JPH10271906A - Operation structure of hst-type transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent a machine body to start rotation at the site by a wrong operation when a sub-transmission is in the neutral position, in an apparatus having the sub-transmission arranged between an HST-type infinitely variable transmission structure for traveling and a differential structure for right and left wheels or crawler. SOLUTION: This operation structure of an HST-type transmission device having an HST-type infinitely variable structure 25 for traveling, a sub transmission device, an HST-type infinitely variable structure 28 for rotation, a main transmission-operating tool 68 for operating the HST-type infinitely variable structure 25 for traveling, a sub-transmission-operating device FL for operating the sub-transmission device and a steer-operating tool 19 for operating the HST-type infinitely variable structure 28 for rotation, has a lock structure for preventing the rotation of the HST-type infinitely variable structure 28 for rotation even if the steer operating tool 19 is operated when the sub- transmission device is in neutral.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an HST type continuously variable transmission mechanism for traveling which changes the vehicle speed in a crawler type working machine and an HST type continuously variable transmission mechanism for turning for steering. The present invention relates to an operation mechanism of a transmission device.

[0002]

2. Description of the Related Art Conventionally, in a crawler type working machine, a traveling drive is controlled by an HST type continuously variable transmission mechanism (for example, a real open-ended 60-8).
The technique performed according to U.S. Pat. No. 7,454,941) is known. However, there has been no HST-type transmission device provided with a traveling HST-type continuously variable transmission mechanism and a turning HST-type continuously variable transmission mechanism.

[0003]

SUMMARY OF THE INVENTION The present invention relates to a driving H
It has an ST-type continuously variable transmission mechanism and an HST-type continuously variable transmission mechanism for turning.
With the ST-type continuously variable transmission mechanism 28, the main transmission
In the transmission device which operates the HST type continuously variable transmission mechanism 25 for traveling by using the steering operation tool 19 and the HST type continuously variable transmission mechanism 28 for turning using the steering operation tool 19, the transmission HST type continuously variable transmission is used as the auxiliary transmission device 32. A continuously variable transmission mechanism 25;
When the auxiliary transmission 32 is in the neutral position and the gears are disengaged when the gears are interposed between the left and right wheels or the crawler differential mechanism 33, the operator or a third party may erroneously steer. When the operating tool 19 is operated, since the rotational force from the turning HST-type continuously variable transmission mechanism 28 is transmitted to the differential mechanism 33, there is a possibility that the aircraft starts the interlining turn on the spot. . The present invention avoids this situation.

[0004]

The problem to be solved by the present invention is as described above. Next, means for solving the problem will be described. In claim 1, the traveling HST
The continuously variable transmission mechanism 25, the auxiliary transmission device 32, and the turning HST continuously variable transmission mechanism 28 are juxtaposed, and the HST continuously variable transmission mechanism 25 for traveling is operated by the main transmission operation tool 68. The auxiliary transmission 32 is operated by the FL, and the steering operation tool 1 is operated.
9, in the transmission device for operating the HST continuously variable transmission mechanism 28 for turning, the HST continuously variable transmission mechanism 28 for rotation is rotated even when the steering operation tool 19 is operated when the auxiliary transmission device 32 is neutral. This is provided with a lock mechanism so as not to prevent such a situation.

According to the second aspect of the present invention, the traveling HST type continuously variable transmission mechanism 25, the auxiliary transmission device 32, and the turning HST type continuously variable transmission mechanism 28 are provided side by side, and the traveling HST type continuously variable transmission mechanism 68 is operated by the main transmission operation tool 68. By operating the speed change mechanism 25, the auxiliary speed change operation tool F
In the transmission device which operates the auxiliary transmission 32 by L and operates the HST type continuously variable transmission mechanism 28 for turning by the steering operation tool 19, a detection mechanism for detecting a state in which the auxiliary transmission 32 is operated in a neutral state is provided. And a mechanism B for closing the hydraulic closed circuit of the turning HST type continuously variable transmission mechanism 28 when the auxiliary transmission 32 is in the neutral position.

According to a third aspect of the present invention, the traveling HST type continuously variable transmission mechanism 25, the auxiliary transmission device 32, and the turning HST type continuously variable transmission mechanism 28 are juxtaposed. By operating the speed change mechanism 25, the auxiliary speed change operation tool F
When the auxiliary transmission device 32 is operated in a neutral position in the transmission device in which the auxiliary transmission device 32 is operated by L and the turning HST type continuously variable transmission mechanism 28 is operated by the steering operation device 19, the steering operation device is operated. When the steering angle of the steering operation tool 19 is not at the straight traveling position, the turning operation arm 16 is detected.
HST type continuously variable transmission mechanism 2 for turning
The forcible return operation is performed to the position where the straight-ahead position 8 is reached.

[0007]

Embodiments of the present invention will be described below in detail with reference to the drawings. FIG. 1 is an overall side view of a crawler type working machine in which an HST type mission device of the present invention is mounted on a combine, FIG. 2 is a plan view of the combine of FIG. 1, and FIG. 3 is an HST type mission of the present combine. FIG. 2 is a skeleton diagram of a mission device in which the device is integrated. In the figure,
The track frame 1 is provided with a traveling crawler 2.

Reference numeral 3 denotes a machine base installed on the track frame 1; 4 denotes a threshing unit formed by a threshing machine which stretches a feed chain 5 on the left side and includes a handling cylinder 6 and a processing cylinder 7; A mowing unit including a culm transport mechanism 9 and a grain stalk transport mechanism 10;
Is a hydraulic cylinder that raises and lowers the cutting unit 8 via the cutting frame 12. Reference numeral 13 denotes a straw processing unit that faces the end of the straw chain 14, and 15 denotes a kernel 16
Tank, which is carried in through the tank, 17 is the grain tank 1
A discharge auger for carrying out the grains 5 outside the machine; 18 a driving cabin provided with a steering operation tool 19 and a driver's seat 20;
An engine provided below the driving cabin 18 is configured to continuously cut and threat grain culms. In this embodiment, the steering operation tool 19 is constituted by a round steering handle.

