KR101529436B1 - Traveling speed change structure for work vehicle - Google Patents

Abstract

In the traveling transmission structure of the work vehicle, the vicinity of the continuously variable transmission for traveling in the transmission case is made compact. For this purpose, a recess 10a is formed in one side of the mission case 10 to enter the other side, and an input shaft 22 of the mission case 10 is provided on the other side of the mission case 10. The continuously variable transmission device 11 for traveling is disposed in the recessed portion 10a of the transmission case 10 so that the output shaft 11c of the continuously variable transmission device 11 for traveling is linked to the input shaft 22 in an interlocked manner. And transmission gears 30 and 31 for transmitting the power of the input shaft 22 downward are provided on the other side of the mission case 10. The transmission case 29 is supported by the transmission case 10 so that the power of the transmission gears 30 and 31 is transmitted to the input shaft 22 side (the other side of the transmission case) of the transmission shaft 29, The right and left side clutches 34 are provided on the concave portion 10a side (one side of the transmission case) of the coaxial shaft 29 (see Fig. 7)

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a traveling-

The present invention relates to a work vehicle such as a combine.

[One]

The combine, which is an example of a work vehicle, includes a continuously variable transmission for traveling and a mission case as disclosed in JP-A-2003-094968, for example. In JP-A-2003-094968, a continuously variable transmission for traveling (9 in Fig. 2 and Fig. 3) is arranged on the lateral side of the upper part of the transmission case (8 in Figs. 2 and 3) The output shaft of the continuously-variable shifting device is inserted into the interior of the transmission case, and is disposed at the right and left center of the transmission case as an input shaft (48 in Figs. 2 and 3) of the transmission case.

In JP-A-2003-094968, a transmission shaft (a transmission shaft supported by bearings 49 in Fig. 3) is supported on the left and right sides of the lower portion of the transmission case, so that the power of the input shaft of the transmission case, And is transmitted to the right and left central portions of the transmission shafts via the transmission gears disposed at the center. (Fig. 2 and Fig. 3) are provided at the right and left ends of the transmission shaft, so that the power of the transmission shaft is transmitted through the right and left side clutches to the right and left traveling devices And 1 in Fig. 2).

As a result, when the right and left side clutches are operated to the power transmission state, power is transmitted to the right and left traveling devices, and the gas straightens. When the left side clutch is operated to the cut-off state and the left side clutch is operated to the power transmission state, the base body changes direction to the right, the left side clutch is operated to the cutoff state, and the right side clutch is switched to the electric state When operated, the gas changes direction to the left.

[2]

The combine, which is an example of a work vehicle, includes a continuously variable transmission for traveling and a mission case as disclosed in, for example, JP-A-2001-054314. In JP-A-2001-054314, a continuously variable transmission for driving (M in Fig. 1) is arranged on the lateral side of the upper portion of the transmission case (2 in Fig. 1). 1) of the continuously variable transmission for driving is inserted into the interior of the transmission case and the power of the output shaft of the traveling continuously variable transmission is transmitted via the transmission gear to the input shaft (21 in Fig. 1) of the transmission case And the input shaft (21 in Fig. 1) of the mission case is disposed at the left and right center of the mission case.

In JP-A-2001-054314, right and left output gears (12 in Fig. 1) for transmitting power to the right and left traveling devices (4 in Fig. 1) are arranged at left and right centers of the mission case, (11 in Fig. 1) capable of being slidably operated on the right and left sides of the transmission case.

Thus, when the transmission gear (11 in Fig. 1) is slid to engage with the transmission gear (27 in Fig. 1), low-speed power is transmitted to the right or left traveling device To the other side (right or left output gear) of the output shaft. (Right output gear) is driven in the forward direction and the left-side running gear (left-side output gear) is driven in the forward direction at low speed, for example, Due to the difference in speed of the traveling device on the left side, the gas turns to the left side.

When the transmission gear (11 of Fig. 1) is slid in the reverse direction to engage with the transmission gear (9 of Fig. 1), the power in the opposite direction to the one of the right or left traveling devices is transmitted to the other Right or left output gear) is obtained. (Right output gear) is driven in the forward direction and the left traveling device (left output gear) is driven in the backward direction, for example, in the reversed state, the right and left traveling By the opposite direction of the driving direction of the apparatus, the gas is pivoted to the left (extreme pivoting state).

[3]

The combine is provided with a support frame capable of pivoting up and down as shown in JP-A-2000-335439 and supporting a preload part (3 in Fig. 1), a driving part (8 in Fig. 1) 2 of 17 are arranged in the left-right direction on the front portion of the base. In JP-A-2000-335439, the operation part is provided on the outside of the right side of the transmission case on the right side, and the support frame is provided on the outside of the other side of the left side of the transmission case.

JP-A-2000-335439 discloses a hydraulic transmission mechanism (23, 36 in Figs. 2 and 4) for traveling or swinging is built in a transmission case. By operating the hydraulic system of the transmission case, Operation or turning operation is performed.

[4]

In the combine which is an example of the work vehicle, the sub-speed change operation sockets for operating the peripheral speed control device and the sub speed change device for operating the peripheral devices are arranged in parallel in the operation control space -A-2007-159467 (paragraphs [0037], [0041] to [0043], Figs. 2 and 7 to 9).

[One]

Problems corresponding to the background art [1] are as follows.

In JP-A-2003-094968, a continuously variable transmission for driving is disposed on a lateral side of a transmission case, and a continuously variable transmission for driving is projected largely to a lateral side from a lateral side of the transmission case. Thus, there is room for improvement in terms of compactness in the vicinity of the continuously variable transmission for traveling in the mission case.

An object of the present invention is to make the vicinity of a continuously variable transmission for traveling in a transmission case compact in a traveling transmission structure of a work vehicle.

[2]

Problems corresponding to the background art [2] are as follows.

JP-A-2001-054314 is structured so as to obtain a complete turn state and an extensional turning state by sliding the electric gear and engaging it with another electric gear. However, for the driver, the sliding operation of the electric gear generally does not fit well unless the operation is heavy and the engagement of the electric gears does not coincide with the phases, so there is room for improvement in terms of operability.

Therefore, the configuration for obtaining the complete turn state and the extensional turning state by sliding the electric gear is eliminated, and the low speed power is transmitted to the other side of the right or left traveling device in the same direction as the right or left traveling device Type friction-relieving clutch, and a multi-disc friction-reverse clutch capable of transmitting power in a direction opposite to that of one of the right or left traveling devices to the other of the traveling devices on the right or left side, It has been proposed to construct a configuration for obtaining a state with good operability.

The present invention relates to a traveling transmission structure for a work vehicle, which includes a continuously variable transmission for traveling and a mission case, and includes a complete line clutch and a reverse clutch, So as to achieve compactness in the vicinity of a continuously variable transmission for traveling in a transmission case.

[3]

Problems corresponding to the background art [3] are as follows.

JP-A-2000-335439 has an oil pressure unit (42 in Fig. 4) provided with a control valve (38, 39, 41 in Fig. 4)

The present invention relates to a combine comprising a support frame capable of pivoting up and down and capable of supporting a cut part, an operation part and a mission case arranged in a left-right direction on the front part of the base, It is an object of the present invention to facilitate the maintenance work of the hydraulic unit by properly arranging an oil pressure unit having a control valve for operating the oil pressure supply mechanism to operate the oil pressure supply mechanism.

[4]

Problems corresponding to the background art [4] are as follows.

In the conventional structure described in JP-A-2007-159467, two shift operating members are arranged in parallel in the operation control space.

There is a room for improvement in terms of effective utilization of the space because arrangement of equipment necessary for steering is required in addition to the shift operation sphere in the operation control space.

It is an object of the present invention to provide a shift operation structure of a work vehicle capable of appropriately arranging devices in an operation control space by studying an operation form of a peripheral speed operation member and a speed change operation member, It is in point of providing.

[One]

Means for solving the problem [1] are as follows. In other words,

A traveling transmission structure of a work vehicle configured to transmit power of an engine to right and left traveling devices through a continuously variable transmission for traveling and a transmission case,

Wherein the transmission case is provided with a recess on one side of the transmission case and an input shaft is provided on the other side of the transmission case adjacent to the recess,

A continuously variable transmission for driving is disposed in the recess, an output shaft of the continuously variable transmission for running is provided on one side of the transmission case,

The output shaft of the continuously variable transmission for running is linked to the input shaft of the transmission case,

A transmission gear for transmitting the power of the input shaft is provided on the other side of the transmission case,

A transmission shaft is extended from one side of the transmission case to the other side so that the power of the transmission gear is transmitted to the transmission shaft,

A side clutch disposed on the right side of the transmission shaft and a side clutch disposed on the left side of the transmission shaft,

The power of the output shaft of the traveling continuously variable transmission is transmitted from the input shaft of the transmission case to the right and left traveling devices via the transmission gear, the transmission shaft, and the right and left side clutches The driving car structure of the work car.

This feature is advantageous in the following respects.

For example, as shown in Figs. 3 and 7, a concave portion 10a is formed on one side (left side of the paper) of the mission case 10 and into the other side (right side of the paper) And the continuously variable transmission device 11 for traveling is disposed in the portion 10a. Thus, the continuously-variable transmission 11 for traveling is moved from the transverse side portion of the transmission case 10 to the other side (right side) of the transmission case 10, The state of being largely projected to the lateral side does not occur.

According to this aspect, when the concave portion 10a of the mission case 10 is formed as shown in Fig. 7, for example, in the mission case 10, the input shaft 22 is placed in the concave portion 10a And the transmission gears 30 and 31 are also provided on the other side (the same side as the input shaft 22 of the mission case 10) on the other side (right side in the drawing) of the adjacent transmission case 10. On the right side of the paper. By providing the input shaft 22 and the transmission gears 30 and 31 on the other side (the input shaft 22 side) (on the right side in the drawing) of the transmission case 10, one side of the transmission case 10 The influence of the input shaft 22 and the transmission gears 30 and 31 is reduced and the concave portion 10a of the mission case 10 is easily formed.

7, in the right and left side clutches 34 located below the transmission gears 30 and 31, one side (left side of the paper sheet) of the transmission case and the other side And the power of the transmission gears 30 and 31 is transmitted to the input shaft 22 side of the transmission shaft 29 (the other side of the transmission case and the right side of the transmission case) And the right and left side clutches 34 are provided on the side of the concave portion 10a of the transmission shaft 29 (on one side of the transmission case and on the left side of the paper surface). The power of the transmission gears 30 and 31 is transmitted to the input shaft 22 side (the right side in the drawing) of the transmission shaft 29 as shown in Fig. 7, The right side and left side clutches 34 can be easily provided on the concave portion 10a side (left side in the drawing) of the power transmission shaft 29 because there is a spatial margin on the side of the left side

In the combine which is an example of the work vehicle, there are many cases where the operation section 5 is provided outside the transverse section of the continuously variable transmission device 11 for travel and the mission case 10 as shown in Fig. 2 . In this case, if the continuously-variable transmission for driving is projected largely to the transverse side from the transverse side portion of the transmission case, the traveling continuously-variable transmission enters the operation portion, and the space of the operation portion is sacrificed.

On the other hand, according to the present invention, even if the continuously-variable transmission for driving is not projected from the transverse side portion of the transmission case to the transverse side significantly, even if the operation portion is provided on the transverse outside side of the continuously- Little space is sacrificed.

Therefore, in the traveling transmission structure of the work vehicle, the recessed portion into the other side is formed on one side of the transmission case, and the continuously variable transmission for traveling is disposed in the recessed portion of the transmission case. It is possible to prevent the state of the continuously variable transmission device of the transmission case from being largely projected to the side of the transverse direction, thereby making it possible to make the vicinity of the continuously variable transmission for traveling in the transmission case compact.

In this case, even when the operating portion is configured to be provided on the outside of the transverse section of the continuously variable transmission for driving and the transmission case, for example, since the space of the operating portion is less likely to be sacrificed, So that it is possible to arrange various devices in the operation section with a sufficient margin, so that the comfort in the operation section can be improved.

Further, in the case of forming the concave portion into the other side of the right or left side on one side of the transmission case, the concave portion of the transmission case is easily formed by providing the input shaft and the transmission gear on the other side And the side clutches on the right and left sides can be provided without difficulty, productivity of the mission case can be improved.

In one preferred embodiment, the input shaft of the traveling continuously variable transmission is provided on one side of the transmission case, and the input shaft is extended to the other side of the transmission case. This feature is advantageous in the following respects.

When the input shaft of the continuously variable transmission device for traveling 11 is projected to the opposite side (left side in the drawing) of the recess 10a in the state shown in Figs. 7 and 8, The input shaft of the continuously variable transmission device 11 for traveling is projected largely to the lateral side (left side in the drawing) from the side.

7 and 8, the input shafts 11b and 16 of the continuously variable transmission device for traveling 11 are provided on the side of the concave portion 10a (left side in the drawing) And the input shafts 11b and 16 of the continuously variable transmission device for traveling 11 are projected from the transverse side portion of the transmission case 10 to the transverse side (right side in the drawing) .

Therefore, since the input shaft of the continuously variable transmission for driving is not greatly projected from the transverse side of the transmission case to the transverse side, it is possible to achieve compactness in the vicinity of the continuously variable transmission for traveling in the transmission case.

[2]

Means for solving the problem [2] are as follows. In other words,

A traveling transmission structure of a work vehicle configured to transmit power of an engine to right and left traveling devices through a continuously variable transmission for traveling and a transmission case,

Wherein the transmission case is provided with a recess on one side of the transmission case and an input shaft is provided on the other side of the transmission case adjacent to the recess,

A continuously variable transmission for driving is disposed in the recess, an output shaft of the continuously variable transmission for running is provided on one side of the transmission case,

The output shaft of the continuously variable transmission for running is linked to the input shaft of the transmission case,

A transmission shaft extending from one side of the transmission case to the other side and extending adjacent to the recess,

A multi-disc type friction relieved sheave clutch capable of transmitting power of different speeds in the same direction to the right and left traveling devices is provided on one side of the transmission case on the transmission shaft,

Type friction-reversing clutch capable of transmitting power in opposite directions to the right and left traveling devices is provided on the other side of the transmission case on the transmission shaft,

And the power of the output shaft of the traveling continuously variable transmission is transmitted from the input shaft of the transmission case to the complete line clutch and the reverse clutch.

This feature is advantageous in the following respects.

For example, as shown in Figs. 3 and 7, a concave portion 10a is formed on one side (left side of the paper) of the mission case 10 and into the other side (right side of the paper) And the continuously variable transmission device 11 for traveling is disposed in the portion 10a. Thus, the continuously-variable transmission 11 for traveling is moved from the transverse side portion of the transmission case 10 to the other side (right side) of the transmission case 10, The state of being largely projected to the lateral side does not occur.

