JP3305869B2 - Work vehicle parking brake device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a parking brake device for a working vehicle such as a combine.

[0002]

2. Description of the Related Art Conventionally, in a working vehicle such as a combine which travels mainly by a left and right crawler traveling body, the left and right crawlers are steered by giving a rotational speed difference to the left and right crawlers. The method of turning with normal rotation is pivot turn, the method of turning with right and left rotation in opposite directions is super pivot turn (or spin turn), and both left and right are rotated in the same direction, but one is slower than the other. The method of rotating at high speed is referred to as gentle turning (or soft turning), and Japanese Patent Application Laid-Open Nos.
What is shown in -114578 is known. As the hydraulic or electric operating devices for performing these steering operations, those disclosed in JP-A-4-321473, JP-A-38275 and JP-A-4-59577 are known.

[0003]

However, in the above-mentioned conventional apparatus, since the friction type brake and clutch are turned on and off by the hydraulic cylinder, the parking brake for parking the body is either of the above-mentioned brake or clutch. Is a mechanism that can be turned on and off by a driving force other than hydraulic pressure by manual operation,
A special parking brake was provided separately. Therefore, if the parking brake fails, there is an inconvenience that there is no alternative brake, and there is a disadvantage that at least one or more preliminary parking brakes are required to solve this.

[0004]

An apparatus according to the present invention for solving the above-mentioned problems transmits a rotational driving force to left and right axles 29, 30 via left and right side clutch gears 23, 24. An intermediate shaft 41, friction-type left and right selection clutches 46 and 47 which are mounted separately to the left and right with respect to the intermediate shaft 41 and which transmit the rotation of the intermediate shaft 41 to the side clutch gears 23 and 24 so as to be freely engaged and disengaged; A relay shaft 16 for transmitting an input-side rotational drive to the intermediate shaft 41;
Clutch 6 that switches the input of the relay shaft 16 to the intermediate shaft 41 between slow forward rotation drive and stop braking.
And a slow-speed switching device 61 comprising a brake 4 and a brake 66, and at least one of the left and right selection clutches 46 and 47 is arbitrarily and manually operable to be engaged. It is characterized in that the brake 66 is always turned on by a spring load and is normally turned on by a hydraulic cylinder 68 by a switching operation.

[0005]

When the parking brake is applied by the present invention, the side clutch gears 23 and 24 are held in the forward direction with respect to the center gear 20 in any case, and the selection clutch 46 is engaged by a mechanical device other than the hydraulic pressure. The first method is a method of connecting the reverse transmission system to the intermediate shaft 41 to form a loop of the forward and reverse transmission systems and locking the axles 29 and 30.

In a second method, the brake 66 of the slow speed switching device 61 is connected to the intermediate shaft 41 in the on state, and the relay shaft 16 locked by the brake 66 and the left and right steering shafts 2 are connected.
In this method, a loop is formed between the slow transmission system and the forward transmission system between the transmission shafts 5 and 26, and the left and right axles 29 and 30 are locked.

The same operation as described above is sufficient for the case where the clutch 64 of the slow speed switching device 61 is always in the on state. However, in this case, the loop of the transmission system includes the shaft on the drive input side and the left and right steering shafts 25, 26, each of which is a loop in the forward direction, the rotation in the loop is locked by the difference in gear ratio between the forward transmission system and the slow forward transmission system, and the left and right axles 29,
30 is to be locked.

[0008]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment will be described below in detail with reference to the drawings. FIG. 1 is a sectional view showing an internal mechanism of a traveling power transmission device (transmission) 1 of a mobile agricultural machine having a crawler traveling device such as a combine.

An input shaft 5 is supported in the case 3, and an input pulley 6 is fixed to a protruding portion of the input shaft 5. The other end of the input shaft 5 extends into a hydraulic continuously variable transmission 7 (HST) mounted outside the case 3, and the rotation of the input shaft 5 transmitted via the input pulley 6 is applied to the hydraulic continuously variable transmission 7. 7
And transmitted to the working unit input shaft 8. The hydraulic continuously variable transmission 7 is operated by a main transmission lever to perform a speed change operation so that the speed can be continuously changed.