The skeleton structure of the transmission case 22 shown in FIG. 3 will be described. The mission device, which is an operation drive unit for driving the traveling crawler 2, includes an HST-type mission device H mounted on a mission case 22. The HST-type transmission device H includes a traveling HST-type continuously variable transmission mechanism 25 which is a main transmission mechanism including a pair of a traveling hydraulic pump 23 and a traveling hydraulic motor 24, and a pair of a swing hydraulic pump 26 and a swing hydraulic motor 27. And an HST-type continuously variable transmission mechanism 28 for turning, which is a turning mechanism composed of: The input shaft 23a of the traveling hydraulic pump 23 is operatively connected to the output shaft 21a of the engine 21 via a counter case K, a transmission belt 29, and the like. The input shaft 23a of the hydraulic pump 23 is interlocked and connected. The transmission belt 30 is a power transmission member that replaces the coupling 143 shown in FIG.

The output shaft 3 of the traveling hydraulic motor 24
1, a driving wheel 34 of the traveling crawler 2 is interlocked and connected via an auxiliary transmission 32 and a differential mechanism 33 in the transmission case 22. The differential mechanism 33 in the transmission case 22 includes a pair of left-right symmetric planetary gear mechanisms 35, 35.
And each planetary gear mechanism 35 has one sun gear 36,
Three planetary gears 3 meshing on the outer periphery of the sun gear 36
7 and a ring gear 3 meshing with these planetary gears 37.
8 and the like. The planetary gear 37 is provided on the carrier 4 of the carrier shaft 40 coaxially with the sun gear shaft 39.
1 is rotatably supported on each of the left and right sun gears 3
The left and right carriers 41 are arranged to face each other with the inner gear 6 and 36 interposed therebetween, and the ring gear 38 has internal teeth meshing with the respective planetary gears 37, is arranged coaxially with the sun gear shaft 39, and is rotatable about the carrier shaft 40. It is pivoted to.

An HST-type continuously variable transmission mechanism 25 for traveling in the HST-type transmission device H controls forward / reverse rotation and rotation speed of the traveling hydraulic motor 24 by adjusting the angle of the rotating swash plate of the traveling hydraulic pump 23. To be performed, traveling hydraulic motor 2
4 is transmitted to the center gear 46 fixed to the sun gear shaft 39 by transmitting the rotation of the output shaft 31 from the transmission gear 42 in the transmission case 22 through the respective gears 43, 44, 45 and the auxiliary transmission 32. 36 is configured to rotate. The auxiliary transmission 32 includes an auxiliary transmission shaft 47 having the gear 45 and a vehicle speed sensor shaft 49 having a gear 48 meshing with the center gear 46.
7 and a pair of low-speed gears 50, 48
Medium speed gears 51, 52 and high speed gears 53, 54 are provided to enable switching between the low speed, medium speed, and high speed by sliding the gear 51 at the center position.

The sensor shaft 49 is provided with a vehicle speed detecting gear 55 and a vehicle speed sensor 56 for detecting a vehicle speed based on the number of revolutions of the gear 55. In addition, the PTO input gear 58 of the PTO shaft 57 that transmits a rotational force to a work machine or the like.
The output shaft 31 is interlocked and connected via a PTO transmission gear mechanism 59. The driving force from the traveling hydraulic motor 24 transmitted to the sun gear shaft 39 via the center gear 46 is transmitted to the carrier shaft 40 via the left and right planetary gear mechanisms 35 and transmitted to the carrier shaft 40. The rotation is transmitted to the left and right wheel shafts 34a of the left and right drive wheels 34 via the pair of left and right reduction gears 60 and 61, respectively.

Further, the HST type continuously variable transmission mechanism 28 for turning in the HST type transmission device H is provided with a turning hydraulic pump 2.
The rotation hydraulic motor 2 is adjusted by adjusting the angle of the rotary swash plate 6.
7 for controlling the forward / reverse rotation and the number of rotations. The rotation output is transmitted from the output gear of the output shaft 62 of the turning hydraulic motor 27 to the input gears 65 a and 65 b of the turning input shaft 64 via a gear transmission mechanism 63 in the transmission case 22. Directly to the external teeth of the left ring gear 38,
Also, for the external teeth of the right ring gear 38, the reverse rotation shaft 6
6 through the reversing gear 67 and the turning hydraulic motor 27
, The left and right ring gears 38 are rotated in the reverse direction, and the right ring gear 38 is rotated in the forward direction at the same rotational speed.

When the driving of the traveling hydraulic pump 23 is stopped and the driving of the traveling hydraulic pump 23 is stopped with the left and right ring gears 38 stationary, the rotation output from the traveling hydraulic motor 24 is reduced. It is transmitted from the center gear 46 to the left and right sun gears 36 at the same rotational speed, and is transmitted to the left and right wheel shafts 34a at the same rotational speed in the left and right same rotational direction via the planetary gear 37 / carrier 41 and the reduction gears 60, 61 of the left and right planetary gear mechanism 35. Then, the aircraft travels straight back and forth.