Generally, the reverse clutch transmits power in the opposite direction to one of the right or left traveling devices to the other of the traveling devices on the right or left side, and transmits a relatively large torque (reverse power) In the case of multi-plate construction, a relatively large diameter and a large number of friction plates are required, and the reverse clutch is relatively large.

On the other hand, the quick-turn clutch transmits low-speed power to the other side of the right or left traveling device in the same direction as the right or left traveling device, and transmits relatively low torque (low-speed driving force in the same direction) Therefore, when the fastener chain clutch is formed of a friction multi-plate type, it is possible to form a friction plate having a relatively small diameter and a small number of teeth, so that the fastener chain clutch becomes relatively small.

7, the transmission shaft 44 is supported adjacent to the concave portion 10a of the transmission case 10, and the recovery clutch 46 and the reverse clutch 53 provided on the transmission shaft 44 are provided on the side of the concave portion 10a of the transmission shaft 44 on the side of the transmission case 44 on the left side of the transmission case and the reverse clutch 53 on the input shaft 22 side of the transmission shaft 44 (the other side of the transmission case and the right side of the paper).

7 and 9, for example, when the concave portion 10a of the mission case 10 is formed, the clearance portion clutch 10b of the mission case 10, which is adjacent to the concave portion 10a of the mission case 10 46 can be made relatively small so that the work to be influenced by the relief clutch clutch 46 is reduced and the concave portion 10a of the mission case 10 is easily formed.

For example, as shown in Figs. 7 and 9, when the reverse clutch 53 is provided, since the reverse clutch 53 is provided at a position deviated from the concave portion 10a of the transmission case 10, The reverse clutch 53 of the reverse clutch 53 can be reliably provided even if the reverse clutch 53 of the reverse clutch 53 is less affected by the recess 10a of the transmission case 10.

In the combine which is an example of the work vehicle, there are many cases where the operation section 5 is provided outside the transverse section of the continuously variable transmission device 11 for travel and the mission case 10 as shown in Fig. 2 . In this case, if the continuously-variable transmission for driving is projected largely to the transverse side from the transverse side portion of the transmission case, the traveling continuously-variable transmission enters the operation portion, and the space of the operation portion may be sacrificed.

On the other hand, according to the above feature, even if the continuously variable transmission for driving is not projected from the transverse side portion of the transmission case largely to the transverse side, even if the operation portion is provided on the transverse side of the transitional transmission for driving and the transmission case, The space of the operation part is less likely to be sacrificed.

Therefore, in the traveling power transmission structure of the work vehicle, the right or left side of the transmission case is provided with a concave portion that enters the other side of the right side or the left side, and the traveling type continuously variable transmission device is disposed in the concave portion of the transmission case , It is possible to prevent the state of the continuously variable transmission for driving from being greatly projected from the transverse side portion of the transmission case to the transverse side, thereby making it possible to make the vicinity of the continuously variable transmission for traveling in the transmission case compact.

In this case, even when the operating portion is configured to be provided on the outside of the transverse section of the continuously variable transmission for driving and the transmission case, for example, since the space of the operating portion is less likely to be sacrificed, So that it is possible to arrange various devices in the operation section with a sufficient margin, so that the comfort in the operation section can be improved.

Further, in the case of forming the concave portion that enters the right side or the left side of the right side or the left side of the transmission case to the other side of the transmission case, the complete line clutch is provided on the concave portion side of the transmission shaft and the reverse clutch is provided on the input shaft side This makes it easier to form the recess of the mission case and improves the productivity of the mission case because the reverse clutch can be provided without difficulty.

In one preferred embodiment, the second electric motor shaft is extended from one side of the transmission case to the other side, and the second output shaft is connected to the second transmission shaft by a right output gear for transmitting power to the right traveling device, And a left output gear for transmitting power to the traveling device of the vehicle,

The power from the input shaft is transmitted to the second transmission shaft via the transmission gear and is transmitted from the second transmission shaft to the loose-wheel rotation clutch through the transmission gear, and from the loose rotation clutch to the right or left output gear And the power of the input shaft is transmitted to the reverse clutch through the transmission gear and is transmitted from the reverse clutch to the right or left output gear.

This feature is advantageous in the following respects.

When the recessed portion 10a of the transmission case 10 is formed as shown in Figs. 7 and 9 and the relief clutch 46 is provided adjacent to the recessed portion 10a, for example, The power of the input shaft 22 is transmitted to the relieving clutch 46 via the power transmission shaft 29 different from the power transmission shaft 44 having the relief clutch 46. [

7 and 9, the input shaft 22 and the relief clutch 46 are engaged with each other in the form of one side (left side of the drawing) and the other side (right side of the drawing) of the mission case 10, The power of the input shaft 22 can be reliably transmitted to the relief clutch 46 through the other transmission shaft 29. [ The influence of the other transmission shaft 29 on the concave portion 10a of the transmission case 10 is reduced by providing the other transmission shaft 29 slightly spaced from the concave portion 10a of the transmission case 10, So that the power can be reliably transmitted to the relief clutch 46 through the other transmission shaft 29.

7 and 9, when the power of the input shaft 22 is transmitted to the reverse clutch 53, the input shaft 22 and the reverse clutch 53 are engaged with the other side of the transmission case 10 The influence of the concave portion 10a of the transmission case 10 is reduced and the power of the input shaft 22 can be reliably transmitted to the reverse clutch 53 .

Therefore, the power of the input shaft can be reliably transmitted to the relief clutch via the other electric shafts, and the power of the input shaft can be reliably transmitted by the reverse clutch, The productivity of the mission case was improved.

In one preferred embodiment, the right and left output gears are provided on the second transmission shaft and are disposed on one side of the transmission case,

A transmission gear for transmitting the power of the input shaft to the second transmission shaft and a transmission gear for transmitting the power of the input shaft to the reverse clutch are provided on the other side of the transmission case.

This configuration is advantageous in the following respects.

7 and 9, when the power of the input shaft 10 is transmitted to the other transmission shaft 29 and the reverse clutch 53, according to this characteristic, the power of the input shaft 10 is transmitted to the other transmission shaft 29 and the reverse clutch 53, The power transmission gears 30 and 31 for transmitting the power to the coaxial shaft 29 and the transmission gear 51 for transmitting the power of the input shaft 10 to the reverse clutch 53 are connected to the other side of the transmission case 10 )side. On the right side of the paper.

Thus, the input shaft 22 and the transmission gears 30, 31 and 51 are connected to the other side of the transmission case 10 (toward the input shaft 22 side). The influence of the input shaft 22 and the transmission gears 30, 31, 51 is reduced on one side (left side of the drawing) of the mission case 10, The concave portion 10a is easily formed.

For example, when the right and left output gears 32R and 32L for transmitting power to the right and left traveling devices are provided on the other transmission shaft 29 as shown in Figs. 7 and 9, The power of the transmission gears 30 and 31 is transmitted to the input shaft 22 side (the other side of the transmission case and the right side of the transmission case) of the transmission shaft 29 and the concave portion 10a Right side and left side output gears 32R and 32L on the right side (left side on the above-mentioned one side of the transmission case).

For example, as shown in Figs. 7 and 9, when the power of the transmission gears 30 and 31 is transmitted to the side of the input shaft 22 of the transmission shaft 29, the concave portion 10a The left and right output gears 32R and 32L can be easily provided on the concave portion 10a side (left side in the drawing) of the power transmission shaft 29. [

Therefore, by providing the input shaft and the transmission gear on the other side (input shaft side) of the transmission case, the recessed portion of the transmission case is easily formed, and the right and left output gears can be provided without difficulty on the side of the concave portion of the transmission shaft The productivity of the mission case was improved by the point that there was.

[3]

Means for solving the problem [3] are as follows. In other words,

A transmission case having a transmission case containing a hydraulic mechanism for traveling or turning is provided on the front portion of the base body,

The operation section is provided on the lateral side of the one side of the mission case,

And a support frame supporting the cut-out portion is provided on the lateral side of the other side of the mission case,

And a control valve for operating and operating the hydraulic oil to the hydraulic mechanism is provided at a lateral side of the support frame side of the transmission case.

This feature is advantageous in the following respects.

Generally, in the combine which is capable of swinging up and down and which supports the cut-out portion, the operation portion and the mission case are arranged in the left-right direction on the front portion of the base, the cut- The worker can come in from the opposite side of the operation part to the front part of the base body by the widening between the preload part and the front part of the base on the opposite side of the operation part (for example, JP- A-2000-335439 discloses that since the operation part is provided on the right side of the front part of the base body and the cut part is provided on the left side of the front part of the base body, Worker can come in between booths).

For example, when the hydraulic unit is provided on the right side or the left side of the operation side of the mission case, when an operator enters the space between the pre-installation part and the front part of the vehicle from the side opposite to the operation part, (Operation side), the maintenance work of the hydraulic unit becomes difficult to be performed.

Likewise, if the hydraulic unit is provided on the front side of the transmission case, the cut-off portion is located on the front side of the hydraulic unit, so that the maintenance work of the hydraulic unit becomes difficult. When the oil pressure unit is provided on the rear side of the transmission case, the front portion of the gas is located on the rear side of the oil pressure unit, so that the maintenance work of the oil pressure unit becomes difficult.

On the other hand, according to the above feature, the hydraulic unit is provided on the lateral side of the support case side of the transmission case. When the worker comes in between the preloading portion and the front portion of the base body from the opposite side to the operation portion, the hydraulic unit is positioned on this side (worker side) of the mission case for the operator, so that the maintenance work of the hydraulic unit becomes easy .

Therefore, in the combine that is capable of swinging up and down and is arranged so as to be laterally arranged on the front portion of the base body, the support frame supporting the cut-off portion, the operation portion and the mission case, The maintenance work of the hydraulic unit including the control valve for supplying the hydraulic oil to the hydraulic mechanism in the steerable manner is facilitated and the maintenance and workability of the combine can be improved.

In one preferred embodiment, the transmission shaft supporting the hydraulic mechanism is supported in the left-right direction inside the transmission case, the end portion of the transmission shaft is inserted into the oil pressure unit,

And a hydraulic fluid passage extending from the hydraulic mechanism to an end portion of the transmission shaft is provided in the transmission shaft so that the hydraulic oil is supplied from the hydraulic pressure unit to the hydraulic mechanism.

This feature is advantageous in the following respects.

In the interior of the mission case, the hydraulic mechanism is supported by a transmission shaft (20 and 28 in Figs. 2 and 4 of JP-A-2000-335439).

According to the above aspect of the present invention, when the operation of supplying hydraulic oil from the hydraulic unit (control valve) to the hydraulic mechanism is performed, the hydraulic unit is provided on the lateral side of the right or left support frame side of the transmission case, Is inserted into the oil pressure unit and the hydraulic oil is supplied to the hydraulic mechanism from the oil pressure unit (control valve) through the oil passage of the transmission shaft. Thereby, it is unnecessary to dispose piping or the like of the hydraulic oil over the hydraulic unit (control valve) and the hydraulic mechanism, and the hydraulic unit (control valve) and the hydraulic mechanism are connected by a short path (hydraulic passage).

Therefore, in the case where the hydraulic pressure unit and the hydraulic mechanism are connected to each other by the short path (flow path of the transmission shaft), when the operation of supplying hydraulic oil from the hydraulic unit (control valve) to the hydraulic mechanism is performed, .

[4]

Means for solving the problem [4] are as follows. In other words,

A continuously variable transmission device comprising: a continuously variable transmission device comprising a hydraulic pump capable of changing the capacity steplessly and a hydraulic motor driven by receiving hydraulic oil from the hydraulic pump; and a gear type negative speed change device A traveling transmission structure of a working machine in which an apparatus is installed,

And a sub speed change manipulation member for adjusting the hydraulic type pump is disposed in the operation control space and the gear type auxiliary speed change mechanism is switched and controlled is disposed outside the operation control space.

This feature is advantageous in the following respects.

Since the peripheral devices can be steplessly shifted, they are used for precise speed control during work traveling and on road running. Because of this, it is necessary to dispose the operation member in the vicinity of the driver as far as possible, and therefore, it is disposed in the operation control space.

On the other hand, the auxiliary transmission is not used for precise speed control, as in the case of a peripheral device, so there is little need to arrange it in the vicinity of the driver. Thus, the auxiliary shift operating member is disposed outside the driving control space.

Therefore, since the installation positions are selected by paying attention to the functions of the peripheral speed control unit and the auxiliary speed change control unit, the arrangement of the devices in the operation control space is not complicated, Can be provided.

In one preferred embodiment, the capacity of the hydraulic motor is configured to be variable.

This feature is advantageous in the following respects.

According to this configuration, since the capacity can be changed even in a hydraulic motor, a step-variable shifting mode different from that of a capacity variable type in a hydraulic pump capable of continuously changing the capacity can be employed in the hydraulic motor, It is also possible to employ a shape.

Therefore, it is possible to diversify the type of shift in the peripheral device.

Other features and advantages of the present invention will become apparent from the following description with reference to the accompanying drawings.

According to the present invention, in the traveling transmission structure of the work vehicle, the vicinity of the continuously variable transmission for traveling in the transmission case can be made compact.

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a view showing one preferred embodiment of the present invention, and is an overall side view of a combine as an example of a work vehicle. Fig.
2 is a plan view of the front portion of the combine in the vicinity of the mission case;
3 is a front view of the vicinity of the mission case in the front part of the combine.
4 is a side view of the vicinity of the mission case in the front part of the combine.
5 is a side view of the mission case;
6 is a side view of the vicinity of the lower portion of the mission case;
7 is a longitudinal front view of the transmission case of the right and left transmission cases.
8 is a longitudinal front view of the vicinity of the input shaft of the hydrostatic stepless speed change device and the transmission case;
Fig. 9 is a front end elevation view of the vicinity of the closed-loop clutch, brake, reverse clutch and right and left side clutches of the mission case; Fig.
10 is a rear view of the right and left side engagement portions of the right and left side clutches;
11 is a perspective view of the orbiting clutch case and the receiving member in the right and left rotating clutches;
12 is a diagram showing a hydraulic circuit structure in the hydraulic unit;
13 is a diagram showing a relationship between a peripheral speed lever, a steering lever, a turning mode switch, a hydrostatic stepless speed change device, and an oil pressure unit.
14 is a front view showing a driving control portion and a mission case portion of the combine.
15 is a plan view showing a driving control portion of the combine.
16 is a perspective view showing a grip portion of the peripheral speed lever;
17 is a side view showing a mission case;
18 is a hydraulic circuit diagram of a hydrostatic stepless speed changer.
19 is a cross-sectional plan view showing a parking brake mechanism.
20 is a side view showing the cam disc and the operation arm of the parking brake mechanism;
Fig. 21 (a) is a longitudinal rear view showing a state in which the parking brake mechanism is in the OFF position, and Fig. 21 (b) is a longitudinal rear view showing a state in which the parking brake mechanism is in the ON position.
Fig. 22 (a) is an operation diagram showing the cam disk, the ball, the guide pin and the urging spring in the OFF position of the parking brake mechanism, Fig. 22 (b) And a ball, a guide pin, and a pressing spring.
23 is a side view of the crawler traveling device.
24 is a plan view of the crawler traveling device.
25 is a longitudinal side view of the crawler guided wheel support structure.
26 is a plan view of the crawler guided wheel support structure.
27 is a side view of the crawler traveling device when the working machine is moved forward from a high place to a low place.
28 is a side view of the rocking motion restricting mechanism;
29 is a plan view of a rocking motion restricting mechanism;
30 is a side view showing the swing limit of the front swinging track frame;

Hereinafter, with reference to the accompanying drawings, one preferred embodiment of the work vehicle according to the present invention will be described on the basis of a combine-harvester which is an example of a work vehicle.

