to correspond. For this reason, even when the steering lever 26 is operated, the linking pin 51 on the side corresponding to the operation area is moved only along the longitudinal direction of both long holes 52 and 53, and the upper link 56 ), The pushing and pulling operation of the third linkage 57 does not occur. Therefore, the operation of the steering lever 26 is not transmitted to the trunnion shaft 32 of the traveling HST 11, and the resonance is performed.

The first linkage 54 integrates a pair of rocking arms 48 around the first shaft center P4 according to the forward rocking operation of the peripheral speed lever 24 in the forward speed increasing direction (reverse speed decreasing direction). The first release wire 58 for oscillating forward acceleration, and the pair of rocking arms 48 in accordance with the oscillation operation in the rearward acceleration direction (forward deceleration direction) of the peripheral speed lever 24 are arranged in the first shaft center. (P4) It consists of the 2nd release wire 59 for reverse acceleration which integrally swings around.

Each second linkage 55 pushes the corresponding linkage pin 51 along the long hole 52 of the swinging arm 48 in accordance with the operation in the direction away from the neutral position of the steering lever 26. The release wire 60 to operate, and the spring (not shown) which pushes and presses the linking pin 51 along the long hole 52 of the swinging arm 48 are comprised.

Each third linkage 57 is formed by rod 62 hypothesized over the upper link 56 of each link mechanism 49 and the operation arm 61 of the trunnion shaft 32 corresponding thereto. Consists of.

When the corresponding third linkage 57 pushes the HST 11 side by the upper link 56, the trunnion shaft 32 of each traveling HST 11 is positioned around the shaft center P3. It is designed to operate electrostatically in the forward acceleration direction (reverse deceleration direction). Conversely, if the corresponding third linkage 57 is pulled to the side spaced apart from the HST 11 by the upper link 56, the trunnion shaft 32 of each traveling HST 11 is Reverse operation is performed in the reverse acceleration direction (forward deceleration direction) around the axis P3.

11 and 12, when the peripheral speed lever 24 is oscillated in the forward direction, both swing arms 48 are integrated around the first axis P4 in conjunction with the operation. The oscillation causes the two links 49 to move in parallel in the same direction in the same direction from the corresponding second axis P5 as a starting point. Then, both third linkages 57 are pushed and pulled in the same direction with the same operation amount, so that the trunnion shaft 32 of both HST 11 has the same operation position according to the operation position of the peripheral speed lever 24. It is intended to be located at.

As a result, when the peripheral speed lever 24 is oscillated in the forward operation area on the front side of the neutral position, the crawler-type traveling device 1 on the left and right at constant speed is driven at the driving speed according to the operation position of the peripheral speed lever 24. It can represent the forward driving state of the electrostatic drive. On the contrary, when the peripheral speed lever 24 is oscillated to the backward operation area behind the neutral position, the crawler-type traveling device 1 on the left and right is rotated at constant speed at a driving speed corresponding to the operation position of the peripheral speed lever 24. It may indicate a driving backward direction. Further, when the peripheral speed lever 24 is oscillated to a neutral position, it is possible to indicate a traveling stop state in which the left and right crawler-type traveling devices 1 are stopped.

That is, by the operation of the peripheral speed lever 24, it is possible to switch between forward and backward steps and stepless shift operation, and further, the front straight state and the rear straight state can be easily displayed at a desired speed.

In the front straight state or the rear straight state described above, as shown in FIG. 13, when the steering lever 26 is swung in the left and right direction, the connecting pin 51 corresponding to the operation direction is connected to the second linkage. It is operated along the long hole 50 of the rocking arm 48 via the sphere 55. By this operation, the corresponding link mechanism 49 moves in parallel with the second shaft center P5 as a starting point, and the third linkage 57 connected to the link mechanism 49 is pushed and operated to respond. The trunnion shaft 32 of the HST 11 is moved in the deceleration direction by an operation amount corresponding to the operation amount at the neutral position of the steering lever 26 from the operation position corresponding to the operation position of the peripheral speed lever 24. To be manipulated.

As a result, when the steering lever 26 is rocked to the operation area on the left side rather than the neutral position, the driving speed of the crawler-type traveling device 1 on the left side corresponding to the operation direction is adjusted from the neutral position of the steering lever 26. It can decelerate by the speed | rate in accordance with the operation amount of, and can show the left turning state which differentials the crawler-type traveling apparatus 1 on either side. Conversely, when the steering lever 26 is rocked to the steering area on the right side rather than the neutral position, the driving speed of the crawler type traveling device 1 on the right side corresponding to the operation direction is adjusted from the neutral position of the steering lever 26. It decelerates by the speed according to the operation amount, and it is possible to show the priority state in which the right and left crawler-type traveling devices 1 are differential.

In addition, the mechanical linkage mechanism 27 controls the trunnion shaft 32 of the corresponding HST 11 by the swinging operation of the steering lever 26 to correspond to the operation position of the peripheral speed lever 24. Is configured to be operated up to the operating area on the opposite side beyond the neutral position. As a result, in the left and right swinging states, by operating the steering lever 26, the crawler type traveling device in which the left and right crawler type traveling devices 1 are driven in the same direction while giving a speed difference and one crawler type traveling device ( Each of the pivot swing state for driving stop 1) and the spin swing state for driving the crawler-type traveling device 1 on the right and left in the reverse direction are easily shown.