On the other hand, when the driving of the traveling hydraulic pump 23 is stopped and the left and right sun gears 36 are stationary and the left and right sun gears 36 are stationary, the left planetary gear mechanism 35 is driven. Reverse or forward rotation, and the right planetary gear mechanism 35 rotates forward or reverse to make the driving direction of the left and right traveling crawlers 2 forward and backward, and to spin the aircraft left or right on the spot. . Further, when the turning hydraulic pump 26 for turning is driven while the traveling hydraulic pump 23 for driving is driven to turn the machine body right and left, a turning with a large turning radius can be performed. It is determined according to the speed of the left and right traveling crawlers 2.

As shown in FIG. 3, a neutral braking device 1 is connected to the other end of the output shaft 62 of the turning hydraulic motor 27.
The neutral braking device 135 is constituted by a wet multi-disc disk mechanism 135a. Also, the other end of the output shaft 31 of the traveling hydraulic motor 24 is connected to the neutral braking device 13.
4, the neutral braking device 134 is constituted by a wet-type multi-plate disc mechanism 134a.

FIG. 4 shows an HST type transmission device H of the present invention.
5 is a hydraulic circuit diagram of FIG.
FIG. 6 is a left side view of the mission apparatus, showing a configuration in which the ST type mission apparatus H is mounted to form a mission apparatus as a whole, FIG. 7 is a right side view of the mission apparatus, FIG.
FIG. 9 is a partial cross-sectional plan view of the HST mission device H, FIG. 9 is a partial front sectional view of the same HST mission device H, FIG. 10 is a partial side sectional view of the HST mission device H, and FIG. Hydraulic pump for turning 2 of device H
FIG. 6 is an enlarged partial cross-sectional view illustrating a portion of a rotation servo mechanism T2.

Referring to FIG. 4, a hydraulic circuit of the HST type transmission according to the present invention will be described. The HST-type transmission device H includes an HST-type continuously variable transmission mechanism 25 for traveling and an H-type transmission for turning.
It comprises an ST-type continuously variable transmission mechanism 28, a charge pump CP, a neutral braking device 135, 134, and the like, and is attached to the front and rear surfaces of the center section C. The charge pump CP includes an input shaft 23a of the traveling hydraulic pump 23,
An input shaft 26a for driving the swing hydraulic pump 26 is connected by a coupling, and a charge pump CP is arranged and driven on the input shaft.

The charge hydraulic oil discharged from the charge pump CP is supplied to the closed circuit of the HST continuously variable transmission mechanism 25 for traveling and the closed circuit of the HST continuously variable transmission mechanism 28 for turning. I have. The charge hydraulic oil from the charge pump CP is supplied to the HST type continuously variable transmission mechanism 28 for turning.
The check valve and the throttle mechanisms 137 and 138 are arranged on both sides of the portion supplied to the closed circuit. Also,
A check valve and a throttle mechanism 141 are also arranged on one side of the supply section from the charge pump CP to the closed circuit of the traveling HST type continuously variable transmission mechanism 25.

An HST type continuously variable transmission mechanism 25 for traveling
The oil amount adjusting valve 142 is arranged in the closed circuit bypass circuit of the above, and the hydraulic pressure adjusting valve 144 is also interposed in the closed circuit bypass circuit of the HST type continuously variable transmission mechanism 28 for turning. The traveling servo mechanism T1 for tilting the swash plate 145 of the traveling hydraulic pump 23 constituting the traveling HST type continuously variable transmission mechanism 25 is operated only by operating the piston P1 and the spool S by the traveling speed manual control valve V3. It is. But,
A turning servo mechanism T2 for tilting the swash plate 146 of the turning hydraulic pump 26 constituting the HST type continuously variable transmission mechanism 28 for turning.
Are the automatic steering control valve V1 and the manual steering control valve V2.
To operate the piston P and the spool S.

As shown in FIG. 4, the charge pump CP
A part of the charge hydraulic oil from
40 and the neutral braking electromagnetic valve 139 to brake the neutral hydraulic braking device 134 and the neutral hydraulic braking device 135 during rotation of the traveling hydraulic motor 24. Running neutral braking solenoid valve 140 and turning neutral braking solenoid valve 1
During the period 39, the pressure oil from the charge pump CP is diverted to both by being connected by piping.

As shown in FIGS. 5, 6 and 7, the HST type transmission device H of the present invention has a
And a planetary gear mechanism 35, 35, an upper portion of the transmission case 22, and an HST type continuously variable transmission mechanism 25 for traveling and an HS for turning around a center section C.
A T-type continuously variable transmission mechanism 28 is additionally provided to constitute a two-pump two-motor HST type transmission device H. In the center section C, the surface on which the traveling hydraulic pump 23 is attached is a surface attached to the side surface of the transmission case 22. A turning hydraulic pump 26 and a turning hydraulic motor 27 are provided on the other surface of the center section C.
, And a traveling hydraulic motor 24 are additionally provided.

The output shaft 31 of the traveling hydraulic pump 23
And the output shaft 62 of the turning hydraulic motor 27 penetrates the center section C and projects in the same direction on the side where the traveling hydraulic pump 23 is mounted. The output shaft 31 of the traveling hydraulic pump 23 is
To drive the traveling transmission. The output shaft 62 of the turning hydraulic motor 27 is also inserted into the transmission case 22 as it is to drive the pair of symmetrical planetary gear mechanisms 35, 35 to drive the crawler-type traveling device to the steering operation tool 19. , So that the vehicle can be turned.