Unless otherwise specified, in the following description, the direction in which the traveling vehicle of the combine advances (advances) forward is referred to as the forward and backward directions, and the horizontal direction orthogonal to the forward and backward directions is referred to as the lateral direction (or the lateral direction) And the direction perpendicular to the longitudinal direction and the lateral direction is referred to as the vertical direction.

[One]

As shown in Figs. 1 and 2, a support frame 2 is supported on a front portion of a base supported by right and left crawler traveling devices 1 so as to be able to move up and down in the direction of the transverse axis P, 2 and the elevating cylinder 3 is supported on the supporting frame 2. The elevating cylinder 4 is supported on the supporting frame 2. [ The operation section 5 is provided on the right side of the front portion of the base and the engine 7 is provided below the operation seat 6 of the operation section 5. [ The preloading section (4) takes the interstices between the grooves and simultaneously transports the cutout sections backward in the lateral direction of the operation section (5). A threshing device 8 is provided on the left side of the rear part of the base and a grain tank 9 is provided on the right side of the rear part of the base to form a combine of a culm head discharging type.

Next, the mission case 10 will be described.

As shown in Figs. 1 and 2, the mission case 10 is provided near the right and left center of the front part of the base, and the operation part 5 is provided outside the right side of the mission case 10 in the lateral direction. The support frame 2 extends from the position of the transverse axis P to the front side and the support frame 2 is disposed on the rear side of the transmission case 2 on the left side of the transmission case 10, 10 on the left side in the lateral direction.

As shown in Figs. 3 and 7, the mission case 10 is made of an aluminum die-cast material and has a two-part structure of a right portion 10R and a left portion 10L. The right portion 10R of the mission case 10 (See Fig. 3 and Fig. 7) of the mission case 10 (the right and left portions 10R and 10L) of the mission case 10 (see Fig. 3 and Fig. 7) The concave portion 10a comes in the vicinity of the front surface 10b (a little left side of the paper surface).

(An example of a continuously variable transmission for HST. And an example of a peripheral speeding device) 11 as shown in Figs. 3 and 7 is mounted on the transmission case 10 (right portion 10R) And the port block 11a of the hydrostatic stepless speed change unit 11 is connected to the concave portion 10a of the mission case 10 (right portion 10R) . A cylindrical support member 12 is connected to the port block 11a of the hydrostatic stepless type speed changer 11 so that the support member 12 extends to the left and the arm 12a of the support member 12 And is connected to the mission case 10 (left portion 10L).

As shown in Figs. 3 and 7, the right support portion 10c and the left support portion 10c are provided outside the lower portion of the mission case 10 (the right and left portions 10R and 10L). The transmission case 14 on the right side and the transmission case 14 on the left side are provided and the transmission cases 14 on the right and left sides are provided on the right side and the left side of the transmission case 10 (right and left portions 10R, 10L) And is connected to the left supporting portion 10c and extends forward (refer to Figs. 4 and 5). Right and left axle cases 15 are connected to the right and left transmission cases 14 to extend to the right and left and sprockets 1a for driving the right and left crawler traveling devices 1 are disposed on the right and left sides, And is provided at the right and left ends of the left axle case 15.

As shown in Figs. 3, 6 and 7, the right side and the left side of the mission case 10 (right and left portions 10R and 10L) are located outside the lower portion of the mission case 10 (right side portion 10R) And the connecting portion 10d is provided at a portion different from the left supporting portion 10c so that the connecting portion 10d of the transmission case 10 (right portion 10R) and the connecting portion 10d of the transmission case 10d, And the linking member 13 is connected.

[2]

Next, the structure of the transmission system (linear system) in the mission case 10 (right and left portions 10R, 10L) will be described.

The input shaft 16 is supported by the support member 12 and the input pulley 17 is connected to the end of the input shaft 16 as shown in Figs. 2, 3 and 8, The input shaft 11b of the hydrostatic stepless speed change unit 21 is connected to the input shaft 16 through a connecting member 18. [ The power of the engine 7 is transmitted to the input pulley 17 via the transmission belt 19 and the power of the engine 7 is transmitted through the transmission belt 20 and the hydrostatic stepless transmission 21 to the pre- ).

As shown in Figs. 7 and 8, in the upper part of the mission case 10 (the right and left portions 10R and 10L), the recess 10a of the mission case 10 (right portion 10R) The input shaft 22 is supported by the transmission case 10 (the left portion 10L) so that the transmission gears 23 and 24 are adjacent to each other (opposite to each other), and the transmission gears 23 and 24 are fixed to the input shaft 22 by a spline structure. The output shaft 11c of the hydrostatic stepless type stepless transmission 11 is inserted into the transmission case 10 (the right and left portions 10R and 10L) and the transmission gear 24 (the input shaft 22) .

7 and 8, a high-speed gear 25 and a low-speed gear 26 are provided on a transmission shaft 27 supported on the upper portion of the mission case 10 (the right and left portions 10R and 10L) The transmission gear 23 and the high gear 25 are meshed with the transmission gear 24 and the low speed gear 26 and the shift member 28 is meshed with the transmission shaft 27 (Not shown). Thus, the gear type negative speed change mechanism A as the auxiliary speed change mechanism is constituted by the transmission gear 23 and the high speed gear 25, the transmission gear 24, the low speed gear 26 and the shift member 28 The power of the input shaft 22 is shifted to the high and low second positions (high speed and low speed positions) and transmitted to the transmission shaft 27 by engaging the shift member 28 with the high speed and low speed gears 25 and 26. Normally, the shift member 28 is slid to a position where it meshes with the high-speed gear 25, so that the high-speed position is set.

The transmission shafts 29 are supported on the lower portions of the transmission case 10 (the right and left portions 10R and 10L) as shown in Figs. 7 and 9, and the transmission shafts 29 10) in the vicinity of the inner surface of the wall portion of the left portion 10L. The transmission gear 30 is fixed to the left side portion of the transmission shaft 27 (in the vicinity of the inner surface of the wall portion of the left portion 10L of the transmission case 10) and the transmission gears 30 and 31 are engaged. Thereby, the input shaft 22 and the front portion (front portion) of the right side (the left side portion 10L of the mission case 10) of the right side and the left side portions 10R and 10L of the transmission case 10 Most of the coaxial shaft 27 and the transmission gears 30 and 31 are disposed.

The output gears 32R and 32L on the right and left sides of the transmission shaft 29 (right portion 10R of the transmission case 10) of the transmission shaft 27 And right and left fitting portions 33R and 33L are integrally formed on the right and left sides of the right and left output gears 32R and 32L by a spline structure (The right engagement portion 33R is disposed in the vicinity of the inner surface of the wall portion of the right portion 10R of the mission case 10). The right side clutch 34 is formed between the right side output gear 32R and the right side engagement portion 33R and between the left side output gear 32L and the left side engagement portion 33L, (34).

The right and left support portions 10c of the transmission case 10 (right and left portions 10R and 10L) and the right and left transmission case 14, as shown in Fig. 7, And a transmission gear 36 fixed to the transmission shaft 35 inside the transmission case 10 (the right and left portions 10R and 10L) meshes with the right and left output gears 32R and 32L And a transmission gear 37 is fixed to the transmission shaft 35 in the right and left transmission case 14. Right and left axles 38 are supported on the right and left transmission case 14 and the right and left axle cases 15. In the right and left transmission cases 14, And a transmission gear 39 fixed to the axle 38 on the left side is meshed with the transmission gear 37. The right and left axles 38 extend right and left in the right and left axle cases 15 so that the sprocket 1a of the right and left crawler traveling devices 1 4) are connected to the right and left ends of the right and left axles 38, respectively.

7, the power of the input shaft 22 is transmitted through the transmission shaft 27, the transmission gears 30, 31, the transmission shaft 29, the right and left side clutches 34 The right and left output gears 32R and 32L, the transmission gear 36, the transmission shaft 35, the transmission gears 37 and 39, the right and left output gears 32R and 32L, And is transmitted to the right and left crawler traveling apparatuses 1 through the air flow passage 38, so that the gas flows straight.

[3]

Next, the right and left side clutches 34 (corresponding to the hydraulic mechanism for pivoting) will be described.

A spline portion 29a is formed on the outer surfaces of the right and left portions of the transmission shaft 29 so that the right and left fitting portions 33R and 33L are engaged with the spline portions 29a And the receiving member 40 is inserted into the spline portion 29a of the transmission shaft 29 so as to be rotatable integrally with the spline portion 29a.

As shown in Figs. 9 and 10, a plurality of recessed portions are disposed on the right side and left side mating portions 33R and 33L on the side of the receiving member 40, and right and left mating portions 33R and 33L The right and left fitting portions 33R and 33L are formed by the receiving member 40 and the spring 41 in the right and left sides To the engagement side of the output gears 32R, 32L. The right and left side clutches 34 are brought into the power transmission state by engaging the right and left side engagement gears 33R and 33L with the right and left output gears 32R and 32L, Are transmitted to the right and left crawler traveling apparatuses 1 through the right and left side clutches 34, respectively.

The piston 42 is slidably disposed between the right and left output gears 32R and 32L and the transmission shaft 29 and the piston 42 is engaged with the right and left engagement portions 33R 33L so that the pistons 42 and the right and left mating portions 33R, 33L are integrally rotated so that the right and left mating portions 33R, (43) is inserted.

9, when hydraulic oil is supplied between the right and left output gears 32R, 32L and the piston 42, the right and left mating portions 33R, 33L and the piston 42 are urged by the spring 41 The left and right side gears 32R and 32L are slid to the separation side, and the left and right side clutches 34 are shut off. The right and left mating portions 33R and 33L and the piston 42 are moved in the right and left directions by the spring 41. When the operating oil is discharged between the right and left output gears 32R and 32L and the piston 42, The left and right side clutches 34 are turned to the engaged state.

In this case, as shown in Fig. 9, the right and left fitting portions 33R and 33L and the piston 42 are formed separately from each other, so that the right and left fitting portions 33R and 33L The inclination of the piston 42 allows the slide operation to be performed without being affected by the inclination of the right and left engagement portions 33R and 33L.

The right and left engagement portions 33R and 33L and the piston 42 and the transmission shaft 29 are integrally rotated by the spring pin 43 so as not to rotate relative to each other And rotational aberration is generated between the inner peripheral portion of the right and left output gears 32R and 32L and the outer peripheral portion of the piston 42. [ A plurality of circumferential grooves 42a are formed in the outer peripheral portion of the piston 42 in contact with the inner surfaces of the output gears 32R and 32L on the right and left sides, Thereby preventing the outer peripheral portion of the piston 42 from being burnt between the inner peripheral portion of the right and left output gears 32R and 32L.

As shown in Fig. 9, the central portion between the right and left spline portions 29a of the power transmission shaft 29 is formed to have the same diameter without a step, The left and right output gears 32R and 32L and the piston 42 and the right and left mating parts 33R and 33L and the receiving member 40 are located on the right and left sides of the transmission shaft 29 It can also be installed from one side and assembled.

[4]

Next, a description will be given of the structure of a transmission system (tilting system) in the mission case 10 (right and left portions 10R and 10L).

The transmission shaft 44 is supported by the transmission case 10 (the right and left portions 10R and 10L) as shown in Figs. 7 and 9 and the right side portion of the transmission case 44 And the transmission gear 44 is meshed with the gear portion of the outer peripheral portion of the right-side mating portion 33R, and the transmission gear 44 is meshed with the gear portion of the right- A grand turn clutch 46 (equivalent to a hydraulic mechanism for pivoting) is provided between the transmission gear 45 and the transmission gear 45. The broken line clutch 46 is formed of a friction multi-plate type, and is operated by being supplied with the operating oil to be operated in the electric state, and being operated to the cut-off state by discharging the operating oil.

7 and 9, the turning clutch case 47 is externally inserted into the transmission shaft 29 such that the turning clutch case 47 is rotatable relative to the transmission shaft 44 and the transmission gear 48 and the orbiting clutch case 47 Is meshed with the power transmission gear 47a of the outer peripheral portion of the power transmission mechanism. The revolving clutch case 47 is configured to be symmetrical in the left and right directions and is provided between the revolving clutch case 47 and the right and left output gears 32R and 32L so that the right and left revolving clutches 49 ). The right and left revolving clutches 49 are of a friction multi-disc type, and are supplied with operating oil to be operated in the electric state. In this case, the right and left rotating clutches 49 are arranged so that the friction plates are pressed against each other, so that the right and left rotating clutches 49 are brought into a semi-conductive state even when the working oil is discharged.

9 and 11, when the ring-shaped receiving member 54 for receiving the friction plates of the right and left rotating clutches 49 is provided in the orbiting clutch member 47, And one of the opening portions 47b of the orbiting clutch case 47 into which the convex portion of the friction plate of the right and left rotating clutches 49 is inserted is provided with a convex portion 54a And the support member 54 is prevented from rotating.

7 and 9, the power of the power transmission shaft 29 is transmitted to the right-hand side engagement portion 32R, the transmission gear 45, Is transmitted to the orbiting clutch case 47 through the clutch 46, the transmission shaft 44 and the transmission gear 48 as a power lower in speed than the transmission shaft 29 in the rotation in the same direction as the transmission shaft 29 . When the right or left side clutch 34 is operated to the cutoff state and the right or left turn clutch 49 is operated to the power transmission state, Is transmitted to the right or left output gears 32R, 32L.

A brake 50 (equivalent to a hydraulic mechanism for pivoting) is provided on the left side of the transmission shaft 44 (in the vicinity of the outer surface of the wall portion of the left portion 10L of the mission case 10) as shown in Figs. 7 and 9 Respectively. The brake 50 is formed of a friction multi-plate type, and is operated to a braking state by supplying operating oil, and is discharged to a released state by discharging operating oil.

7 and 9, when the brake 50 is operated in the braking state, the orbiting clutch case 47 is brought into a braking state via the transmission shaft 44 and the transmission gear 48. [ When the right or left side clutch 34 is operated to the disconnected state and the right or left revolving clutch 49 is operated to the electric state, the right or left output gears 32R, 32L are in the braking state.