A gear 9 is fixed to a shaft 8 supported in the case 3, and a driving force is transmitted to a gear shaft 12 via a gear 11 meshed with the gear 9. The gear shaft 12 has a sub-transmission gear (dog gear) 13a that rotates integrally with the gear shaft 12.
However, gears 13b and 13c, which are selectively slidable in the axial direction and are selectively meshed with dog gears 13a on both left and right sides thereof, are attached so as to be freely rotatable. Gears 13a-1
3c is a plurality of transmission gears 15a to 15c having different diameters fixed to the input drive shaft 14 for the steering system also serving as the transmission shaft.
Meshes with

The gears 15a, 15b of the drive shaft 14
The gear 15a also serves as an output gear together with an input gear, and the smallest-diameter gear 15a meshing with the dog gear 13a meshes with a center gear 20, which will be described later, to transmit forward rotation power.
5b meshes with an input gear 17 of a relay shaft 16 to be described later to transmit slow forward rotation power. Further, the drive shaft 14 is fitted with a reverse rotation power transmission gear 15d having a diameter at an intermediate position between the two gears 15a and 15b, and meshes with a gear 18 of an intermediate shaft 41 described later.

Next, a description will be given of a forward rotation transmission system. An inner tooth is formed on both right and left sides of a center gear 20 which is integrally supported by a center shaft 19, and a side clutch gear 2 is provided.
3 and 24 are engaged with each other in a detachable manner. The side clutch gears 23 and 24 are attached to the left and right steering shafts 25 and 26, which are coaxially mounted on the steering shaft 19, so as to be integrally rotatable and slidable. By sliding, engagement with the internal teeth of the center gear 20 is disengaged.

Numerals 54 and 56 denote side clutches which rotate left and right to disengage the side clutch gears 23 and 24 from right and left. Left and right side clutch gear 2
Output gears 27 and 28 provided on the left and right axles 29 and 30 mesh with the gears 3 and 24, respectively. Therefore, the driving force of the center gear 20 is transmitted to the axles 29, 30 when the left and right side clutch gears 23, 24 are engaged with the internal teeth.
The axles 29 and 30 extend in the left-right direction from the case 3, and a sprocket 31 is attached to a tip thereof, and a crawler belt 32 is wound around the sprocket 31.

According to the above-described forward rotation transmission system, when the side clutch gears 23 and 24 are in the ON state and the friction type selection clutches 46 and 47 at both ends of the intermediate shaft 41 are in the OFF state, the drive shaft 14 and the gear 15a, center gear 20, side clutch gears 23, 24, output gears 27, 28, axles 29, 3
Power is transmitted in the order of 0, and the aircraft goes straight forward.

Next, the reverse (reverse) transmission system will be described. The left and right steering shafts 25 and 26 reach the left and right outer sides of the case 3, and reverse transmission gears 35 and 36 are fitted and fixed to the protruding ends, respectively. The left and right reverse transmission gears 35, 36
The support parts 33 and 34 made of bare link bearings
Are provided, and the steering shafts 25 and 26 and the center shaft 19 are provided.
At the same time and on the same axis.

On the other hand, a free rotation gear 42 rotatably supported by an intermediate shaft 41 meshes with the gear 15d of the drive shaft 14. Similarly, a free rotation gear 45 is fitted to the reverse rotation shaft 41, and a switching (dog) clutch 43 is supported between both gears 42 and 44 as a forward / reverse switching device (means). It is provided slidably in the axial direction so as to rotate integrally with the reverse rotation shaft 41 and to engage and disengage with the pawls on the side surfaces of the gears 43 and 44.

When the switching clutch 43 is engaged with the clutch pawl of the free rotation gear 44, the power of the drive shaft 14 is transmitted to the intermediate shaft 41 via the free rotation gear 44,
When the switching clutch 43 is engaged with the free rotation gear 42, the state in which the intermediate shaft 41 does not rotate is maintained.

Both ends of the intermediate shaft 41 reach the outside of the case 3, and input ends of friction type selection clutches 46 and 47 are attached to the both ends. In the apparatus of this embodiment, the selection clutches 46 and 47 are friction type multi-plate clutches which are always in a disengaged state by a spring. Clutch cases 50 and 51 are formed outside the selection clutches 46 and 47, respectively. The clutches 46, 47 and the reverse transmission gears 35, 36 are covered. Further, in the clutch cases 50 and 51, hydraulic cylinders 46a and 47a are provided for pressing the disc in the clutch from the outside of the selection clutches 46 and 47 to simultaneously engage or disengage the clutch left or right or separately.