As shown in FIG. 8, FIG. 9, FIG. 10, and FIG.
A traveling hydraulic pump 23 constituting half of the ST type continuously variable transmission mechanism 25 is additionally provided. The traveling hydraulic motor 24, which is the other half of the HST type continuously variable transmission mechanism 25 for traveling, has the traveling hydraulic motor 24 and the output shaft at a position lateral to the input shaft 23a as shown in the plan view of FIG. 31 are arranged. The output side of the output shaft 31 projects toward the center section C, and is inserted into the transmission case 22 to drive the auxiliary transmission 32 and the differential mechanism 33. The other end of the output shaft 31 opposite to the center section C is provided with a neutral braking device 134 and a wet multi-disc disc mechanism 13.
4a and the traveling neutral braking solenoid valve 140 are arranged.

On the left side of the center section C, a turning hydraulic pump 26 constituting a turning HST type continuously variable transmission mechanism 28 is arranged at a position facing the traveling hydraulic pump 23. An input shaft 23a of the traveling hydraulic pump 23,
The input shaft 26a of the turning hydraulic pump 26 is connected to the input shaft 26a by a coupling 143, and integrally transmits the rotation of the engine 21. In this embodiment, the transmission belt 3 shown in FIG.
A coupling 143 is used instead of 0. Power from the output shaft 21a of the engine 21 is transmitted to the input shaft 23a via the transmission belt 29. A charge pump CP is provided at the other end of the driven input shaft 26a via the coupling 143, and another PTO pulley is fixed to a portion of the charge pump CP.

An automatic turning travel control valve V1 is provided on the upper surface of the turning hydraulic pump 26. The automatic turning control solenoid valve V1 and the manual turning control valve V2 and the piston P1 disposed inside the piston P2 are connected to each other. The entire rotation servo mechanism T2 is configured between the two. In the vicinity of the traveling hydraulic pump 23, a traveling servo mechanism T1 is configured by a manual traveling control valve V3 or a spool S3, an electromagnetic switching valve V3, and a piston P2. The other end of the output shaft 62 of the turning hydraulic motor 27 is provided with the neutral braking device 13.
5, a turning neutral braking solenoid valve 139 and a wet multi-disc disc mechanism 135a are additionally provided.

Next, the configurations of the traveling servo mechanism T1 and the turning servo mechanism T2 will be described. 8, 9 and 1
At 0, a plan view of the traveling servomechanism T1 is shown. The traveling servo mechanism T1 includes a manual traveling speed change valve V
By operating the spool S1 that constitutes No. 3, the piston P1 is moved up and down, the swash plate 145 is turned, and the HST type continuously variable transmission mechanism 25 for turning for traveling is shifted. It is necessary to hold the traveling HST type continuously variable transmission 25 at a neutral position. A traveling neutral holding arm 148 is provided, and a traveling neutral holding roller 148a is pivotally supported at a tip of the traveling neutral holding arm 148. .

The traveling neutral holding roller 148a is formed integrally with the traveling gear shift operation arm 151 by rotating the traveling neutral cam 149, and the traveling neutral holding roller 148a is fitted into a central concave portion of the traveling neutral cam 149. Maintain neutrality. A long hole is formed through the traveling neutral holding arm 148, and a pin portion of the traveling speed change operation arm 151 is fitted into the long hole to absorb backlash of the link system due to vibration of the working machine. Further, the traveling speed change operation arm 151 is provided with a traveling stopper rod 150 that rotates together with the traveling speed change operation arm 151 via an impact absorbing spring 151a, and is engaged with the stopper plate 157 to further move the traveling speed change operation arm 151. Prevent rotation.

The traveling speed change operation arm 151 is provided with a crank arm 159 for operating the spool S1 via an impact absorbing spring 151a. The crank arm 159 is engaged with a concave portion of the spool S1. I have. The spool S1 slides inside the piston P1 to form a manual traveling shift valve V3. A similar turning servo mechanism T2 is configured to turn the swash plate 146 of the turning hydraulic pump 26 as shown in FIG. The configuration of the turning servo mechanism T2 of the turning hydraulic pump 26 is substantially the same as that of the traveling servo mechanism T1 and is symmetrical.

That is, the turning neutral holding arm 152 which rotates together with the turning operation arm 162, and the turning neutral holding roller 152a supported by the turning neutral holding arm 152 are formed. Further, a turning neutral cam 153 to which the turning neutral holding roller 152a is prefixed is provided, and a turning stopper rod 154 and a turning stopper plate 156 with which the turning stopper rod 154 is engaged are formed. The swing operation arm 162 is provided with a shock absorbing spring 162a.

The traveling servo mechanism T1 and the turning servo mechanism T2
Are formed to be substantially symmetrical with each other, and between the traveling neutral holding arm 148 and the turning neutral holding arm 152, the traveling neutral holding roller 148a and the turning neutral holding roller 152a
An urging spring 160 that is constantly urged in the direction of the traveling neutral cam 149 and the turning neutral cam 153 is interposed. These rollers 148a, 152a are used as neutral cams 14a, 15a.
When engaging with the neutral position formed on the cam surface of No. 3,
The traveling crawler 2 is kept in an operation stop state when the traveling crawler 2 is neutral.

Referring now to FIG. 11, the arrangement of the turning hydraulic pump 26, the turning hydraulic motor 27, and the turning servo mechanism T2 of the turning HST type continuously variable transmission mechanism 28 will be described. An HST type continuously variable transmission mechanism 28 for turning is additionally provided in the center section C, and a turning servo mechanism T2 is embedded in the case of the HST type continuously variable transmission mechanism 28 for turning. This configuration is the same as that of the traveling HST-type continuously variable transmission mechanism 25. The case of the traveling HST-type continuously variable transmission mechanism 25 is directly attached to the other surface of the center section C. The traveling servo mechanism T1 is embedded in the case of the pump 23 and is integrally formed.