The transmission gear 51 is fixed to the left side portion of the transmission shaft 27 (in the vicinity of the inner surface of the wall portion of the left side portion 10L of the mission case 10) as shown in Figs. 7 and 9, The transmission gears 52 and 52 are engaged with each other so that the transmission gear 52 is relatively rotatably inserted into the left portion of the transmission case 10 (in the vicinity of the inner surface of the wall portion of the left portion 10L of the transmission case 10) A reverse clutch 53 (equivalent to a hydraulic mechanism for pivoting) is provided between the transmission 44 and the transmission gear 52. The reverse clutch 53 is of a frictional multi-plate type, and is operated by being supplied with operating oil, and is operated into a shut-off state by discharging operating oil.

7 and 9, when the reverse clutch 53 is operated to the power transmission state, the power of the transmission shaft 27 is transmitted to the transmission gears 51 and 52, the reverse clutch 53, the transmission shaft 44 And is transmitted to the orbiting clutch case 47 as a power for rotating in the direction opposite to the transmission shaft 29 through the transmission gear 48 and the transmission gear 48. [ When the right or left side clutch 34 is operated to the cutoff state and the right or left turn clutch 49 is operated to the power transmission state, the power of the reverse rotation to the power transmission shaft 29 is transmitted to the right / (32R, 32L).

7 and 9, the reverse clutch 53 transmits the power in the opposite direction to the one of the right or left crawler traveling apparatus 1 to the other side of the right or left crawler traveling apparatus 1 , And transmits relatively large torque (reverse power). The crawler wheel clutch 46 transmits the low speed power to the other side of the right or left crawler traveling device 1 in the same direction as the one of the right or left crawler traveling device 1, Speed directional power).

As a result, the reverse clutch 53 requires a relatively large diameter and a large number of friction plates, so that the reverse clutch is relatively large, and the outer diameter is particularly large. Since the loose-wire clutch 46 can be a relatively small-diameter and a small number of friction plates, the loose-wire clutch 46 is relatively small in size, and in particular, has a small outer diameter.

[5]

Next, the operation of the hydrostatic stepless speed change unit 11 will be described.

The pump (corresponding to the hydraulic pump) 11P of the hydrostatic stepless type continuously variable transmission 11 shifts from the neutral position N to the neutral position N to the high speed side and the reverse side R), and the motor (corresponding to a hydraulic motor) 11M of the hydrostatic stepless type stepless transmission 11 is configured so as to be capable of being shifted to the high and low second stages. A hydraulic cylinder 59 for operating the swash plate of the pump 11P of the hydrostatic stepless type speed changer 11 and a control valve 60 for operating the hydraulic cylinder 59 for operating the hydraulic oil to the hydraulic cylinder 59 are provided, And a control valve 60 is mechanically linked to the peripheral lever 61 (an example of the peripheral control member). Thereby, by operating the peripheral speed lever 61, the control valve 60 is operated to operate the hydraulic cylinder 59, and the hydraulic pressure in the hydrostatic stepless transmission (hereinafter referred to as " The swash plate of the pump 11P of the pump 11 is operated.

A hydraulic cylinder 62 for operating the swash plate of the motor 11M of the hydrostatic stepless speed change unit 11 as shown in Fig. 13, an electromagnetic operated control valve 63 for operating the hydraulic oil to the hydraulic cylinder 62 A shift switch 61a is provided at the grip portion of the peripheral speed lever 61 and an operation signal of the speed change switch 61a of the peripheral speed lever 61 is input to the control device 64 . Thereby, by operating the shift switch 61a of the peripheral speed lever 61, the control valve 63 is operated by the control device 64 to operate the hydraulic cylinder 62, and the hydrostatic stepless transmission 11 Of the motor 11M of the motor 11M are operated to the high-speed and low-speed positions.

As shown in Fig. 13, an operating position sensor 65 for detecting the operating position of the peripheral speed lever 61 is provided, and a traveling speed sensor 79 for detecting the running speed of the base is provided. 65 and the running speed sensor 79 are input to the control device 64. [ The detection of whether the swash plate of the motor 11M of the hydrostatic stepless transmission 11 is at the high speed position or the low speed position is carried out by the control device 64 by the operation signal of the speed change switch 61a of the peripheral speed lever 61 . 7 and 8) by the operating positions of the pump 11P and the motor 11M of the hydrostatic stepless type stepless speed change unit 11 and the running speed of the base, Speed position or low-speed position.

In the hydrostatic stepless speed changer 11 and the auxiliary speed shift device (shift member 28) shown in Fig. 13, there is a power transmission state in which the mechanical efficiency is good and a machine efficiency is inferior.

When the hydrostatic stepless transmission 11 (the pump 11P and the motor 11M) is in the high speed region and the auxiliary transmission (shift member 28) is in the high speed position, the hydrostatic stepless transmission 11 (The shift member 28) is in the high-speed position, the hydrostatic stepless transmission 11 (the pump 11P and the motor 11M) is in the low speed region, the auxiliary shift device (Shift member 28) is in the low-speed position, the mechanical efficiency becomes good. When the hydrostatic stepless speed change unit 11 (the pump 11P and the motor 11M) is in the high speed region and the auxiliary speed shift device (the shift member 28) is in the low speed position, the machine efficiency becomes poor.

In this case, in the control device 64, by the detection values of the operation position sensor 65 and the traveling speed sensor 79 and the operation signal of the shift switch 61a of the peripheral speed lever 61, If it is recognized that the apparatus 11 (the pump 11 P and the motor 11 M) is in the high speed region and the auxiliary speed shift device (the shift member 28) is in the low speed position, (Not shown) of the vehicle, so that the driver is alerted.

In the turn mode switch 78, the complete turn state, the full turn state, and the full turn turn state, described in [8] [9] [10] [11] The ground state and the extreme pivoting state can be selected because the swash plate of the motor 11M of the hydrostatic stepless transmission 11 is operated to the low speed position by the speed change switch 61a of the peripheral speed lever 61 . When the swash plate of the motor 11M of the hydrostatic stepless transmission 11 is being operated to the high speed position by the speed change switch 61a of the peripheral speed lever 61, Regardless of whether or not the loose stance state is selected.

In the following description, " grand turn " means that the left and right traveling devices 1 are driven in the same direction (forward direction) and at different speeds to turn the vehicle with a relatively large turning radius It says. The " pivot turn " means that the vehicle is turned by driving only one traveling device 1 on the other side while driving one traveling device 1 on the other. The " spin turn " means that the left and right traveling devices 1 are driven in different directions (one side in the forward direction and the other side in the backward direction) Which means that the gas is turned at a smaller turning radius.

[6]

Next, the right and left side clutches 34 (the right and left engagement portions 33R and 33L), the right and left rotation clutches 49, the relief clutch 46, the brake 50, A description will be given of the oil pressure unit 57 for operating the oil supply valve 53 to operate the working oil.

As shown in Figs. 3 and 8, a portion of the input shaft 11b of the hydrostatic stepless type continuously variable transmission 11 opposite to the input shaft 16 (the lateral side portion on the right side of the hydrostatic stepless transmission 11) The charge pump 55 and the hydraulic pump 56 are connected so that the charge pump 55 and the hydraulic pump 56 are driven by the input shaft 11b of the hydrostatic stepless transmission 11, The operating oil of the charge pump 55 is supplied to the hydrostatic stepless transmission 11.

3 and 7, the oil pressure unit 57 is connected to the outer surface of the horizontal side portion on the left side of the support frame 2 of the transmission case 10 (left portion 10L) An external piping 58 (see Fig. 12) is connected to the oil pressure unit 57 from the outside. The support frame 2 is positioned on the outer side of the left side of the oil pressure unit 57 in the state in which the preload portion 4 (support frame 2) is driven down as shown by solid lines in FIGS. 2, Is located. The support frame 2 is positioned above the left side of the left side of the oil pressure unit 57 in a state in which the preload portion 4 (the support frame 2) is driven to the upper limit as shown by the two-dot chain line in Fig. 4 have.

As shown in Figs. 1, 2, 3 and 4, when the preload section 4 (supporting frame 2) is driven upward to the upper limit, the preload section 4 is moved forward The worker can be brought in from the left side of the front part of the base to the front part of the base and the front part of the base by opening the gap between the preload part 4 and the front part of the base.

In this case, as shown in Figs. 1, 2, 3 and 4, the oil pressure unit 57 is disposed on the left side of the transmission case 2 (left side portion 10L) When the operator enters the space between the preload portion 4 and the front portion of the base body from the left side of the front portion of the base body, the hydraulic unit 57 (on the operator side) of the mission case 10 And the maintenance work of the oil pressure unit 57 can be easily performed.

[7]

Next, the structure of the oil pressure unit 57 (the right and left side clutches 34 (the right and left engagement portions 33R and 33L, the right and left circulating clutches 49, The hydraulic circuit structure of the brake 50 and the reverse clutch 53] will be described.

As shown in Figs. 5, 7, and 9, the transmission shafts 29, 44 are supported by the transmission case 10 (right and left portions 10R, 10L) The left end portion of the transmission case 29 penetrates the wall portion of the left portion 10L of the transmission case 10 and is inserted into the oil pressure unit 57. The left end portion of the transmission shaft 29 and the right and left side clutches 34, A flow passage 29b is provided in the inside of the transmission shaft 29 across the right and left side engagement clutches 33R and 33L and right and left rotation clutches 49. The left side of the transmission shaft 44 The oil passage 44a is provided in the inside of the transmission shaft 44 over the end portion and the complete line clutch 46 and the reverse clutch 53. In the oil pressure unit 57, A brake 50 is provided.

The right turn control valve 67 (corresponding to the control valve), the left turn control valve 68 (corresponding to the control valve) and the relief valve 69 (corresponding to the control) are provided in the oil pressure unit 57 as shown in Fig. (Equivalent to a control valve), an unloading valve 70 (corresponding to a control valve), a proportional control valve 71 (corresponding to a control valve), a swinging changeover control valve 72 74 (corresponding to a control valve) are provided. The external piping 58 from the hydraulic pump 56 is connected to the oil pressure unit 57 and connected to the connection surface (mating surface) of the outer surface of the oil pressure unit 57 and the mission case 10 (left portion 10L) Right and left pivot control valves 67 and 68, a relief valve 69 and an unload valve 70 are connected to a flow path 66 connected to the external piping 58 , And a connection surface (mating surface). The drain passage is formed on the connecting surface (mating surface) of the outer surface of the hydraulic unit 57 and the outer surface of the mission case 10 (left portion 10L), and the operating oil of the relief valve 69 and the unloading valve 70 And is returned to the mission case 10 (right and left portions 10R and 10L) through one drain passage.

The right side swing control valve 67 is connected to the right side clutch 34 (the right side coupling portion (right side)) through the flow path of the connecting surface (mating surface) and the flow path 29b of the transmission shaft 29, 33R) and the revolving clutch 49 on the right side. The left side swivel control valve 68 is connected to the left side clutch 34 (the left side engagement portion 33L) and the left side swivel And is connected to the clutch 49.

The right and left swing control valves 67 and 68 are configured to be electromagnetically manipulable by the supply positions 67a and 68a and the discharge positions 67b and 68b so that the discharge positions 67b and 68b ). The unloading valve 70 is configured to be electromagnetically manipulable to the shutting position 70a and the discharging position 70b and is being pressed to the shutting position 70a. The proportional control valve 71 and the swing switching control valve 72 are connected in series to the flow path 75 branched from the right and left swing control valves 67 and 68 and the flow path 29b of the transmission shaft 29 And the swing switching control valve 72 is connected to the relief clutch 46 and the reverse clutch 53 via the oil passage on the connection surface (mating surface) and the oil passage 44a on the transmission shaft 44, The swing switching control valve 72 is connected to the brake 50 via the oil passage 76 of the oil pressure unit 57. [

The oil passage 44b branched from the oil passage 44a of the transmission shaft 44 is connected between the transmission shaft 29 and the relief clutch 46 and between the transmission shaft 29 and the reverse clutch 53 so that a part of the hydraulic fluid in the oil passage 44a of the transmission shaft 44 is connected between the transmission shaft 29 and the relief clutch 46 and between the transmission shaft 29 and the reverse clutch 53 So that the stipulated time and reverse clutches 46 and 53 are cooled.

Ring shaped recesses 46b and 53b concentric with the transmission shaft 29 are formed on the pistons 46a and 53a of the fastening and reversing clutches 46 and 53 And the pistons 46a and 53a of the reverse clutch 46 and the reverse clutch 46 are moved (for example, the pistons of the loose-wheel clutch 46) The friction plate supporting portion of the transmission gears 45 and 52 and the relief shaft and the reverse clutches 46 and 53 are moved to the left side of Fig. 53b of the pistons 46a, 53a of the pistons 53, This makes it possible to prevent the rotation of the transmission shaft 29 and the relief clutch 46 and the friction between the transmission shaft 29 and the reverse clutch 53 by the pistons 46a and 53a of the relief clutches 46 and 53 Closing hydraulic fluid for cooling from the power transmission shaft 29 and the relief clutch 46 and between the transmission shaft 29 and the reverse clutch 53 becomes difficult to come out.

As shown in Fig. 12, the proportional control valve 71 is constituted by an electromagnetic operation type, and the flow rate of the operating oil can be controlled. The swing switching control valve 72 is constituted by a pilot operated type which can be operated by the complete turn position 72a, the position of the stop position 72b and the position of the stop position 72c and is pushed by the complete turn position 72a . The pilot operated valve 73 is constituted to supply the pilot operated oil branched from the oil passage 75 to the swing switching control valve 72 and to operate the vehicle with the pivotal swivel position 72b, The pilot control valve 74 is configured to supply the pilot control valve 72 with the swing switching control valve 72 to operate the swinging switching control valve 72 to the extension pivot position 72c.

The right and left swing control valves 67 and 68, the unload valve 70, the proportional control valve 71 and the pilot control valves 73 and 74 are described in [8] [9] [10] [11] And is operated by the control device 64 as described.

[8]

Next, the straight-ahead state by the steering lever 77 will be described.

As shown in Fig. 13, a steering lever 77 which is operable to the right and left is provided in the operation section 5 and the operation position of the steering lever 77 is inputted to the control device 64, 77 are configured to be operable by the straight forward position N, the first pivot positions R1 and L1 on the right and left sides and the second pivot positions R2 and L2 on the right and left sides. The turning mode switch 78 is provided in the operation section 5 and the operating position of the turning mode switch 78 is inputted to the control device 64. The turning mode switch 78 is set to the full turn position, And an extreme pivot position.

12 and 13, when the steering lever 77 is operated to the straight forward position N, regardless of the operating position of the turn mode switch 78, the right and left turn control valves 67, 68 The left and right side clutches 34 (the right and left engagement portions 33R and 33L) and the left and right side clutches 34 and 34 are operated at the discharge positions 67b and 68b and the unloading valve 70 is operated to the discharge position 70b, The left and right side clutches 34 (right and left side engagement portions 33R and 33L) are operated in the transmission state and the right and left side clutches 34 49) is operated in a state of inversion. The broken line and reverse line broken clutches 46 and 53 are operated to the disconnected state by the proportional control valve 71 and the brake 50 is operated to the disengaged state.