On the output side of the selection clutches 46 and 47, gears 48 and 49 that rotate freely on the intermediate shaft 41 are formed, and the above-mentioned reverse rotation transmission gears 35 and 36 are meshed with each other. A clutch lever 52 is provided on the outer side of the clutch case 50 so as to be swingable, and the swing operation of the clutch lever 52 causes the left-side selection clutch 46 to be turned on and off via an internal cam. Functions as a parking brake.

According to the above reverse transmission system, the switching clutch 43 is engaged with the free rotation gear 42, the side clutch gears 23 and 24 are disengaged from the center gear 20, and the selection clutches 46 and 47 are engaged. In this state, the drive shaft 14, the free rotation gear 42, the switching clutch 43, the intermediate shaft 41, the selection clutches 46 and 47, the gears 48 and 49, the reverse transmission gears 35 and 36, the steering shafts 25 and 26, and the side clutch gear 23, 24, output gears 27, 28, axles 29, 3
Power is transmitted in the order of 0, and the aircraft goes straight backward.

Next, the slow transmission system will be described. The gear 15b of the drive shaft 14 and the gear 17 on the relay shaft 16 are always meshed with each other, but the gear 17 is freely rotating with respect to the relay shaft 16. Is connected to the slow speed switching device 61 via a clutch, and serves as an input gear for the slow speed switching device 61.

That is, the slow speed switching device 61 is mounted on the right end of the relay shaft 16 in the transmission 1,
Movable disk holder 62 fitted and fixed to the side
And a drum-shaped fixed disk holder 63 fixed to the clutch case 51 side. A multi-plate friction clutch that separates and separates the inner periphery of the cylindrical inner end of the movable disc holder 62 and the outer periphery of the outer end of the gear 17 to turn the rotation of the gear 17 on and off the movable disc holder 62 and the shaft 16. 64 are formed.

On the other hand, a multi-plate friction type brake 66 is formed between the inner periphery of the outer end of the movable disk holder 62 and the outer periphery of the inner end of the fixed disk holder 63. A biasing portion 67 made of a disc spring that constantly biases the clutch 64 in the off direction and the brake 66 in the on direction is interposed.

A hydraulic cylinder 68 is formed in the clutch case 51 around the outer end of the fixed disk holder 63, and a ring-shaped piston 69 is fitted between the cylinder 68 and the fixed disk holder 63. And
By pressing the cylindrical pusher 71 fitted to the outer end of the movable disc holder 62 with the piston 69 by hydraulic pressure, the urging portion 67 is compressed, the brake 66 is turned off, and the clutch 64 is turned on. Is done. As a result, the relay shaft 16 is connected to the gears 15 b and 17 and the slow speed switching device 6.
1 is rotatably driven so as to be freely turned on and off.

The intermediate shaft 4 is connected to the relay shaft 16.
A small-diameter gear 18 that is always meshed with the first free rotation gear 44 is fixedly supported, and rotates the drive shaft 14 by using the slow switching device 61, the gears 18 and 44, and the switching clutch 43. Through this, a mechanism for decelerating to the intermediate shaft 41 and performing slow forward rotation is provided.

The slow speed switching device 61 includes a brake 66
Is always in the on state, and the clutch 64 is always in the off state. However, the clutch 64 is always on, the brake 66 is always off, and the hydraulic cylinder 68 is turned on. It is also possible to use the clutch 64 as a disengagement mechanism. The numbers in circles in FIG. 2 indicate the number of teeth of each gear or wheel to which the numbers are close.

Next, the operation of each part when the steering operation is performed based on the traveling power transmission device 1 will be described. The forward / backward movement is as described above. When the parking brake is applied, in any case, the side clutch gears 23 and 24 mesh with the center gear 20 and are held in the forward rotation direction.
The selection clutch 46 is engaged by the lever 52. In the first method, the switching clutch 43 is engaged with the free rotation gear 42 to connect the reverse rotation transmission system, and the selection clutch 46 is engaged by the lever 52. In this way, a forward and reverse rotation transmission system loop is formed between the drive shaft 14 and the steering shafts 25 and 26, and the left and right output gears 27 and 28 and the axles 29 and 30 are locked.