The directions of the traveling servomechanism T1 and the turning servomechanism T2 correspond to the vertical rotation direction of the cradle type swash plate provided on the traveling hydraulic pump 23 and the turning hydraulic pump 26, the pistons P1, P2, and the spool S1S2. Have the same sliding direction. The pistons P1 and P2 and the cradle-shaped swash plate 146 are connected by connecting pins 190.
As shown in FIG. 8, the charge pump CP includes:
The suction port 196 and the discharge port 195 are opened, and the hydraulic oil from the hydraulic oil tank is sucked into the suction port 196, discharged as pressure oil from the suction port 196, and passed through the hydraulic oil filter. A check valve / throttle mechanism 137, 138, a check valve / throttle mechanism is supplied to the upper supply port 194, and a part thereof is connected to a closed circuit of the traveling HST type continuously variable transmission mechanism 25 and the turning HST type continuously variable transmission mechanism 28. Excess hydraulic oil is supplied from the relief injection valve 199 to the inside of the turning HST type continuously variable transmission mechanism 28 and used as cooling oil.

Hereinafter, an HST type continuously variable transmission mechanism 25 for traveling will be described.
A link system extending from a main shift lever 68, which is a main shift operation tool connected to the steering gear, and a steering operation tool 19 connected to the HST type continuously variable transmission mechanism 28 for turning, to a turning neutral holding arm 152 and a turning operation arm 162. Will be described. FIG. 12 is an explanatory diagram of a traveling shift and steering operation unit, FIG. 13 is a front explanatory diagram of the operating unit, FIG. 14 is a plan explanatory diagram of the operating unit, FIG. 15 is a side explanatory diagram of the operating unit, and FIG. FIG. 17 is a front view of the operation member, FIG. 18 is a plan view of the operation member,
FIG. 19 is a plan view of the steering handle, and FIG. 20 is a plan view of the link mechanism.

As shown in FIGS. 12 to 20, a main transmission lever 68, which is a main transmission operation tool connected to the traveling HST type continuously variable transmission mechanism 25, and a HST type continuously variable transmission mechanism 28 for turning. The steering operation tool 19 is linked to a speed change and turning interlocking mechanism 69 which is an interlocking means, and the interlocking mechanism 69 is connected to a traveling speed change and steering link mechanism 70, 71.
, The traveling shift operation arm 151 and the turning neutral holding arm 152 of the HST type transmission mechanisms 25 and 28 for traveling and steering.
It is linked and linked.

The interlocking mechanism 69 is configured as follows. The base bent portion 68a of the main transmission lever 68 is
It is pivotally supported to swing right and left. The cylindrical shaft 74 is fixedly mounted on a rotating plate 75 that is rotatable back and forth. The rotating plate 7
5 is pivotally supported by a first pivot 77 that is bearing-supported by a fixed mounting plate 78 integrated with the machine frame 76 on the machine body side. The rotation of the main transmission lever 68 causes the cylinder shaft 74 to rotate, and the rotation plate 75 integrally formed with the cylinder shaft 74 rotates. The pivot plate 75 is provided with a second pivot 79 in the front-rear direction orthogonal to the pivot 77. The rotating plate 75 is
When the main shift lever 68 is turned around the first pivot 77, the second pivot 79 also turns back and forth. The speed change operation member 80 and the steering operation member 81 are pivotally supported on the second pivot 79 separately and rotatably. A speed change operation member 80 rotatably provided on a second pivot 79;
The steering operation member 81 rotatably connected around the axis of the steering wheel is used to link the operation output sections 80a, 81a at the eccentric positions to the speed change and steering link mechanisms 70, 71 in an interlocking manner.

The speed change and steering link mechanisms 70 and 71, which are connected to the traveling speed change operation arm 151 and the turning operation arm 162 of the HST type transmission device H,
9 and is linked to the speed change and turning interlocking mechanism 69 at the position of a swing shaft 82 supported on the machine frame 76 side. Further, from the position of the swing shaft 82, the driving cabin 18 is connected via the steering universal joint type first rods 97, 98.
The first swing arms 95 and 96 at the position of the rotation fulcrum shaft 92
It is connected to. For the first swing arms 95 and 96, a universal joint type second rod for steering 107 and 108, which constitutes a traveling speed change and steering link mechanism 70, 71, is provided.
The swing arms 109 and 110 are connected. Swing axis 8
2, a swing cylinder shaft 83 is loosely fitted to the outside, and a speed change arm 84 is fixed to the swing cylinder shaft 83.

A base end of a steering arm 85 is fixed to the swing shaft 82. The output portions 80a of the speed change operation member 80 pivotally supported by the second pivot 79 and the output portion 81a of the steering operation member 81 also pivotally supported by the second pivot 79 are provided with respective operation output shafts 86 and 87 in FIG. The operation output shaft 8
Between the universal joint shafts 88 and 8 and the respective arms 84 and 85
9 are connected. The swing shaft 82 and the swing cylinder shaft 83
Transmission and steering output arms 90, 91 fixed to the right end
And first speed change and steering first swing arms 95 and 96 rotatably provided on an intermediate shaft 94 mounted on a fulcrum bearing 93 of a rotation fulcrum shaft 92 of the driving cabin 18 are a universal joint type for speed change and steering. They are connected by first rods 97 and 98. The output arms 90 and 91 and the first swing arm 95,
The first universal joint-type rods 97 and 98 for shifting and steering are respectively connected between the respective ends of the first and second 96 and the second shifting and steering mechanism provided on the intermediate shaft 94 and integrally connected to the first swing arms 95 and 96. Two swing arms 99 and 100 are provided.