As a result, the power of the input shaft 22 is transmitted to the transmission shaft 27, the transmission gears 30 and 31, the transmission shaft 29, the right and left transmission shafts 30 and 31, The right and left output gears 32R and 32L, the transmission gear 36, the transmission shaft 35, the transmission gears 37 and 39, , The right and left axles 38 to the crawler traveling apparatus 1 on the right and left sides, and the gas goes straight.

[9]

Next, the state of the complete turn by the steering lever 77 will be described.

When the turning mode switch 78 is operated to the complete turn position as shown in Figs. 12 and 13, the pilot control valves 73 and 74 cause the turning control valve 72 to move to the complete turn position 72a . Thus, when the steering lever 77 is operated to the first pivotal position R1 on the right side, the right turn control valve 67 is operated to the supply position 67a and the unloading valve 70 is operated to the shutoff position 70a And the hydraulic oil is supplied to the right side clutch 34 (the right side engagement portion 33R) and the right side swing clutch 49 while the right side clutch 34 (the right side engagement portion 33R) Is operated in the cut-off state, and the right-hand rotating clutch 49 is operated in the electric form.

In this case, since the left side turning clutch 49 is in the inverted state as shown in Figs. 7 and 9, the power of the left side clutch 34 (left side engagement portion 33L) Is transmitted to the output gear 32R on the right side via the right side turning clutch 49 from the left side turning clutch 32L and the left side turning clutch 49 so as to rotate in the same direction as the transmission shaft 29 A slightly low speed power is transmitted to the right output gear 32R. As a result, the gas gently changes direction to the right.

As shown in Figs. 12 and 13, when the steering lever 77 is operated to the right first pivotal position R1, the right swing control valve 67 is operated to the supply position 67a as described above The unloading valve 70 is operated to the cutoff position 70a and the hydraulic oil is supplied to the relief clutch 46 via the proportional control valve 71 and the swing switching control valve 72 The proportional control valve 71 controls the amount of rotation of the relief clutch 46 so that as the steering lever 77 is operated from the first pivotal position R1 on the right side to the second pivotal position R2 on the right side, The operating pressure is increased.

As shown in Figs. 7 and 9, when the operating pressure of the relief clutch 46 is raised by the proportional control valve 71 based on the operating position of the steering lever 77, The electric power of the right side coupling portion 33R, the electric transmission gear 45, the clearance circuit clutch 46, the transmission shaft 44, the transmission gear 48, the swing clutch case 47 and the right side swing clutch 49, The lower speed power is transmitted to the right output gear 32R through rotation of the transmission shaft 29 in the same direction as the transmission shaft 29. [

In this case, as shown in Figs. 7 and 9, the power from the left side clutch 34 (left side engagement portion 33L) and the power from the relief clutch 46 are simultaneously transmitted to the right output gear The power from the left side clutch 34 (the left side engagement portion 33L) is transmitted to the relief clutch 46 (the left side engagement portion 33L) when the operating pressure of the relief clutch 46 is in the low pressure range, And the right output gear 32R is driven by the power from the left side clutch 34 (left-side engagement portion 33L). As a result, when the operating pressure of the fastening line clutch 46 is in the low pressure range, the gas gently changes direction to the right.

7 and 9, when the operating position of the steering lever 77 approaches the second pivotal position R2 on the right side and the working pressure of the relieved revolution clutch 46 becomes a high pressure, The power from the clutch 46 drives the power from the left side clutch 34 (the left side engagement portion 33L) and the output gear 32R on the right side is driven by the power from the relief clutch 46 do. In this state, the right output gear 32R is driven by the power from the left side clutch 34 (left-side engagement portion 33L) The output gear 32R of the right side is driven at a low speed and the base body is wound to the right side.

12 and 13, when the steering lever 77 is operated to the left first pivotal position L1, the left swing control valve 68 is operated to the supply position 68a, and the unloading valve 70 The operating oil is supplied to the left side clutch 34 (the left side coupling portion 33L) and the left side circulation clutch 49 and the left side clutch 34 (left side And the left swivel clutch 49 is operated to the electric state. At the same time, the same operation as described above is performed, and the gas gently changes direction to the left. When the steering lever 77 is operated from the first pivotal position L1 on the left side to the second pivotal position L2 on the left side, the same operation as described above is performed, and the gas turns to the left side.

[10]

Next, the state of the landing by the steering lever 77 will be described.

12 and 13, when the swing mode switch 78 is operated to the stop position, the swing switching control valve 72 is operated by the pilot operation valves 73 and 74 to the stop position 72b do. Thus, when the steering lever 77 is operated to the right first pivotal position R1, the right swing control valve 67 is operated to the supply position 67a and the unloading valve 70 is operated to the shutoff position 70a. And the hydraulic oil is supplied to the right side clutch 34 (right side engagement portion 33R) and the right side revolving clutch 49 while the right side clutch 34 (right side engagement portion 33R) And the right turning clutch 49 is operated to the electric state. In this case, since the left swing clutch 49 is in the inverted state, the vehicle gently changes its direction to the right as in the case of [9].

12 and 13, when the steering lever 77 is operated to the first pivotal position R1 on the right side, the right turn control valve 67 is operated to the supply position 67a as described above, The hydraulic oil is supplied to the brake 50 via the proportional control valve 71 and the swing switching control valve 72 (the pivot position 72b) while the valve 70 is operated to the shutoff position 70a The operating pressure of the brake 50 is increased by the proportional control valve 71 as the steering lever 77 is operated from the first pivotal position R1 on the right side to the second pivotal position R2 on the right side, do.

The operating pressure of the brake 50 is raised by the proportional control valve 71 on the basis of the operating position of the steering lever 77 as shown in Figs. 7 and 9, The braking force is applied to the right output gear 32R through the gear 48, the swing clutch case 47 and the right swing clutch 49. [

7 and 9, the power from the left side clutch 34 (left side engagement portion 33L) and the braking force of the brake 50 are simultaneously transmitted to the right output gear 32R, The power from the left side clutch 34 (the left side engagement portion 33L) overcomes the braking force of the brake 50 when the operating pressure of the brake 50 is in the low pressure range, The right output gear 32R is driven by the power from the side clutch 34 (left-side engagement portion 33L). Thereby, when the operating pressure of the brake 50 is in the low pressure range, the gas gently changes direction to the right.

7 and 9, when the operating position of the steering lever 77 approaches the second pivotal position R2 on the right side and the working pressure of the brake 50 becomes a high pressure, The braking force of the left side clutch 34 (the left side engagement portion 33L) increases the power from the left side and the braking force of the brake 50 causes the right side output gear 32R to be in the braking state, Shinji turns around.

12 and 13, when the steering lever 77 is operated to the left first pivotal position L1, the left swing control valve 68 is operated to the supply position 68a, and the unloading valve 70 Is operated to the cutoff position 70a and the operating oil is supplied to the left side clutch 34 (the left side coupling portion 33L and the left side turning clutch 49), and the left side clutch 34 And the left swivel clutch 49 is operated to the electric state. At the same time, the same operation as described above is performed, and the gas gently changes direction to the left. When the steering lever 77 is operated from the first pivotal position L1 on the left side to the second pivotal position L2 on the left side, the same operation as described above is carried out, and the vehicle is pivoted to the left.

As shown in Figs. 12 and 13, a steering switch 77a is provided on the grip portion of the steering lever 77. Fig. The turning mode switch 78 is operated to the complete turning position as described in the preceding paragraph [9], and the steering lever 77 is moved from the first pivot position R1 (L1) on the right side (left side) , It is necessary to turn to the smaller radius in the right turn state operated on the second turning position [R1 (L1)].

In this case, as shown in Figs. 12 and 13, when the steering lever 77 is moved from the first pivotal position R1 (L1) on the right side (left side) to the second pivotal position R1 (L1) When the steering switch 77a of the steering lever 77 is depressed and operated, the swing switching control valve 72 is operated from the complete turn position 72a to the ground pivot position 72b, (Left). The turning control valve 72 is operated only when the steering switch 77a of the steering lever 77 is depressed and operated. When the steering switch 77a of the steering lever 77 is released, Is turned from the new-land turning position 72b to the complete turn position 72a, and the gas returns to the complete turn state.

[11]

Next, the steering wheel turning state by the steering lever 77 will be described.

When the swing mode switch 78 is operated to the extreme pivot position as shown in Figs. 12 and 13, the pilot control valves 73 and 74 cause the swing switching control valve 72 to move to the destination swing position 72c, . Thus, when the steering lever 77 is operated to the right first pivotal position R1, the right swing control valve 67 is operated to the supply position 67a and the unloading valve 70 is operated to the shutoff position 70a. And the hydraulic oil is supplied to the right side clutch 34 (right side engagement portion 33R) and the right side revolving clutch 49 while the right side clutch 34 (right side engagement portion 33R) And the right turning clutch 49 is operated to the electric state. In this case, since the left swing clutch 49 is in the inverted state, the vehicle gently changes its direction to the right as in the case of [9].

12 and 13, when the steering lever 77 is operated to the first pivotal position R1 on the right side, the right turn control valve 67 is operated to the supply position 67a as described above, The hydraulic oil is supplied to the reverse clutch 53 via the proportional control valve 71 and the swing switching control valve 72 (the extension pivot position 72c) while the valve 70 is operated to the shutoff position 70a And the operating pressure of the reverse clutch 53 is reduced by the proportional control valve 71 as the steering lever 77 is operated from the right first pivotal position R1 to the right second pivotal position R2, Up operation.

The operating pressure of the reverse clutch 53 is raised by the proportional control valve 71 based on the operating position of the steering lever 77 as shown in Figs. 7 and 9, The power is transmitted to the transmission shaft 29 via the transmission gears 51 and 52, the reverse clutch 53, the transmission shaft 44, the transmission gear 48, the swing clutch case 47 and the right swing clutch 49, And is transmitted to the right output gear 32R as the power of the reverse rotation.

In this case, as shown in Figs. 7 and 9, the power from the left side clutch 34 (left side engagement portion 33L) and the power from the reverse clutch 53 are simultaneously transmitted to the right output gear When the operating pressure of the reverse clutch 53 is in the range of low pressure, the power from the left side clutch 34 (left side engagement portion 33L) is transmitted from the reverse clutch 53 And the right output gear 32R is driven by the power from the left side clutch 34 (left side engagement portion 33L). Thus, when the operating pressure of the reverse clutch 53 is in the low pressure range, the gas gently changes direction to the right.

Next, when the operating position of the steering lever 77 approaches the second pivot position R2 on the right side and the operating pressure of the reverse clutch 53 becomes high, as shown in Figs. 7 and 9, the reverse clutch Power from the left side clutch 34 (the left side engagement portion 33L) is applied to the power from the right clutch 53 and the right side output gear 32R is driven by the power from the reverse clutch 53. In this state, the output gear 32R on the right side is driven in the reverse direction with respect to the output gear 32L on the left side, and the base body is pivoted to the right side.

12 and 13, when the steering lever 77 is operated to the left first pivotal position L1, the left swing control valve 68 is operated to the supply position 68a, and the unloading valve 70 The operating oil is supplied to the left side clutch 34 (the left side coupling portion 33L) and the left side circulation clutch 49 and the left side clutch 34 (left side And the left swivel clutch 49 is operated to the electric state. At the same time, the same operation as described above is performed, and the gas gently changes direction to the left. When the steering lever 77 is operated from the first pivotal position L1 on the left side to the second pivotal position L2 on the left side, the same operation as described above is performed, and the vehicle turns to the left side.

[12]

As shown in Figs. 8 and 17 to 18, the hydrostatic stepless transmission (HST) 11 as a peripheral speed device is provided with an axial plunger type pump (not shown) capable of steplessly changing the rotational speed in the HST case 11A And a motor 11M in the form of an axial plunger capable of shifting the rotational speed to the high and low second speeds. The pump 11P and the motor 11M are connected to each other by a closed circuit 81, (11).

The pump 11P is constituted to drive and control the movable swash plate 11D capable of changing the rotating speed by the reciprocating cylinder 82 and the hydraulic oil supplied to the reciprocating cylinder 82 is supplied to the electromagnetic proportional control valve 83 And the like.

On the other hand, the motor 11M is configured to drive and control the movable swash plate 11D capable of changing the rotational speed by the reciprocating cylinder 84, and the hydraulic oil supplied to the reciprocating cylinder 84 is supplied to the two electromagnetic ON- OFF valve 85 in order to control the flow rate.

In this manner, the capacity of the motor 11M is configured to be variable. The cylinder capacity used for the motor 11M is larger than the cylinder capacity of the pump 11P, and the cylinder is arranged so that the control angle of the movable swash plate 11D can be set in two stages.

The reciprocating cylinder 84 for the motor 11M is provided in the one working space with the urging spring 86 for returning to the low speed position so as to press the electromagnetic valve 85. When the electromagnetic valve 85 fails, .

Since the pressing spring 86 is applied to only one side of the piston 87 in the reciprocating cylinder 84 in this way, the operating speed of the piston 87 is different. However, An orifice 88 is provided in the flow path to adjust the operating speed.

With the above-described configuration, the switching between the work travel and the road running is performed by switching the motor 11M to the high and low position.

As shown in Figs. 14 to 16, the operation section 5 is provided with a peripheral speed lever 61 for changing the speed of the pump 11P in the lateral direction of the driver's seat 6 so as to be movable forward and backward And a switch 61a for shifting the motor 11M to the high and low second ends is provided in the grip portion 61A of the peripheral speed lever 61. [

When the main switch is turned on again after stopping the traveling gas and turning off the main switch, the motor 11M is set to the low speed state irrespective of the state at the time point when the main switch is turned off.

The input shaft receiving the power transmission from the engine 7 is defined as the input shaft 11b as the pump shaft of the pump 11P and the input shaft 11b is projected from the HST case 11A A charge pump 55 for supplying working oil to the closed circuit 81 and a hydraulic pump 56 as a mission pump for supplying hydraulic oil to the hydraulic clutch used for transmission are provided on the input shaft 11b provided in a protruded manner, Are installed in two consecutive years. The charge pump 55 and the hydraulic pump 56 are separated by a seal, and a separate system hydraulic oil is used as the hydraulic oil.

Next, the configuration in the mission case 10 will be described. 7 and 8, an input shaft 22 receiving power transmission from a hydrostatic stepless speed changer 11 is installed at one end of the transmission case 10, And a transmission shaft 27 as an axis is provided. A gear type auxiliary speed-change mechanism A capable of high-low two-speed shifting is provided between the input shaft 22 and the transmission shaft 27. A parking brake mechanism B is provided at one end of the transmission shaft 27 .