However, as shown in FIG. 11, in the running stop state in which the peripheral speed lever 24 is operated to the neutral position, as described above, the long hole 52 and the longitudinal link 50 of the rocking arm 48 are separated. Since the long holes 53 coincide with each other, even when the steering lever 26 is rocked, the linking pins 51 on the side corresponding to the operation area move only along the respective long holes 52, 53. Since the three linkages 57 are not pushed and operated, the trunnion shaft 32 of each HST 11 cannot be operated. As a result, despite the rocking operation of the steering lever 26, the driving stop state can be maintained, and in the traveling stop state in which the peripheral speed lever 24 is positioned at the neutral position, by the misoperation of the steering lever 26. The disadvantage of gas unpredictably turning can be avoided.

(Other embodiment)

Hereinafter, other embodiment of this invention is listed.

[1] The working machine may be a ginseng harvester, a non-harvester or the like instead of a combine.

[2] As the continuously variable transmission 11, a belt type continuously variable transmission may be used instead of the hydrostatic stepless transmission HST.

[3] As the shift operation knob 24, a shift pedal or the like may be used instead of the illustrated lever.

[4] As the steering operation tool 26, a steering wheel or the like may be used instead of the illustrated lever.

[5] In the first embodiment, the first linkage tool 30 and the second linkage mechanism 31, and in the second embodiment, the first linkage tool 54 and the second linkage tool 55 are push-pull. It may be made of wire or rod. In addition, in 1st Embodiment, the 3rd linkage 33 may be comprised with a push pull wire, a rod, a release wire, and a spring. In addition, in 2nd Embodiment, the 3rd linking tool 57 may be comprised from a push pull wire, a release wire, and a spring.

[6] The mechanical linkage mechanism 27 may be configured so as to show only a normal turning state that gives a speed difference while driving the left and right traveling apparatuses 1 in the same direction by the operation of the steering operation tool 26. It may be configured to show the normal turning state and the pivot turning state for driving stop of one travel device 1.

[7] A state in which only the normal turning state giving the speed difference while driving the mechanical linkage mechanism 27 in the same direction and the left and right traveling devices 1 can be displayed, and the pivot turning state can be shown in addition to the normal turning state. The state may be configured to enable switching between two states. The two states and the two states, and in addition to the two states, may be configured to be switched to the three states in which the spin turning state for driving the right and left crawler-type traveling devices 1 in the reverse direction is possible.

According to the present invention, the configuration of the mechanical linkage mechanism can be simplified, and the assemblability and maintenance property can be improved, and the manufacturing cost can be reduced.

Claims (4)

A shift operation tool 24 for carrying out the increase / deceleration operation in the forward direction or the reverse direction; A steering control section 26 for turning in the left or right direction; A pair of left and right traveling devices 1; A pair of continuously variable transmissions (11) which are electrically transmitted to each of said traveling devices (1); A mechanical linkage mechanism 27 for linking the shift control tool 24 and the steering control tool 26 with the pair of continuously variable transmissions 11; As a work machine provided with, The mechanical linkage mechanism 27 is capable of oscillating around the first shaft centers P1 and P4, and a second oscillation around the second shaft center P2 different from the first shaft center. A rocking member (29; 56), The shift operation tool 24 is connected to the first swing member 28 in conjunction with the operation of the shift operation tool, the first swing member is configured to swing around the first shaft center, The steering operating tool 26 is interlocked with the second oscillating member 29; 56, and configured to oscillate around the second shaft center in response to the operation of the steering operating tool; When the shift operation tool 24 is in the neutral position, the continuously variable transmission device 11 is not shifted even when the second swinging members 29 and 56 are interlocked by the steering operation tool 26. Without, When the speed change control tool 24 is in a position other than the neutral position, the second swinging members 29 and 56 are interlocked by the operation of the steering control tool 26, and the continuously variable transmission device 11 ) Is shifted operation. The method of claim 1, wherein the second rocking member 29 is connected to the first rocking member 28, and the first shaft core P1 and the second shaft core P2 extend in different directions. , The second swinging member 29 oscillates around the first shaft center when the first swinging member swings around the first shaft center in conjunction with the operation of the shift operation mechanism 24. Independently of, the work machine characterized in that the swinging around the second axis (P2) in conjunction with the operation of the steering operation tool (26). The method of claim 2, wherein the second swinging member 29 is interlocked with the continuously variable transmission device 11 through a sliding member 44 which is pushed and pulled in a straight line, Engaging grooves 43 are formed in this sliding member in accordance with the swinging direction of the second swinging member based on the operation of the steering operating tool 26 when the shift operating tool 24 is in the neutral position. The work machine characterized by the above-mentioned. 4. The work machine according to claim 3, wherein a spherical body (47) is provided at an engagement position with the sliding member in the second rocking member.