The bearing plate 1 above the transmission case 22
01, a shift and steering cylinder shaft 103, 104 rotatably supported by a support shaft 102 mounted on the cylinder shaft 103, and the cylinder shaft 103, 1
A first swing arm 105, 106 having a base end fixedly mounted on the base 04 and a second universal joint type rod 107, 108 for speed change and steering, which connects between the distal ends of the second swing arms 99, 100 are provided. Have been. A second swing arm 109 and 110 having a base end fixed to the cylindrical shafts 103 and 104, a speed change servo rod 111 and a turning servo rod 112 for connecting between respective ends of the control levers 72 and 73 are provided. doing.

The rotation of the traveling operation member 80 about the first pivot 77 causes the traveling speed change operation arm 151 to rotate, and the steering operation member 81 about the traveling second pivot 79.
The shift and the steering control are performed by operating the steering turning operation arm 162 by the rotation of.

On the other hand, a gear 114 is provided on the steering operation shaft 113 at the lower end of the steering operation tool 19, and the rear rotation shaft 11
The gear 114 is engaged with a sector gear 116 attached to the fifth gear 5. A first swing arm 118 of the steering shaft 117 disposed below the position of the main shift lever 68 is provided. An output arm 11 having a base fixed to the rotation shaft 115
9 are connected via a universal joint type steering first rod 120 which is a steering link mechanism. Steering axis 11
7, the second swing arm 12 integrated with the first swing arm 118
1 is attached to the front end of the universal joint shaft 89 by a universal joint type steering second
They are connected via a rod 122. The steering operation member 81 is configured to rotate about the second pivot 79 by the rotation operation of the steering operation tool 19.

The gear 114 of the steering operation shaft 113
A neutral positioning plate 123 is provided below, and one end of a steering detection link 125 is connected to a projecting shaft 124 on the lower surface of the positioning plate 123. The first swing arm 127 of the reduction arm shaft 126 disposed on the right side of the rotation shaft 115 is connected to the other end long hole 125 a of the detection link 125 via an engagement pin 128. The deceleration arm 129 of the steering shaft 117 and the second swing arm 1 of the deceleration arm shaft 126
The universal joint type first deceleration rod 131, which is a deceleration link mechanism, is connected between the respective ends of the first and second end portions 30.

The rightmost end of the deceleration transmission shaft 132 of the speed change operation member 80 and the other end of the second swing arm 130 are connected by a universal joint type second deceleration rod 133, and the steering operation is performed in a running state. As the steering amount of the tool 19 increases, the second deceleration rod 133 is pulled downward to reduce the traveling speed.

As shown in FIG. 20, a speed change and steering operation member 8081 is rotatable around an axis, a second pivot 79, and a universal joint 89a between a steering arm 85 and a joint shaft 89. Are positioned on the horizontal line Ll in the front-rear direction. A universal joint portion 88b, 89b between the operation output shaft 86, 87 and the universal joint shaft 88, 89,
The pivot 77 is positioned on a horizontal horizontal line L2 orthogonal to the line Ll. Further, the shifting arm 84
Joint part 88a between the shaft and the joint shaft 88 and the tentacle part 89a
Are positioned on a horizontal horizontal line L3 parallel to the line L2, and when the main shift lever 68 and the steering operating tool 19 are held neutral, even if either one of them is operated, each of the operating members 80 and 81 Is rotated only about the first and second pivots 77 and 79, and no operating force is applied to the joint shafts 88 and 89.

As shown in FIG. 16, when the operation member 80 is tilted back and forth by an angle α1α2 around the first pivot 77 by the forward / reverse operation of the main transmission lever 68, the joint shaft 8
By pulling or pushing 8, the speed change arm 84 is operated to switch the traveling speed between forward and backward. Also, as shown in FIG. 17, during this state, that is, when the main shift lever 68 is at a position other than the neutral position, the second pivot 79
When the operating member 81 is tilted up and down by an angle β1β2 around the center, the steering shaft 8 is pulled by pushing or pushing the joint shaft 89.
5 is rotated to make a left and right turn of the aircraft.
That is, even if the turning operation is performed during the neutral time of the main shift, the joint shaft 8
9 moves to a position on the conical surface centered on the line Ll, and the distance between the joints 89a and 89b does not change.
Therefore, the turning hydraulic motor 2 of the HST type continuously variable transmission mechanism 28
7 does not rotate.

As shown in FIG. 19, the detection link 125 provided on the steering operation tool 19 is provided with the first swing arm 127 regardless of the right or left turning operation from the neutral position.
Are rotated in the same direction within the range of the angle θ, and the second deceleration rod 133 is always pulled. When the operating member 80 at the time of the forward operation is inclined to the angle α1 in FIG.
When the distance between the joints 88a and 88b is reduced, and the contact member 80 at the time of the reverse operation is inclined toward the angle α2,
By increasing the distance between the joints 88a and 88b, the shift arms 84 in FIG. 12 involved in the shift of the HST-type continuously variable transmission mechanism 25 are respectively displaced toward the low speed side in the neutral direction, and the shift arms 84 are adjusted according to the amount of turning. Deceleration is performed.

As described above, the H provided with the traveling HST type continuously variable transmission mechanism 25 and the turning HST type continuously variable transmission mechanism 28.
In the ST-type transmission device, in the present embodiment, as the auxiliary transmission device 32, the gear transmission mechanism includes a traveling HST-type continuously variable transmission mechanism 25 and a left and right wheel or crawler differential mechanism 33.
If the operator or a third party erroneously operates the steering operation tool 19 when the auxiliary transmission 32 is in the neutral position and the gear is disengaged, the HST type for turning is installed. The rotational force from the continuously variable transmission mechanism 28 is applied to the differential mechanism 3
Therefore, there is a possibility that the aircraft will start an interlining turn on the spot. In order to solve this problem, when the auxiliary transmission 32 is in the neutral position, the steering operation tool 19
Is operated, a lock mechanism is provided so that the turning HST-type continuously variable transmission mechanism 28 does not rotate.