The gear type auxiliary transmission mechanism A will be described. Two large and small gears 25 and 26 are loosely supported on the input shaft 22 and the transmission shaft 27 as shown in Figs. 7 and 19, The sleeve 28 is disposed and the clutch sleeve 28 is engaged with the gear portion 27a of the transmission shaft 27. [

The gear type negative speed change mechanism A capable of achieving a high and low speed state by selectively coupling the clutch sleeve 28 to one of the large and small gears 25 and 26 and the gear portion 27a of the transmission shaft 27 Respectively.

The clutch sleeve 28 is set to a high-speed state both during work travel and on-road traveling, and is switched to the low-speed side only for emergency escape.

As described above, the gear type negative speed transmission mechanism A is configured such that the shift fork 150 for operating the clutch sleeve 28 is slidably mounted on the operation shaft 151 on the other surface that is not shifted during normal travel And a camshaft 152 for slidingly driving the shift fork 150 is supported by the transmission case 10 and an end portion of the camshaft 152 protruding from the transmission case 10 is provided with an auxiliary shift lever (For example, an operation arm 128A for an example). As shown in Figs. 11 and 14 to 15, the auxiliary shift lever 128 connected to the operating arm 128A is installed upright from the side of the transmission case 10, Respectively. That is, the auxiliary speed change lever 128 that performs the switching control of the gear type auxiliary transmission mechanism A is disposed outside the operation control space.

The structure in the mission case 10 will be described. (A side clutch shaft) 29 on which a transmission shaft (pivot shaft) 44 for swinging and a side clutch 34, 34 or the like are mounted in parallel with the transmission shaft 27 as shown in Fig. 7, And the transmission gear 51 that outputs the transmission gear to the transmission shaft 44 and the transmission gear 30 that outputs the transmission gear to the transmission shaft 29 are connected to the gear type auxiliary transmission mechanism A of the transmission shaft 27, And the brake mechanism B for the vehicle.

In the mission, it is possible to perform three types of turning operations, that is, a straight line running, a quick turn, and a new-line turning, in addition to the straight running. Each of the clutches and the gears for enabling these turning operations is connected to the transmission shaft 44, And is provided on the shaft on the downstream side.

A transmission gear 53 engaged with the transmission gear 51 is loosely rotatably supported on the transmission shaft 44 and a reverse clutch 53 which is a multi-plate friction grounding clutch adjacent to the transmission gear 52 Respectively.

9, the reverse clutch 53 includes a clutch boss 53A integrally formed with the transmission gear 52, a clutch body 53B fixed to the transmission shaft 44, A friction platen 53C, and a piston 53a. A multi-plate friction drive brake C for a sudden turn is mounted at one end of the transmission shaft 44. [ A loosening clutch 46 is provided at the other end opposite to the traveling brake C with the reverse clutch 53 interposed therebetween and the transmission gear 45 is loosely fitted to the other end of the loosening clutch 46, And is rotatably supported.

9, a multi-plate type friction rotary clutch 49 for transmitting power to either one of the left and right crawler traveling devices 1 is mounted on the transmission shaft 29, The turning clutch 49 is provided with a transmission gear 47a engaging with the transmission gear 48 so as to receive power transmission from the transmission gear 48 fixed between the reverse clutch 53 and the loose- .

As shown in Figs. 7, 9, and 17, the transmission gear 45, which is also used as the clutch boss of the fastener chain clutch 46, is loosely supported on the transmission shaft 44, And is engaged with the gear 33 of the left and right side clutches 34 coupled to the splines. With this configuration, the complete rotation turning force is configured to be returned from the power transmission shaft 29 to the power transmission shaft 44 and transmitted to the transmission gear 48 and the orbiting clutch 49. The other side of the transmission shaft 29 is provided with the other side clutch 34 so that it can output to the axle 38. [

The transmission gear 31 is loosely rotated and supported on the side ends of the side clutches 34 on the other side of the left and right sides so as to engage with the transmission gear 30 provided on the transmission shaft 27, To receive the delivery.

The linkage structure of the right side clutch 34 and the orbiting clutch 49 is as follows. The right clutch C is provided between the gear 33 of the right side clutch 34 and the clutch case 47B of the orbiting clutch 49 so as to be engaged with the gear 33, The sleeve 32 is loosely rotatably supported. The right clutch sleeve 32 has an output gear portion 32R to the axle 38. [

9, a hydraulic piston 42 is interposed between the right clutch sleeve 32 and the gear 33. This piston 42 receives pressure oil to make contact with the gear 33, The gear 33 urged in the coupling direction is switched to the state of being separated from the right clutch sleeve 32 so that the gear 33 and the right clutch sleeve 32 reach the clutch off state. When the pressurized oil is released, the gear 33 urged by the spring pushes the piston 42 and is engaged with the right clutch sleeve 32.

The right clutch sleeve 32 is engaged with the transmission gear 36 provided on the transmission shaft 35 as an idle shaft provided between the axle 38 and the transmission shaft 29, And is configured to be able to transmit power to the axle 38.

Next, the structure of the left side clutch 34 as shown in Figs. 7 and 9 will be described. The structure of the left side clutch 34 is different from that of the right side clutch 34. [ That is, the clutch boss 45, which does not correspond to the gear 33 and is not provided with the gear, is configured to be able to engage and disengage from the left clutch sleeve 32 belonging to the orbiting clutch 49 so that the left side clutch 34 Respectively. The clutch boss 45 is urged by a spring in a direction in which it engages with the left clutch sleeve 32.

With the above configuration, when the left side clutch 34 is set to the ON state, the rotational power introduced from the transmission shaft 27 through the transmission gear 31 to the transmission shaft 29 is transmitted to the left side clutch 34 to the axle 38 as rectilinear power. When the left side clutch 34 is set to the OFF state, the turning output can be output to the axle 38 via the orbiting clutch 49 as described above.

With the above-described configuration, three turning states are generated. In addition, the electric path to one (left) crawler traveling apparatus 1 that maintains the traveling speed at the time of going straight is as follows.

The power from the input shaft 22 is transmitted to the transmission gear 30 mounted on the transmission shaft 27 and the transmission gear 31 splined to the transmission shaft 29. The left side clutch The left clutch sleeve 26 serving as the turning clutch 34 and the electric transmission gear 36 serving as the left clutch sleeve 36 as well as the transmission shaft 35 on the left side and the axle 38 on the left side.

The electric path to the crawler traveling device 1 on the other side (right side) at the time of complete winding is as follows.

7 and 9, the power from the input shaft 22 is transmitted to the transmission gear 30 mounted on the transmission shaft 27 and the transmission gear 31 and the transmission gear 31, which are loosely rotated on the transmission shaft 29. [ The clutch 33 of the right side clutch (in this case, the side clutch is in the OFF state) 34, and the transmission clutch 46 of the transmission gear 45, which is also used as the clutch boss, A case 46A, a transmission shaft 44, a transmission gear 48 provided on the transmission shaft 44, a rotary clutch 49 having a transmission gear 47a meshed with the transmission gear 48, Is transmitted to the right clutch sleeve 32 of the clutch 49 - the transmission gear 36 on the right side - the transmission shaft 35 on the right side - the axle 38 on the right side.

The electric path to the crawler traveling apparatus 1 on the other side (right side) at the time of the pivotal turning is as follows.

In this case also, the crawler traveling apparatus 1 on one side (left side) maintains the straight-ahead state. That is, the power from the input shaft 22 is transmitted to the transmission gear 30 mounted on the transmission shaft 27, the transmission gear 31 loosely supported on the transmission shaft 44, and the left side clutch The clutch sleeve 26 which is also used as the rotary clutch 49 and the fifth input gear 22 on the left side of the transmission shaft 35 on the left side .

The crawler traveling apparatus 1 on the right side rotates in the opposite (backward) direction at a speed that is one-third of the speed of the left crawler traveling apparatus 1, and is set in the ground pivot operation state. 7 and 9, the power from the input shaft 22 is transmitted through the transmission gear 51 mounted on the transmission shaft 27, the transmission gear loosely supported on the transmission shaft 44 The clutch boss 52 of the clutch 53, the clutch body 53B of the reverse clutch 53, the transmission shaft 44, the transmission gear 48 provided on the transmission shaft 44, The right clutch sleeve 32 of the turning clutch 49, the transmission gear 36, the right transmission shaft 35, and the right-side axle 38 of the revolving clutch 49, ).

The electric path to the crawler traveling device 1 on the other side (right side) at the time of complete winding is as follows.

In this case, however, the crawler traveling apparatus 1 on one side (left side) maintains the straight-ahead state. That is, the power from the input shaft 22 is transmitted to the transmission gear 30 mounted on the transmission shaft 27, the transmission gear 31 loosely supported on the transmission shaft 44, and the left side clutch The left clutch sleeve 32 and the left transmission gear 36 and the transmission shaft 35 on the left side and the axle 38 on the left side of the left clutch sleeve 32 serving as the swing clutch 49 do.

As shown in Figs. 7 and 9, a drive brake C is provided on the transmission shaft 44, and the drive brake C is switched to ON by hydraulic pressure. The right clutch of the transmission gear 48 -rotated clutch 49 fixed to the transmission shaft 44 is connected to the ON-right clutch sleeve 32 (the right side clutch 34 is OFF And the braking force is transmitted to the axle 38 on the right side of the transmission gear 36, the transmission gear 36 on the right side, and the transmission shaft 35 on the right side.

When the turning operation is performed while the motor 11M of the above-described hydrostatic stepless transmission 11 is set to the high-speed state, the turn-around mode is employed in the turn-around mode. As a result, the traveling stability is ensured even when the vehicle is running on the road without causing a sudden turn mode or a new ground turning mode.

Next, the structure of the parking brake mechanism B will be described. The brake case 133 is fitted and held in the mounting boss portion 10A for supporting the transmission shaft 27 of the transmission case 10 as shown in Figs. 19 to 22, Type friction disc 134 and the cam disc 135 which is in press-contact with the brake disc 134 are housed in the parking brake mechanism B to constitute the parking brake mechanism B.

The cam mechanism E is provided over the inner side wall 133A of the brake case 133 and the back side of the cam disk 135 opposed to the inner side wall 133A. As shown in Figs. 21 and 22, the ball 136 is held and held at three positions in the circumferential direction of the inner wall 133A, and at the three positions in the circumferential direction on the back surface of the cam disk 135, And an engaging hole 135A to be engaged with the engaging portion 136 is formed. The engaging hole 135A is provided with an induction surface 135a, which is tapered toward the one circumferential direction and has a gradually decreasing coupling depth and a narrow coupling width.

The cam mechanism E is constituted by the cam disc 135 and the ball 136. [

The guide pin 137 is embedded and fixed at the same radial position at a position different from the engagement hole 135A in the inner wall 133A and the tip end portion of the guide pin 137 is projected from the surface of the inner wall 133A It is installed and installed. The engaging elongated hole 135B along the circumferential direction is formed with a certain depth from the back side of the cam disk 135 and the cam disk 135 is mounted in a predetermined position of the brake case 133 The guide pin 137 is engaged in the engagement long hole 135B.

As shown in Figs. 9 and 19 to 22, a coil spring 138 is accommodated in the coupling long hole 135B, and the coil spring 138 is inserted into a guide pin 137 and one long end of the coupling long hole 135B. Is acted by the coil spring 138 as a resistance when the cam disk 135 is rotated in the circumferential direction, and is pressed toward the return direction. This coil spring 138 is referred to as a return spring that rotates the cam disk 135 in the return direction (opposite direction).

As shown in Fig. 21, a through hole 135C is formed at the rotation center position of the cam disk 135 to allow the shaft end of the transmission shaft 27 to enter. The cam disk 135 is loaded on the depth side of the brake case 133 and the wet type multiple friction brake disk 134 is placed on the entrance side of the cam disk 135. [

As shown in Fig. 21, a pressure plate 139 is provided near the entrance of the brake disk 134, and the pressure plate 139 is prevented from being pulled out by the fixing ring 140 for the hole.

With the above arrangement, the cam disk 135, the wet type multi-disc type friction brake disc 134, and the pressure plate 139 are prevented from coming off by the hole fixing ring 140, The shaft end of the transmission shaft 27 enters the through hole 135C of the cam disk 135. [

The operation mechanism for the parking brake mechanism B will be described. A through hole 133B communicating with the storage space for storing the cam disk 135 and the like is formed on the outer surface of the brake case 133 as shown in Figs. 19 to 22, Thereby projecting the portion 133C. A fixing portion 133D having a screw hole 133a is provided at a position spaced apart from the boss portion 133C by a predetermined distance in the radial direction. An operation shaft 141 linked to a parking brake operation opening (not shown) is inserted and held in the through hole 133B of the boss 133C and the operation shaft 141 is inserted into the through hole 133B As shown in Fig. A groove 141a for an O-ring is formed in the operating shaft 141, and rotational resistance in the circumferential direction and moving resistance in the axial direction are attached by mounting the O-ring 142. [

The shaft end 141b of the operation shaft 141 is projected from the boss 133C and the operation arm 143 is connected to the shaft end 141b as shown in Figs. A rotation regulating plate 144 with respect to the operation arm 143 is bolted and fixed between the proximal end 143A of the operation arm 143 and the distal end face 133c of the boss 133C. The rotation regulating plate 144 has a base end 144A formed with an insertion hole for external insertion into the operation shaft 141 and a fixing portion 133D formed with a screw hole 133a from the base end 144A. The through hole 144C for bolt fastening and the bearing restricting portion 144D of the operation arm 142 are formed by uplifting the tip end portion 144B of the cam disk 135, Is placed at the brake ON position. In addition, a pressing spring (not shown) may be provided to position the cam disk 135 at the brake ON position.

As shown in Figs. 19 to 22, a cam hole 135b concaved into the thickness is formed in one circumferential direction on the back side of the cam disk 135. As shown in Fig. On the other hand, an eccentric protrusion 141c protrudes from the distal end face of the operation shaft 141, which is fixed to the operation arm 142 and faces the cam disk 135. The cam disc 135 can be rotated in the direction of the driving shaft 27 by engaging the eccentric protrusion 141c with the cam hole 135b of the cam disc 135 and rotating the operating arm 142 .

Although not shown, the operation arm 143 is provided with a linkage mechanism, and is operable by an operation opening provided in the operation control section.

With the above-described configuration, when the operator operates the operation tool, the operation arm 143 is operated from the position of the solid line a to the position of the virtual line b as shown in Fig. 21 (b), the cam disk 135 rotates the brake disk 134 (see Fig. 21 (b)) from the brake OFF state shown in Fig. 21 So that the brake-ON state is generated.

When the cam disk 135 rotates, the cam disk 135 gradually presses the brake disk 134 in a state in which the guide surface 135a of the engaging hole 135A also rides on the ball 136. [ Thereby, the brake can be turned ON and operated.

