JP3257644B2 - Travel transmission - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a traveling speed change of a traveling vehicle which enables a fine speed adjustment at a low speed such as during work.

[0002]

2. Description of the Related Art Conventionally, it has been known to use an HST type transmission and a hydraulic clutch type transmission as a traveling transmission used for driving agricultural machines such as a combine.
For example, Japanese Utility Model Laid-Open No. 4-90462 and Japanese Utility Model Laid-Open No. 63-142
No. 451.

[0003]

In such a prior art, when an HST type transmission is used, the transmission efficiency from the hydraulic pump to the hydraulic motor is poor, so the engine is enlarged to increase the output. There is a need to.
In addition, when driving in a high-speed range, the loss of the engine output increases. When a hydraulic clutch type transmission is used, a continuously variable transmission like an HST type transmission is not possible, and a fine speed adjustment required for work in a field cannot be performed. As described above, both transmissions have the above-mentioned disadvantages.

[0004]

Means for Solving the Problems The present invention has the following configuration in order to solve the above problems. HST type
Hydraulic clutch for low speed range for operating transmission (H1)
(A) and a hydraulic clutch type transmission (H2).
For transmission changeover switching hydraulic clutch (B) for high speed range
A valve (V1) is provided, and a hydraulic clutch type transmission is provided.
(H2) speed switching valve (V
2), the transmission switching valve (V1) and the speed
The switching valve (V2) and the HST-type transmission (H1)
Main transmission lever (1) to operate trunnion for continuously variable transmission
And the main shift lever (1) is located in a predetermined low speed range.
At this time, the speed is changed by the HST type transmission (H1),
Hydraulic clutch type transmission when located on high speed side other than
Transmission switching valve (V
1) is switched, and on the high-speed side,
Low-range hydraulic clutch (A) is OFF, high-speed hydraulic
The clutch (B) is turned on and the hydraulic clutch type transmission (H
2) Hydraulic clutch (C1) (C2) (C3) (R)
Is turned on, and on the low speed side,
Hydraulic clutch (A) ON, hydraulic clutch for high speed range
(B) is turned off and is in the forward constant speed range (X).
In the case, the first-speed hydraulic clutch (C1) is ON, the reverse body side area
(Y) When the reverse hydraulic clutch (R) is ON
And, HST and corresponds to the position of simultaneously main shift lever (1)
Continuously variable speed by the trunnion rotation of the transmission (H1)
It is what is done.

[0005]

When the main shift lever 1 is in a low speed range having a certain width from the neutral position, the hydraulic clutch A on the output shaft of the HST type transmission H1 is turned on, and the agricultural machine is driven at a continuously variable speed. When the main shift lever 1 is set in a high speed region exceeding a certain width, the hydraulic clutch B on the input shaft of the hydraulic clutch type transmission H2 is turned on, and each hydraulic clutch is turned on in accordance with the set position of the main shift lever 1. It is turned on and off, and the agricultural machine runs at the set speed.

[0006]

Embodiments of the present invention will be described below with reference to the drawings.
1 is an overall side view of a combine driven by the transmission of the present invention, FIG. 2 is a skeleton diagram of the transmission of the present invention,
3 is a hydraulic circuit diagram of the hydraulic clutch, FIG. 4 is a side view of the main transmission lever 1, FIG. 5 is a plan view showing a guide 2 for the main transmission lever 1, and FIG. 6 is a side view of a combine crawler traveling device. 7, FIG. 7 is a side view showing the movement of the equalizer 18, FIG. 8 is a side view of the same, FIG. 9 is a side view of a belt transmission mechanism for preventing belt loosening at the time of clutch switching, and FIG. FIG. 11 is a block diagram showing an auger turning operation mechanism of the combine.

First, the overall structure of a combine as an embodiment of an agricultural machine to which the axle drive device of the present invention is applied will be described with reference to FIG. The combine forms a fuselage frame 11 at the upper part of the crawler traveling device 10, on which a threshing unit 13 and a sorting unit 14 are vertically arranged on the left side, and a steering unit 15 and a Glen tank 16 are arranged on the right side. The main shift lever 1 and the auxiliary shift lever 7 are disposed in the steering section 15, and an auger 17 for discharging the paddy is provided on the Glen tank 16 so as to be rotatable. In addition, a mowing unit 12 is provided in front of the threshing unit 13 and the sorting unit 14.
Then, the engine E is arranged near the lower part of the steering section 15,
Part of the driving force of the engine E is transferred to the crawler traveling device 10.
The transmission is transmitted to the traveling transmission H disposed therein, the axle 9 is rotated, and the crawler traveling device 10 is driven.