In the hydraulic circuit diagram shown in FIG.
An embodiment in which a mechanism B for closing an oil passage is provided to a steering control piston P2 for operating a swash plate of a turning hydraulic pump 26 of an ST-type continuously variable transmission mechanism 28 is shown. The mechanism B for closing the oil passage is constituted by an electromagnetic valve or the like. When the neutral sensor switch FS detects that the auxiliary transmission 32 is in the neutral state, the steering control piston P2 is immediately turned on.
Is returned to the neutral position, the mechanism B for closing the oil passage is closed, and the steering control piston P2 is operated, that is, the turning H
This prevents the ST type continuously variable transmission mechanism 28 from being operated from the neutral position to the rotational position. In this state, the turning HST-type continuously variable transmission mechanism 28 goes straight, and even if the steering operation tool 19 is operated, the turning hydraulic motor 27 starts rotating because the steering control piston P2 does not move. There is no.

In the embodiment shown in FIG.
FIG. 9 illustrates a lock mechanism for preventing the turning operation arm 162 of the ST type continuously variable transmission mechanism 28 from turning from the neutral position to another position, and a configuration in which the turning neutral holding arm 152 is operated by the solenoid SO. I have. That is, when the sub-transmission 32 comes to the neutral position, the solenoid SO is turned on to turn on.
Of the circuit. Then, the solenoid SO is turned on.
Then, the solenoid SO is pivoted to the neutral holding arm 152.
The turning neutral holding roller 152a at the tip of the turning neutral holding arm 152 presses the concave portion of the turning neutral cam 153, and the turning neutral cam 153 that rotates integrally with the turning operation arm 162 cannot rotate. Thus, even if the operator turns the steering handle constituting the steering operation tool 19 by mistake, the turning neutral holding roller 152a locks the turning neutral cam 153, so that the turning HST continuously variable transmission mechanism 28 can be used. Cannot be in a state to start rotation.

In FIG. 22, the solenoid S of FIG.
An embodiment using a clutch motor G instead of the embodiment of O is illustrated. Also in this case, the circuit is configured so that the clutch motor G is turned on when the auxiliary transmission 32 is operated to the neutral position. Then, when the clutch motor G rotates, via the return spring b,
The arm a protruding from the turning neutral holding arm 152 is strongly pulled, and the portion of the turning neutral holding roller 152a presses the concave portion of the turning neutral cam 153. Even if the direction operating tool 19 is operated, the turning operation arm 162 can be locked so as not to rotate to a position other than the neutral position.

In the embodiment shown in FIG. 23, when the auxiliary transmission 32 becomes neutral, the steering operation tool 19 is erroneously operated by the operator and the steering HST type continuously variable transmission mechanism 28 is turned.
Is rotated to a position other than the neutral position, the steering operation tool 1 such as a potentiometer is positioned below the steering operation tool 19.
9, a rotation position detection sensor PM is provided, a signal from the rotation position detection sensor PM is detected, and the steering operation tool 19 is turned regardless of the operation position of the turning HST type continuously variable transmission mechanism 28. Arm 162 and the turning operation arm 16
A return drive motor SM is provided for returning the turning neutral holding arm 152 that rotates integrally with the motor 2 to a neutral position. By operating the return drive motor SM, the turning neutral holding arm 1
52 and the turning operation arm 162 are forcibly rotated to the left or right, and returned to the neutral position of the turning HST-type continuously variable transmission mechanism 28.

In FIG. 24, FIG. 21, FIG. 22, and FIG.
3 discloses a mechanism for detecting that the auxiliary transmission 32 has been operated to the neutral position. The neutral sensor switch FS of the auxiliary transmission device 32 in FIG. 24 detects that the projection of the projection cam CA provided below the auxiliary transmission operation tool FL is neutral when the neutral sensor switch FS is pressed. The solenoid SO, the clutch motor G and the return drive motor SM are operated. In FIG. 25, a control circuit that inputs a signal from the neutral sensor switch FS to the controller T and turns on the return drive motor SM in response to a signal from the controller T that the auxiliary transmission 32 has become neutral. Is shown.

[0053]

As described above, the present invention has the following advantages. That is, the auxiliary transmission 32
However, when the operator erroneously operates the steering operation tool 19 in the neutral state, the turning hydraulic motor 27 rotates, and the gears of the sub-transmission 32 are not engaged. The differential mechanism acts, the left and right crawlers or wheels start to reverse, and start a spin turn,
As in the present invention, when the neutral position of the auxiliary transmission 32 is detected, the swash plate of the turning hydraulic pump 26 is fixed at the neutral position so that the turning hydraulic motor 27 does not rotate immediately.
It was possible to eliminate the occurrence of this spin turn. This locking mechanism also locks the hydraulic circuit to the steering control piston P2 by closing the oil passage by a method of locking the turning operation arm 162 at the neutral position so that the turning operation arm 162 cannot rotate by the solenoid SO or the clutch motor G. Alternatively, the steering operation tool 19 may be returned to the neutral rotation position and returned by the drive motor SM.

[Brief description of the drawings]

FIG. 1 is an overall side view of a crawler type working machine in which an HST type mission device of the present invention is mounted on a combine.

FIG. 2 is a plan view of the combine shown in FIG. 1;

FIG. 3 is a skeleton diagram of a mission device in which the HST mission device H of the present invention and a mission case 22 are integrated.