In this case, it is desirable that the transmission ratio of the forward rotation transmission system and the reverse rotation transmission system be the same, and the selection clutch 46 can be used as a parking brake, so that a special parking brake structure is not required. As a result, simplification of the mechanism, weight reduction, cost reduction, and the like can be achieved.

The second method is to engage the switching clutch 43 with the free rotation gear 44 while the brake 66 of the slow speed switching device 61 is in the on state (always on), so that the brake 6
6, the relay shaft 16 and the left and right steering shafts 25,
26, a loop is formed between the slow transmission system and the forward transmission system to lock the left and right axles 29, 30.

The same operation as described above is sufficient for the case where the clutch 64 of the slow speed switching device 61 is always in the engaged state, but the transmission system loop in this case is composed of the drive shaft 12 and the left and right steering shafts 2.
5 and 26, each of which is a loop in the forward rotation direction, but rotation in the loop is locked by a difference in gear ratio between the forward rotation transmission system and the slow forward transmission system, and the left and right axles 29, 3
0 is to be locked.

Next, a description will be given of a case where the left crawler 32 is stopped and the other crawler is advanced. Is turned off, the brake 66 of the slow speed switching device 61 is turned on, and the relay shaft 1 is turned on.
6 and lock the switching clutch 43 to the free rotation gear 44.
When the intermediate clutch 41 is locked by engaging the left side clutch 41 with the hydraulic cylinder 46a, the right axle 30 is rotated forward, the left axle 29 is locked, and the body is shifted to the left. Turn. Similarly, when only the right side clutch gear 24 is turned off and only the right selection clutch 47 is turned on, the vehicle turns right.

A description will be given of a spin turn in which one crawler is rotated forward and the other crawler is rotated in the case where a left spin turn is performed. First, only the left side clutch gear 23 is moved from the forward state. Is disengaged with respect to the center gear 20, the switching clutch 23 is engaged with the free rotation gear 42, and the selection clutch 46 is engaged with the hydraulic cylinder 46a, and the gears 15d and 42, the intermediate shaft 41, the selection clutch 46, 48, 35, steering axis 2
5, the left axle 29 reversely rotates via the gears 23 and 27,
A super turn is performed. In the case of a right turn, the right side clutch 24 and the right selection clutch 4 are replaced with the on-operation of the left side clutch gear 23 and the left selection clutch 46.
7 may be operated.

The case of a gentle turn (soft turn) will be described with respect to a gentle left turn. First, the side clutch gear 23 is disengaged from the center gear 20 from the forward state, and the selected clutch 43 is shifted to the free rotation gear 44 side. With the on-operation, the hydraulic cylinder 68 is turned on and the brake 6
6 is disengaged, the clutch 64 is engaged, the slow transmission system is operated, and the intermediate shaft 41 is slowly rotated forward.

Then, by turning on the hydraulic cylinder 46a and turning on the left selection clutch 46, the left steering shaft 25 is slowly rotated forward, the right axle 30 is rotated at normal speed, and the left axle 29 is rotated. Is slowly rotated forward at a low speed, so that the aircraft slowly turns to the left on a gentle curve. At this time, the hydraulic cylinder 68 is operated in accordance with the operation amount of the steering lever 91 by operating a variable relief valve 88 described later, and the slow forward rotation speed can be continuously adjusted by adjusting the friction amount of the clutch 64. The curve can also be adjusted steplessly.

On the other hand, when making a gentle right turn, the right side clutch gear 24 is disengaged instead of the left side clutch gear 23 and a right selection clutch is used instead of the left selection clutch 46, as compared with the gentle left turn. The clutch 47 may be engaged. It is also possible to apply braking to the left and right axles 29 or 30 by connecting the intermediate shaft 41 to the reverse rotation transmission system and setting the friction type selection clutch 46 or 47 to a half-clutch state.