[13]

Next, the detailed structure of the left and right traveling devices 1 and 1 will be described with reference to Figs. 23 to 30. Fig. Since the traveling device 1 has the same configuration on the left and right, only the traveling device 1 on the left side is shown in these drawings, and the traveling device 1 on the right side is omitted.

23 is a side view of the traveling device 1. Fig. Fig. 24 is a plan view of the traveling device 1. Fig. As shown in these figures, the traveling apparatus 1 includes a main track frame 210 along the front-rear direction, and a front swinging track frame 211 Four ground wheels 213 (hereinafter referred to as front ground wheels 213), which are provided in the front swinging track frame 211 and are arranged and supported in the forward and backward directions, and a rear swinging track frame 212, Four ground wheels 214 (hereinafter referred to as rear ground wheels 214) which are arranged and supported in the forward and backward directions on the swinging track frame 212. The front ground wheels 213 and the rear ground wheels 214 A crawler drive wheel 215 arranged on the front side of the front ground wheel 213 and a crawler drive wheel 216 disposed on the rear side of the front ground wheel 213 and the rear ground wheel 214, And an upper guide wheel 217 disposed above the ground wheel 214. The crawler drive wheel 215 and four And a rubber crawler belt 218 wound around the front ground wheels 213, the four rear ground wheels 214, the crawler guide wheels 216 and the two upper guide wheels 217 have.

The main track frame 210 is supported on a traveling support frame portion 207 provided on the base frame 100 through a lifting operation mechanism 240 having a pair of pivotal connection arms 241 and 242 have. The running support frame portion 207 is constituted by a steel pipe material for the gas flow front and rear which is connected to the base frame 100 through a pair of connecting members 208, 208 in the fore-and-aft direction.

The crawler drive wheel 215 is rotatably supported by a transmission case 10 provided at a front end portion of the base frame 100. The crawler drive wheel 215 is driven by a forward mission (not shown) located in the interior of the mission case 10 to switch between a forward side and a backward side to drive the crawler belt 218 to the front ground wheel 213 And is driven to rotate to the forward side or the backward side along the rear ground wheel 214, the crawler guide wheel 216 and the upper guide wheel 217. Each of the upper guide wheels 217 is loosely rotatably supported on the travel support frame portion 207. [

A connecting portion provided with a cylinder in the middle in the longitudinal direction of the front swinging track frame 211 and a supporting portion 210a provided with a cylindrical body at the front end portion of the main track frame 210 are provided on the supporting shaft 221 And the front swinging track frame 211 is pivotally supported on the support portion 210a so as to pivot upward and downward about the support shaft 221 with the axis of the support shaft 221 as the swing axis center P1.

The four front ground wheels 213 are positioned such that two front ground wheels 213 are located on the gas front side of the swing axis center P1 of the front swing track frame 211, And is loosely rotatably supported on the front swinging track frame 211 in a distributed arrangement in the forward and backward directions so that the two front grounding wheels 213 are located.

A connecting portion provided with a cylinder in the middle in the longitudinal direction of the rear swinging track frame 212 and a supporting portion 210b provided with a cylindrical body at a rear end portion of the main track frame 210, And the rear swinging track frame 212 is pivotally supported by the support portion 210b such that the support shaft 222 swings up and down with the swing axis center P2 as the axial center of the support shaft 222 in the gas transverse direction.

The four rear ground wheels 214 are positioned such that two rear ground wheels 214 are positioned on the gas front side of the swing axis P2 of the rear swing track frame 212 and the rear ground wheels 214 are located on the gas rear side And is loosely rotatably supported on the rear swinging track frame 212 in a backward and rearwardly distributed arrangement so that the two rear ground wheels 214 are located.

The crawler guide wheel 216 guides the inner surface of the crawler belt 218 so that the crawler belt 218 passing through the rear ground wheel 214 or the upper guide wheel 217 is returned to the front side. The crawler guide wheel 216 is connected to the rear pivot track frame 212 via a support structure H having an angular tubular support 225 loosely and rotatably connected to the rear end of the crawler guide wheel 216 As shown in Fig.

The front swinging track frame 211 and the rear swinging track frame 212 are provided with a crawler guide 219. The crawler guides 219 of the respective track frames 211 and 212 are engaged between the pair of left and right core projections of the crawler belt 218 to separate the crawler belts 218 from the ground wheels 213 and 214 prevent.

Figure 25 is a longitudinal side view of the support structure (H). 26 is a plan view of the support structure H; As shown in these drawings, the supporting structure H is a structure in which a plate member is provided at the rear end of another rear swinging track frame 212 having the support 225, A tension spring 227 provided inside the holding cylinder 226, and a tension adjusting screw shaft 228. The tension springs 227,

The holding cylinder 226 holds the front end side of the support body 225 by inserting the front end side of the support body 225 slidably.

The tension spring 227 is interposed between a spring receiving portion 229 located inside the holding cylinder 226 and a spring contacting portion 225a provided on the supporting body 225. [ That is, the tension spring 227 presses the spring contact portion 225a against the spring contact portion 225a by using the spring receiving portion 229 as a reaction force member, thereby sliding the support body 225 to the side projecting from the holding cylinder 226, And the crawler guide wheel 216 is pressed against the crawler belt 218.

The spring receiving body 229 is slidably held in the holding cylinder 226 and is screwed to the tension adjusting screw shaft 228. The tension adjusting screw shaft 228 is rotated so that the spring receiving body 229 is moved along the retention cylinder 226 to thereby adjust the movement of the crawler belt 216 of the crawler guide wheel 216 by the tension spring 227. [ (218).

23, the front swinging track frame 211 and the rear swinging track frame 212 are configured such that the center of gravity G of the machine body is positioned on the horizontal plane of the forward swinging track frame 211, And is disposed on a vertical line passing between the rear swinging track frame 212.

That is, when the working machine is moved from a relatively high level to a low level, the movement of the traveling device 1 can be suppressed while suppressing the generation of a grounding impact when the entire traveling device 1 is lowered.

27 (a) and 27 (b) are side views of the traveling device 1 when the working machine is advanced from the high place S to the low place T and moved.

As shown in FIG. 27 (a), when the center of gravity G of the vehicle is advanced from the high place S to the low place T with the forward movement of the working machine, the front end side of the traveling device 1 is lower (T) and grounded, so that the traveling device 1 is grounded at an inclined posture in which the traveling device 1 goes down from the low point T to the high point S. The front swinging track frame 211 is pivoted in the direction of the swing axis P1 due to the grounding reaction force acting on the front end side of the traveling device 1 so that the rear end side of the front swinging track frame 211 is moved to the main track frame 210 So that the front ground wheel 213 supported on the front swinging track frame 211 can easily be grounded at the low point T and the flat surface C. [

27 (b), when the working machine further moves, the rear swinging track frame 212 swings in the direction of the swing axis P2 by the ground reaction force acting on the rear end side of the traveling device 1, The front end side of the swinging track frame 212 descends with respect to the main track frame 210 so that the rear grounding wheel 214 supported by the rear swinging track frame 212 is positioned at the low position T and the bottom face C It becomes easy to ground. As a result, the traveling apparatus 1 descends to the low point T while earthing the large number of the front ground wheels 213 and the rear ground wheels 214 early, T), it is possible to suppress the generation of grounding shock.

When the traveling apparatus 1 is moved backward from a high place to a low place and the traveling apparatus 1 is in a tilted posture which is grounded over a low place T and a high place S, And the front swinging track frame 211 is located on the upper side and is a relative position in the up-and-down direction of the front swinging track frame 211 and the rear swinging track frame 212. However, in that the ground wheels 213, 214 supported by the rear swinging track frame 212 and the front swinging track frame 211 are easily grounded at the low point T or the bottom surface C, .

When the rocking of the front rocking track frame 211 and the rocking motion of the rear rocking track frame 212 occurs, movement of the front grounding wheel 213 with respect to the main track frame 210 due to rocking of the front rocking track frame 211, Movement of the rear ground wheel 214 relative to the main track frame 210 due to the swinging motion of the rear rocking track frame 212 may generate an operation force in the direction of increasing the tension of the crawler belt 218. [ At this time, the crawler guide wheel 216 oscillates together with the rear swinging track frame 212 to move in the direction to relax the tension of the crawler belt 218. [ Even when the tension of the crawler belt 218 is increased, the tension spring 227 is elastically deformed with the increase in the tension, and the crawler guide wheel 216 moves backward to the retention cylinder 226 side. Whereby the increase in tension of the crawler belt 218 is suppressed.

23, the traveling apparatus 1 includes an intermediate portion of the main track frame 210, a swing restricting mechanism 230 provided across the front swinging track frame 211 and the rear swinging track frame 212, .

28 is a side view of the swing restricting mechanism 230. Fig. 29 is a plan view of the swing restricting mechanism 230. Fig. As shown in these figures, the rocking motion restricting mechanism 230 includes a front rocking regulating link 231 extending from the rear end of the front rocking track frame 211 and a front rocking regulating link 231 extending from the front end of the rear rocking track frame 212 And a stopper portion 233 for rotatably supporting an extension end of the front swing regulating link 231 and an extending end of the rear swing regulating link 232. The rear swing regulating link 232 is provided with a rear swing regulating link 232,

The front swing regulating link 231 rocks with respect to the front swinging track frame 211 in the axial direction of the connecting pin 234 connecting the link 231 and the front swinging track frame 211. [ The rear swing regulating link 232 rocks with respect to the rear swinging track frame 212 in the axial direction of the connecting pin 35 connecting the link 232 and the rear swinging track frame 212. [ The stopper portion 233 is provided in the main track frame 210. The stopper portion 233 is slidable in an elongated hole 236 formed in the extending end portion of the forward swing regulating link 231 and in the elongated hole 237 formed in the extending end portion of the rearward swing regulating link 232 It is rotatable.

The stopper portion 233 moves the forward swing track frame 211 through the forward swing regulating link 231 as the swing angle of the forward swing track frame 211 with respect to the main track frame 210 increases, So that the front swinging track frame 211 is set as the swing limit. The stopper portion 233 moves the rear swinging track frame 212 through the rear swinging regulating link 232 as the swinging angle of the rear swinging track frame 212 with respect to the main track frame 210 increases. So that the rear swinging track frame 212 is set as the swing limit. The rocking motion restricting mechanism 230 prevents the forward swinging track frame 211 and the rear rocking track frame 212 from being excessively loosened or excessively tautened even when the front rocking track frame 211 and the rear rocking track frame 212 rock, And the rear swinging track frame (212).

The maximum swinging angle of the front swinging track frame 211 on the side where the front end side of the front swinging track frame 211 ascends from the neutral position with respect to the main track frame 210 is defined as U, The maximum swinging angle of the front swinging track frame 211 on the side where the front end side of the track frame 211 descends from the neutral position with respect to the main track frame 210 is defined as D. The rocking motion restricting mechanism 230 regulates the swinging angle of the forward swinging track frame 211 such that the maximum swinging angle U of the forward swinging track frame 211 becomes smaller than the maximum swinging angle D,

As shown in Figs. 23 and 24, the elevating operation mechanism 240 includes a pair of front and rear swing connection arms 241 and 242, a swing connection arm 242 on the rear side, A connecting link 243 connecting the rear end of the swing link 210 to the swing connection arm 241 and a swing support shaft 244 rotatably connecting the swing connection arm 241 on the front side, And a rotary support shaft 246 rotatably connecting the pivotal connection arm 242 on the rear side to the drive support frame portion 207 so as to be rotatable integrally with each other An interlocking lever 248 for interlocking the front operation arm 245 and the rear operation arm 247 with each other and a cylinder 247 provided for the rear operation arm 247 and the gas frame 7, And a hydraulic cylinder 249 connected to the bracket 249a The.

The elevating operation mechanism 240 is configured such that the rear operating arm 247 is pivoted by the hydraulic cylinder 249 so that the pivoting connection arm 242 on the rear side is rotated up and down And the rear end side of the main track frame 210 is raised and lowered via the connecting link 243 by the pivoting connecting arm 242. The front operation arm 245 is pivoted by the rear operation arm 247 via the interlocking lever 248 and the rotation support shaft 244 is rotated by the front operation arm 245 to rotate the front side And the front end side of the main track frame 210 is lifted and lowered by the pivoting connection arm 241 to move the traveling device 1 to the base frame 100, As shown in Fig.

That is, the traveling device 1 on the left side is operated by the elevating operation mechanism 240 to move the right traveling device 1 up and down with respect to the base frame 100 by the elevating operation mechanism 240, The height of the ground plane of the base frame 100 is changed in parallel.

The traveling device 1 on the left side is operated by the elevating operation mechanism 240 to lift and operate the traveling device 1 on the right side with respect to the base frame 100 by the elevating operation mechanism 240, By differentiating the lifting stroke of the device 1, the traveling gas is inclined in the left-right direction with respect to the ground, and the height of the ground surface on the right and left of the base frame 100 is changed. That is, the traveling vehicle is inclined to the left and right with respect to the ground.

As described above, the crawler traveling apparatus 1 includes a plurality of ground wheels 213, 214 arranged in the front-rear direction, a crawler drive wheel 215 positioned on the gas front side of the plurality of ground wheels, A crawler guide wheel (216) positioned at a rear side of the base body with respect to a plurality of ground wheels; and a crawler belt (218) wound around the crawler drive wheel, the plurality of ground wheels and the crawler guide wheel.

Among the conventional crawler traveling apparatuses, a plurality of ground wheels are divided into groups in a state in which two ground wheels belong to one ground wheel group, and two ground wheels of each ground wheel group are connected to the track frame. . Each balance arm is supported so as to be able to swing up and down in the track frame through a fulcrum shaft. Each of the balance arms supports the two ground wheels dispersed to the front end side and the rear end side of the fulcrum shaft (see, for example, JP 2001-260956 A (JP-A-2001-260956) 0012], [0015], see Figs. 1-4).

In the crawler traveling apparatus, it is possible to suppress the occurrence of the vibration due to the step of the traveling floor, and the above-described conventional technique is considered to be applied. However, even when the conventional technique described above is applied, there are the following problems.

For example, in a combine, you may enter a field of rice on top of it. When the step moves from a relatively high level to a low level and then moves, the front end side of the traveling device descends to a low level and is grounded as the weight center of gravity moves from a high place to a low place, And in a state of inclining downward going forward from a high position. At this time, due to the inclined posture of the traveling device, a relatively large number of ground wheels are lifted from the ground between the low point and the high point. Thereafter, when the rear end side of the traveling device deviates from the high place as the traveling progresses, the entire traveling device is grounded at a low place. As described above, the number of ground wheels that are in a floating state from the ground increases from the time when the front end side of the traveling apparatus is lowered to the time when the rear end side is lowered to ground and grounded. As a result, there was a tendency that the grounding shock when the traveling device came down to a low point throughout the entire area.

When the vehicle travels from a high place to a low place due to the backward movement, the traveling device is grounded at a low position from the rear end side, so that the inclined posture grounded by the traveling device at low and high positions becomes a posture of inclining downward, There was the same problem as.