FIG. 4 is a hydraulic circuit diagram of the HST type transmission device H of the present invention.

FIG. 5 is a rear view showing a configuration in which an HST type mission device H is mounted on an upper portion of a mission case 22 to form a mission device as a whole.

FIG. 6 is a left side view of the mission device.

FIG. 7 is a right side view of the mission device.

FIG. 8 is a partial cross-sectional plan view of the HST mission device H;

FIG. 9 is a front partial cross-sectional view of the HST mission device H;

FIG. 10 is a partial cross-sectional side view of the HST mission device H.

FIG. 11 is an enlarged partial cross-sectional view showing a part of a turning hydraulic pump 26 and a turning servo mechanism T2 of the HST type transmission device H.

FIG. 12 is an explanatory diagram of a traveling speed change and steering operation unit.

FIG. 13 is an explanatory front view of an operation unit.

FIG. 14 is an explanatory plan view of an operation unit.

FIG. 15 is an explanatory side view of the operation unit.

FIG. 16 is an explanatory side view of the operation member.

FIG. 17 is an explanatory front view of an operation member.

FIG. 18 is an explanatory plan view of an operation member.

FIG. 19 is an explanatory plan view of a steering handle portion.

FIG. 20 is an explanatory plan view of a link mechanism.

FIG. 21 is a view showing a mechanism for locking the rotation of a turning operation arm 162 by pressing a turning neutral holding roller 152a against a turning neutral cam 153 by a solenoid SO.

FIG. 22 is a drawing showing a mechanism for rotating a turning neutral holding arm 152 by a clutch motor G to press a turning neutral cam 153 to lock the turning operation arm 162;

23 shows a rotation position of the steering operation tool 19 detected by a rotation position detection sensor PM, and returns the steering operation tool 19 to a neutral position where the turning hydraulic motor 27 does not rotate by a return drive motor SM. Drawing which shows a mechanism.

FIG. 24 is a view showing a mechanism for detecting a neutral position of a subtransmission operating tool FL by a neutral sensor switch FS.

FIG. 25 is a diagram showing a control circuit that drives a neutral sensor switch FS by processing a signal from the neutral sensor switch FS by a controller T.

[Explanation of symbols]

 T Controller FL Sub gearshift operation tool FS Neutral sensor switch CA Projection cam G Clutch motor SO Solenoid H HST type transmission device C Center section CP Charge pump T1 Travel servo mechanism T2 Swing servo mechanism P1 Travel control piston P2 Steering control piston S1 Travel control Spool S2 Steering control spool 18 Operating cabin 19 Steering operation tool 22 Transmission case 23 Traveling hydraulic pump 24 Traveling hydraulic motor 25 HST type continuously variable transmission mechanism for traveling 26 Rotating hydraulic pump 27 Rotating hydraulic motor 28 Non-rotating HST type Step shifting mechanism 32 Auxiliary transmission

──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. ⁶ Identification code FI // F16H 59:58 (72) Inventor Taiji Mizukura 1-32 Chaya-cho, Kita-ku, Osaka City, Osaka Inside Yanmar Agricultural Machinery Co., Ltd. 72) Inventor Wataru Nakagawa 1-32 Chaya-cho, Kita-ku, Osaka, Osaka, Japan Inside Yanmar Agricultural Machinery Co., Ltd. (72) Inventor Ritsuko Kajioka 1-32-Chaya-machi, Kita-ku, Osaka, Osaka, Japan Yanmar Agricultural Machinery Co., Ltd.

Claims (3)

[Claims] An HST continuously variable transmission mechanism 25 for traveling is provided with an auxiliary transmission device 32, an HST continuously variable transmission mechanism 28 for turning, and an HST continuously variable transmission mechanism 28 for turning. Is operated, the auxiliary transmission device FL is operated by the auxiliary transmission operation device FL, and the turning HST-type continuously variable transmission mechanism 28 is operated by the steering operation device 19. When the auxiliary transmission device 32 is neutral, An operation mechanism for an HST-type transmission device, wherein a lock mechanism is provided to prevent rotation of the turning HST-type continuously variable transmission mechanism 28 even when the steering operation tool 19 is operated. 2. A traveling HST-type continuously variable transmission mechanism 25 having a traveling HST-type continuously variable transmission mechanism 25, an auxiliary transmission device 32, and a turning HST-type continuously-variable transmission mechanism 28 arranged side by side. , The auxiliary transmission device FL is operated by the auxiliary transmission operation device FL, and the turning HST type continuously variable transmission mechanism 28 is operated by the steering operation device 19, the auxiliary transmission device 32 is operated to neutral. An HST-type transmission device provided with a detection mechanism for detecting a state, and a mechanism B for closing a hydraulic closed circuit of the turning HST-type continuously variable transmission mechanism 28 when the auxiliary transmission 32 is in a neutral position. Operation mechanism. 3. An HST continuously variable transmission mechanism 25 for traveling, an auxiliary transmission device 32 and an HST continuously variable transmission mechanism 28 for turning are juxtaposed, and the HST continuously variable transmission mechanism 25 for traveling is operated by a main transmission operation tool 68. , The auxiliary transmission device FL is operated by the auxiliary transmission operation device FL, and the turning HST type continuously variable transmission mechanism 28 is operated by the steering operation device 19, the auxiliary transmission device 32 is operated to neutral. In this case, the turning angle of the steering operation tool 19 is detected, and when the steering operation tool 19 is not in the straight-ahead position, the turning operation arm 162 is forcibly operated to turn the HST type stepless stepless turning. HS for forcibly returning the transmission mechanism 28 to a position where the transmission mechanism 28 becomes a straight-ahead position.
Operation mechanism of T-type mission device.