FIG. 4 is a diagram showing a hydraulic device for operating the above-described transmission device and its piping. A main piping 71 for supplying hydraulic pressure has left and right steering circuits 73a and 73b via left and right steering switching valves 72.
And an auger circuit 76 via a paddy discharging auger (not shown) switching valve 74 and a preprocessing circuit 78 via a preprocessing unit (not shown) elevating switching valve 77 are connected in parallel. Numerals 79 and 81 denote an auger elevating cylinder and a pre-processing unit elevating (lift) cylinder, respectively. The left and right steering circuits 73a and 73b, the auger circuit 76, and the pre-processing unit circuit are respectively switched via switching valves 74 and 77. Drain circuit 82
The main pipe 71 and the drain circuit 82 are connected via a relief valve 83 and are connected to a drain pipe 85.

The left and right steering circuits 73a and 73b include:
The clutch cylinders 84a and 84b outside the transmission for turning on and off the left and right side clutches 54 and 56 are respectively branched and connected, and the left and right switching clutch cylinders 46a and 46b are connected and branched via throttle valves 86a and 86b. , 56 perform a preferential operation, and then the left and right selection clutches 46, 47 are engaged against the spring.
73b is connected in parallel to a slow switching circuit 87, and a downstream side of the slow switching circuit 87 is connected to a variable relief valve 88.
Is connected to the drain circuit 82 via the. Further, the slow speed switching circuit 87 is connected to a slow speed switching valve 89 for turning on and off the slow speed switching cylinder 68 against the urging portion 67.

With the above arrangement, the variable relief valve 88 is adjusted by the second-stage swing of the steering lever 91, which will be described later, to adjust the operation amounts of the left and right selection clutch cylinders 46a and 47a, thereby reducing the frictional force of the friction plate. Gear 35,3
6, the rotational speeds of the axles 29 and 30 can be arbitrarily adjusted, and the operation of the slow switching cylinder 68 can be similarly changed.

FIGS. 5A and 5B show the mounting and operating state of the multi-type steering lever 91 which can swing back and forth and right and left, and is erected on the driver's seat panel in front of the driver's seat of the body. . A lever 91 provided with a head 92 on the upper side has a mounting portion 94 provided with a mounting bracket at the lower end, and has a left and right rotation fulcrum (axis) 93 and a left and right rotation fulcrum 95 on the driver's seat panel (not shown) side. It is pivotally supported.

When the lever 91 is swung right and left, a rotary switch 96 mounted in a mounting portion 94 which rotates with the lever rotation by the first rotation is operated, and the switching valve 72 is switched. The left and right side clutch cylinders 84a and 84b are actuated, and the lever 91 is swung in the second stage to squeeze the variable relief valve 88 and the left and right selected clutch cylinders 46a and 47a are turned on. With the side clutch 54 or 56 on one side disengaged, the selection clutch 46 or 47 is engaged.

When the push button switch 97 on the lever head 92 is depressed while the lever 91 is in the two-stage rocking state, or when the lever 91 is previously pressed and enters the two-stage rocking state. , The slow-speed switching valve 89 is switched by an electric means (solenoid) so that the slow-speed switching cylinder 68
Is turned on, the brake 66 of the slow speed switching device is turned off, and then the clutch 64 is turned on.

Further, the steering lever 91 is moved to a pivot 93
Is pivoted back and forth around the center, the rotary switch 98 provided on the mounting portion 94 is turned on and off, the pre-processing portion switching valve 77 is switched, and the pre-processing portion cylinder 81 is used to lower or raise the pre-processing portion. .

FIG. 6 shows a main part of an electric control circuit for operating the steering transmission. The entire steering control is performed by a microcomputer unit 99, which is connected to a power supply circuit 100 and operates. However, the power supply circuit 100 has the steering lever 91 described above via the microcomputer unit 99.
Push button switch 97, rotary switches 96, 9
8, switch 7 for left and right side clutch switching valve 72
2a, 72b, a switch 89a for operating a slow switching valve, a switch 77a, 77b for switching a pre-processing section switching valve 77
And the like are connected, and the microcomputer controls turning on and off of these switches to perform drive control of the hydraulic device shown in FIG.