On the other hand, the crawler traveling device (1) is characterized by the following configuration. In other words,

A plurality of ground wheels (213, 214) arranged in the front-rear direction, a crawler drive wheel (215) positioned on the gas front side of the plurality of ground wheels, and a crawler guide wheel (216), and a crawler belt (218) wound around the crawler drive wheel, the plurality of ground wheels and the crawler guide wheels,

A main track frame 210 supported on the base frame 100, a front swinging track frame 211 supported in the fore and aft direction on the main track frame and separately pivotable up and down in the direction of the pivot axis in the transverse direction of the vehicle, And a rear swinging track frame (212)

A part of the plurality of ground wheels 213 and 214 is dispersed and supported on the front swinging track frame 211 toward the front side of the swinging motion of the front swinging track frame 211 and the rear side of the vehicle,

The rest of the plurality of ground wheels 213 and 214 is dispersed and supported on the rear swinging track frame 212 toward the front side of the swinging motion of the rear swinging track frame 212 and the rear side of the vehicle,

And the crawler guide wheel 216 is supported on the rear swinging track frame 212.

When the crawler traveling device 1 advances and moves from a high place to a low place, the front end side of the crawler traveling device 1 descends to a low place and is grounded. The front swinging track frame 211 swings with respect to the main track frame 210 by the grounding reaction force acting on the front end side of the crawler traveling device 1, The grounding wheel 213 supported by the front swinging track frame 211 tends to be grounded at a low place or on the ground surface. The rear swinging track frame 212 swings with respect to the main track frame 210 by the grounding reaction force acting on the rear end side of the crawler traveling apparatus 1, So that the ground wheel 214 supported by the rear swinging track frame 212 can easily be grounded at a low point or on the ground surface.

On the other hand, when the crawler traveling device 1 moves from a high position to a low position, when the crawler traveling device 1 is in a tilted posture that is grounded at low and high positions, the rear swinging track frame 212, 211 are located on the upper side and are relatively positioned in the vertical direction of the front swinging track frame 211 and the rear swinging track frame 212, And the ground wheels 213 and 214 supported by the front swinging track frame 211 are easily grounded on the lower surface or the front surface.

When the front rocking track frame 211 or the rear rocking track frame 212 rocks, the main track frames 211 and 212 of the ground wheels 213 and 214 swinging together with the front rocking track frame 211 or the rear rocking track frame 212 210, an operation force for increasing the tension of the crawler belt 218 may be generated. When the rear swinging track frame 212 swings, the crawler guide wheel 216 swings together with the rear swinging track frame 212 to move in a direction to relax the tension of the crawler belt 218, so that the tension of the crawler belt 218 The increase may be suppressed.

Therefore, even when moving by either the forward movement or the backward movement, the ground wheels 213 and 214 are grounded to a low or a flat surface and the crawler belts The crawler belts 218 can be moved downward while suppressing the increase in tension of the crawler belts 218, so that a grounding shock when the entire crawler traveling apparatus 1 is lowered is less likely to occur, It is possible to obtain a working machine excellent in durability because deterioration due to stress is hard to occur.

In the crawler traveling device 1, the main track frame 210 is supported on the base frame so as to be movable up and down.

According to this structure, the height of the ground plane of the base frame 100 can be changed by moving the main track frame 210 up and down relative to the base frame 100. Therefore, even in the case of the soft paper, the height of the ground surface of the base frame 100 can be adjusted to a high level irrespective of the settlement of the crawler belt 218 on the ground, so that the work can be advantageously performed have.

The crawler traveling apparatus 1 further includes a front swing regulating link 231 pivotally extending from the rear end of the front swing track frame 211 and a front swing regulating link 231 swingably from the front end of the rear swing track frame 212 The rear end portion of the forward swing regulating link 231 and the rear swing regulating link 232 to regulate the rocking of the forward swinging track frame 211 and the rear swinging track frame 212 And a stopper portion 233 for rotatably supporting an extending end portion of the stopper portion 233.

According to this configuration, as the swinging angle of the front swinging track frame 211 with respect to the main track frame 210 increases, the front swinging track frame 211 moves forward through the front swinging regulating link 231, And the front swinging track frame 211 becomes the swing limit. The rear swinging track frame 212 is moved by the stopper portion 233 through the rear swinging regulating link 232 as the swinging angle of the rear swinging track frame 212 with respect to the main track frame 210 increases, So that the rear swinging track frame 212 becomes the swing limit.

The front swinging movement link 231 and the rear swinging regulating link 232 are provided on the same stopper portion 233 so as not to overstretch the swing motion of the front swinging track frame 211 and the rear swinging track frame 212 (The shaking motion restricting mechanism 230) supported by the rear swinging track frame 212 and the swinging movement of the front swinging track frame 211 and the rear swinging track frame 212 by the regulating mechanism It can be obtained by a simple structure that can prevent problems such as loosening and becoming too tight.

The crawler traveling device 1 further includes a tension spring 227 for pushing the crawler guide wheel 216 against the crawler belt 218 and pressing the crawler guide wheel 216.

According to this configuration, even if the tension of the crawler belt 218 is increased by the movement of the ground wheels due to the swinging motion of the front swinging track frame 211 or the rear swinging track frame 212, 227 are elastically deformed so that the crawler guide wheel 216 moves backward to suppress the increase in tension of the crawler belt 218.

Therefore, the increase in tension of the crawler belt 218 due to the movement of the ground wheel relative to the main track frame 210 can be suppressed by the integral swinging motion of the crawler guide wheel 216 with the rear swinging track frame 212 In addition, the crawler belt 218 can be restrained by the retracting movement of the crawler guide wheel 216, and the durability of the crawler belt 218 can be increased so that deterioration due to excessive slackening of the crawler belt 218 is less likely to occur.

In the crawler traveling device 1, the center of gravity G of the body is located on a vertical line passing between the front swinging track frame 211 and the rear swinging track frame 212 as viewed from the side.

According to this configuration, even when the movement from the high position to the low position is performed by either the forward movement or the backward movement, it is possible to perform the operation while making it difficult to generate the grounding impact.

In other words, even if the movement from the high place to the low place is performed by the forward movement or the backward movement is performed, the movement from the high center of gravity G to the low place, The rear end side is lowered to ground, and the traveling device 1 is grounded in a tilted state at a low place and a high place. Since the center of gravity G of the vehicle is located on the vertical line passing between the front swinging track frame 211 and the rear swinging track frame 212, when the movement from the high place to the low place is performed by forward movement, The front swinging track frame 211 swings with respect to the base frame 100 in an early stage as the apparatus 1 is switched to a grounded state in an inclined posture in which the apparatus 1 descends downward and upwards.

On the other hand, when the traveling device 1 is moved from the high to the low position by the backward movement, the traveling device 1 is switched to the grounded state in the inclined posture in which the backward descent goes down from the low point to the high point, The frame 212 rocks with respect to the base frame 100.

As a result, the ground wheels (213, 214) supported by the front rocking track frame (211) and the rear rocking track frame (212) can be grounded early , It can be lowered while suppressing the generation of a grounding shock when it is lowered.

[Other Embodiments]

(1) In the configurations shown in Figs. 3 and 7, the right and left side portions and the other side portions of the mission case 10 may be arranged so as to be horizontally reversed as follows.

In this case, a stepped concave portion 10a is formed on the outer side of the upper portion of the left side portion 10L of the mission case 10 so that the mission case 10 (the right and left portions 10R and 10L) The concave portion 10a enters in the vicinity of the fitting portion 10b of the housing 10a (slightly to the right of the paper). The hydrostatic stepless transmission 11 is disposed so as to enter the transmission case 10 (the concave portion 10a of the left portion 10L) so that the port block 11a of the hydrostatic stepless transmission 11 is engaged with the transmission case 11 The input shaft 11b and the input shaft 12 and the support member 12 of the hydrostatic stepless transmission 11 are extended to the right side by being connected to the concave portion 10a of the input shaft 10 (left portion 10L).

(Right side and left side portions 10R and 10L) of the mission case 10 (the left side portion 10L) The input shaft 22 is supported on the right side portion 10R of the transmission case 10 and the right side portion of the transmission gears 27 and 29 (in the vicinity of the inner surface of the wall portion of the right side portion 10R of the mission case 10) 30, and 31 are fixed. The right and left output gears 32R and 32L are externally inserted into the transmission shaft 29 so as to be relatively rotatable in the left side portion (left side portion 10L of the transmission case 10) of the transmission shaft 29, The left side fitting portion 33L is integrally rotatably and slidably inserted in the left side portion 10L of the transmission case 10 by the spline structure of the left side fitting portions 33R and 33L Disposed in the vicinity of the inner surface of the wall portion. And a reverse clutch 53 is provided on the left side of the transmission shaft 44. The reverse rotation clutch 46 is provided on the right side of the transmission shaft 44,

(2) In the above-described embodiment, the transmission case 10 (right and left portions 10R and 10L) and the hydrostatic type stepless transmission 11 are configured separately, but the transmission case 10 (10R, 10L) and the hydrostatic stepless transmission (11) may be integrally formed into a single casing.

The output shaft 11c and the input shaft 22 of the hydrostatic stepless drive unit 11 may be configured not by separate but by one transmission shaft (not shown). The power of the output shaft 11c of the hydrostatic stepless type stepless transmission 11 may be transmitted to the input shaft 22 through a transmission gear (not shown).

The continuously variable transmission device for running (peripherals) is not necessarily limited to the hydrostatic stepless transmission 8 shown in the drawing. For example, a belt-type continuously variable transmission or a continuously variable transmission in which a planetary gear is combined with a hydrostatic continuously variable transmission may be used.

(3) In Fig. 7, the brake 50 may be abolished, and the reverse clutch 53 may be provided with the function of the brake 50. Fig.

In this case, the power from the right side (left side) side clutch 34 (right side (left side) engagement portion 33R (33L)) and the power from the reverse clutch 53 (The right side (left side) engagement portion 33R (33L)) of the right side (left side) is transmitted from the right side (left side) clutch 34 The operating force of the reverse clutch 53 is set so that the power from the reverse clutch 53 is balanced and the output gear 32L (32R) on the left side (right side) is stopped.

(4) In Fig. 2, the operation section 5 may be provided on the left side of the left side of the mission case 10, and the support frame 2 may be provided on the right side of the mission case 10 . The oil pressure unit 57 is connected to the outer surface of the horizontal side portion on the right side of the support case 2 side of the transmission case 10 (right side portion 10R).

The hydraulic unit 57 is not located on the outer side of the lateral sides of the mission case 10 (the right and left portions 10R and 10L) but the inside of the mission case 10 (right and left portions 10R and 10L) And the lid for opening and closing the maintenance unit of the hydraulic unit 57 is provided on the outer surface of the lateral side of the mission case 10 (right and left portions 10R and 10L) .

(5) The shift member 28 of the auxiliary transmission device (gear type auxiliary transmission mechanism A) may be configured to be slid by a hydraulic cylinder (equivalent to a hydraulic mechanism for a transmission) or The auxiliary speed change device may be constituted by a plurality of hydraulic clutches (corresponding to a hydraulic mechanism for running transmission).

The hydraulic clutch is supported by the transmission shaft 27 so that the right or left end of the transmission shaft 27 is inserted into the hydraulic unit 57 and the transmission shaft 27 is supported by the transmission shaft 27. [ And a flow passage is provided in the inside of the transmission shaft 27 across the hydraulic clutch.

(6) The hydraulic motor 8C constituting the hydrostatic stepless speed changer 8 is configured such that the movable swash plate 8D is fixed at a predetermined inclined angle and the displacement is controlled only by the hydraulic pump 8B, You can. On the other hand, also in the hydraulic motor 8C, the movable swash plate 8D can be adjusted steplessly.

(7) A method of driving the movable swash plate 8D of the hydraulic pump 8B by an electric actuator such as an electric motor is employed, and the operation amount of the peripheral speed lever 61 as a peripheral speed control valve is controlled by a sensor such as a potentiometer And the electric actuator is controlled based on the detected value.

(8) The double-acting cylinder 8d is used to drive and control the hydraulic pump 8B, and the orifice 8h is provided in the supply path in order to make the operating speed constant, but it is not necessary to install the orifice 8h.

1: Crawler traveling device
5-1: Side control tower
10: Mission Case
10a:
11: continuously variable transmission
22: input shaft
30, 31: Electric gear
34: Side clutch

Claims (7)

And a cutout portion for taking the cutting grooves and transporting the cut grooves backward from the lateral side of the operation portion,
A continuously variable transmission according to any one of claims 1 to 3, further comprising a peripheral speed device capable of continuously variable transmission, the hydraulic speed type comprising a hydraulic pump capable of continuously changing the capacity and a hydraulic motor driven by hydraulic oil from the hydraulic pump, Wherein the mechanism is a traveling change gear mechanism of a combine built in a transmission case disposed at the left and right middle portions of the front face of the vehicle,
Wherein a peripheral speed operating port for changing and controlling the hydraulic pump is disposed in the operation control space and a sub speed change operation port for switching and controlling the gear type speed change mechanism is disposed outside the operation control space,
Wherein the auxiliary speed change operating element is located upwardly from the mission case between a transverse side portion of the operation portion facing the preload portion and a transverse side portion of the preload portion facing the operation portion. The traveling change transmission structure of a combine according to claim 1, wherein the capacity of the hydraulic motor is variable. 2. The air conditioner according to claim 1, wherein a side manipulation tower is disposed on the inboard side of the driving seat of the operating seat,
And the transmission case is disposed below the side control tower. The gas turbine engine as claimed in claim 3, wherein a recessed portion is formed on the lower portion of the side manipulation tower of the operation portion,
The mission case is disposed in the recessed portion,
Wherein the transmission case is formed in a shape bent in the upper and lower middle portions so that a side portion of the transmission case in the auxiliary transmission operating member is located in the recessed portion. The transmission according to claim 4, characterized in that the auxiliary speed change manipulation opening is formed by a lower portion connected to a lower end of the manipulation arm connected to the gear portion transmission mechanism and extending upwardly and a lower portion extending upwardly from the extended projection end of the lower portion, And an upper side portion extending upwardly from the extending projecting end portion of the transverse portion and having a leading end operating portion provided at an upper end portion of the transverse direction portion. 6. The air conditioner according to any one of claims 1 to 5, wherein the side control tower is disposed on the inside of the gas transverse side of the driver's seat in the operation section,
The peripheral speed control means is disposed on the side control table,
And the front operating portion of the auxiliary speed change operating member is disposed at a lower arrangement height than the grip portion of the peripheral speed operating member, constituting the auxiliary speed change operating member. The traveling change transmission structure of a combine according to claim 2, wherein a shift switch is provided on a grip portion of the peripheral speed operating member and the swash plate of the hydraulic motor is operated to a high speed position and a low speed position in accordance with an operation signal of the shift switch.

Images