FIG. 7 shows another example of the steering transmission. The reference numerals in FIG. 7 correspond to those in FIG. 1 and the components and the like. In this example, the relay shaft 16 in FIG.
Instead of omitting the shaft products such as the gears 17 and 18 of the relay shaft 16 and the switching device 61, one free rotation gear 44 meshes with the center gear 20.

As a result, for example, the left side clutch gear 23 is disengaged while the right side clutch gear 24 is meshed in the forward rotation direction, and the forward / reverse switching clutch 43 is meshed with the free rotation gear 44, and the left selection clutch 46 is engaged. O
When the N operation is performed, the forward rotation force reduced by the free rotation gear 44 is transmitted to the left axle 29, and the left turning can be slowly performed. At this time, the transmission friction of the left selection clutch 46 is adjusted, thereby gradually turning. The curvature of itself can be adjusted.

In the case of a left turn (spin turn), the switching clutch 22 is engaged with the free rotation gear 42 for reverse rotation transmission and the left selection clutch 46 is turned on as in the case of FIG. Do it at least.

In the case of further turning to the left side, the left selection clutch 46 is half-clutched and used as a brake for the left axle 29 while the intermediate shaft 41 is rotated in the same manner as described above, and the left axle 29 is stopped and the right axle is stopped. What is necessary is just to turn 30 forward. When turning right, the above left and right operations are performed in reverse. Although the hydraulic and electric devices for operation in this example can be generally those shown in FIGS. 4 and 5, the operation system relating to the slow speed switching device 61 and various devices for it are not required.

[0048]

The present invention is configured as described above.
Two types of parking brake functions can be exhibited by using the selection clutch of the intermediate shaft and the slow switching device of the relay shaft.
In addition to the advantage that a special parking brake is not required, it is possible to adopt a configuration in which any one of the parking brakes is always activated at the time of parking, and in this case, the parking brake on a slope or the like is reliably applied.

[Brief description of the drawings]

FIG. 1 is an overall sectional view of a steering transmission.

FIG. 2 is an enlarged sectional view of a slow speed switching device.

FIG. 3 is an overall schematic view of a steering transmission.

FIG. 4 is a hydraulic circuit diagram for operating the steering transmission.

FIGS. 5A and 5B are a rear view and a side view of an operation lever portion of the steering transmission.

FIG. 6 is an electric circuit diagram for operating the device.

FIG. 7 is an overall sectional view showing another example of the steering transmission.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Transmission 14 Drive shaft 16 Relay shaft 20 Center gear 23, 24 Side clutch gear 25, 26 Steering shaft 29, 30 Axle 41 Intermediate shaft 43 Switching device (clutch) 46, 47 Selection clutch 54, 56 Side clutch 61 Slow switching Apparatus 64 Friction clutch 66 Friction brake 68 Cylinder 88 Variable relief valve 89 Slow switching valve 91 Steering lever 97 Switching switch

Continuation of the front page (56) References JP-A-57-177446 (JP, A) JP-A-1-101272 (JP, A) JP-A-1-114578 (JP, A) JP-A-4-38275 (JP) JP-A-4-151380 (JP, A) JP-A-4-183684 (JP, A) JP-A-4-321473 (JP, A) JP-A-5-65759 (JP, U) (58) Field surveyed (Int. Cl. ⁷ , DB name) B62D 11/00 B60T 1/00

Claims (1)

(57) [Claims] The left and right side clutch gears (23),
An intermediate shaft (41) for transmitting rotational driving force to the left and right axles (29) and (30) via the (24), and the intermediate shaft (41);
Left and right friction clutches (46), (4) that transmit the rotation of the intermediate shaft (41) to the side clutch gears (23), (24) so as to be able to freely turn on and off.
7), a relay shaft (16) for transmitting an input-side rotational drive to the intermediate shaft (41), and a relay shaft (16) mounted on the relay shaft (16) with respect to the intermediate shaft (41). A friction switching device (61) comprising a friction type clutch (64) and a brake (66) for switching the input between slow forward driving and stop braking is provided, and the left and right selection clutches (4) are provided.
At least one of 6) and (47) is configured to be arbitrarily and manually operable to be engaged, and the clutch (64) or the brake (66) of the slow speed switching device (61) is always engaged by a spring load, and is switched. A parking brake device for a working vehicle configured to be in a normal state by a hydraulic cylinder (68) when operated.