Next, the internal structure of the traveling transmission H will be described with reference to FIG. The travel gear device H, mission
An HST-type transmission H1 is attached to the transmission case MC , and the HST-type transmission H1 is provided in the transmission case MC .
Input shaft S1, output shaft S2, and the transmission case M
The input shaft S3 for driving each gear in C is mounted on the shaft.
The input shaft S1 of the HST transmission H1 is connected to a power take-off shaft S
The gear pump 8 drives the charge pump P that supplies pressure oil to each hydraulic device. A low-speed range hydraulic clutch A is interposed between the output shaft S2 and the gear G1,
The gear G1 meshes with a gear G2 fixed to the input shaft S3. Whether the input shaft S3 is the mission case MC
A pulley is provided on the part protruding outside from
Entering rotation from. A high-speed range hydraulic clutch B is interposed on the input side of the input shaft S3, and auxiliary transmission gears G3, G4, G5 are arranged on the shaft. The auxiliary transmission gear G
The gears 3 to G5 are slidable by the operation of the auxiliary transmission lever 7, and are selectively meshable with the gears G7 to G9 on the counter shaft S4. Further, the mission case
In the MC , the transmission clutch shafts S5 and S6 are suspended, and the gears G6 and G9 on the counter shaft S4 mesh with the gears G10 and G12 on the transmission clutch shaft S5, respectively.
Let me. Furthermore, the gear G9 on the counter shaft S4
Is also engaged with the gear G11 on the transmission clutch shaft S6.
The second speed hydraulic clutch C2 is configured to rotate forward.
ing. The gear G10 on the transmission clutch shaft S5
Directly meshes with the gear G13 on the transmission clutch shaft S6.
The gear G13 is connected to the other gears G10, G11, G
It is configured to make reverse rotation and reverse rotation
I have. On the transmission clutch shaft S5, the gear G10
And a third-speed hydraulic clutch C3 between the first-speed hydraulic clutch C1 and the gear G12. On the transmission clutch shaft S6, a second-speed hydraulic clutch C2 is interposed between the gear G11 and a reverse hydraulic clutch R is interposed between the gear G13 and a three-speed forward and one-speed reverse hydraulic clutch.
The transmission H2 is configured. Each of the hydraulic clutches is selectively connected by a turning operation of the main shift lever 1 to perform a shifting operation.

Further, in the mission case MC ,
A gear G14 on the transmission clutch shaft S5 and a gear G15 on the transmission clutch shaft S6 are meshed with a gear G16 fixed on the side clutch shaft S7 .
The power is transmitted to the side clutch shaft S7. The sa
Left and right gears G18, G loosely fitted on the id clutch shaft S7
19, disconnect and connect the left and right side clutches 8R and 8L,
The gears G20 and G21 on the axles 9L and 9R
Has reached. The side clutches 8R and 8L are connected during straight running, and the side clutch 8 on the outside of the turn is connected during turning, and the side clutch 8 on the outside is disconnected, and only the power on one side is transmitted. 9L and 9R are driven for turning.

The hydraulic clutches A and B for shifting shown in FIG.
・ C1, C2, C3, R, and side clutch 8L ・ 8
R is operated by a hydraulic valve shown in FIG. That is, when the transmission switching valve V1 is switched, one of the low speed range hydraulic clutch A for operating the HST type transmission H1 and the high speed range hydraulic clutch B for operating the hydraulic clutch type transmission H2 is selected . One of them can be turned ON. With the speed switching valve V2, the hydraulic clutches C1, C2,
One of the side clutches 8R and 8L can be turned on by the turning switching valve V3. In the shifting operation, when the speed switching valve V2 is set to F1, the first-speed hydraulic clutch C1 is turned on, when F2, the second-speed hydraulic clutch C2 is turned on, and when F3, the third-speed hydraulic clutch C2 is turned on. C3 is ON
In the case of R, the reverse hydraulic clutch R is turned on, and in Nu, all four hydraulic clutches are turned off. The hydraulic valves V1 and V2 are switched based on the position of the main shift lever 1, and the relationship between the positions and the operation of the hydraulic valves will be described later. In addition,
The turning switching valve V3 can be switched by a turning operation using a steering lever or the like in the steering section.

Referring to FIGS. 4 and 5, the structure of the main shift lever 1 will be described. The main transmission lever 1 is provided so as to be movable back and forth in a guide groove 2 shown in FIG. At the lower part of the guide groove 2, as shown in FIG. 4, the base end of the main transmission lever 1 fitted in the guide groove 2 is fixed to the rotation shaft 3 a of the transmission cam 3. And, at the front end of the speed change cam 3,
The hydraulic clutch for the low-speed range for operating the HST-type transmission H1 described above.
High speed range for operating the clutch A and the hydraulic clutch type transmission H2
The end of a transmission rod 4 for switching the speed switching valve V2 for switching the hydraulic clutch B is pivotally supported. Further, on the side surface of the transmission cam 3, an arc-shaped operation arm rotation groove 3b is provided from the front to the rear. The front end portion 5b of the operation arm 5, which is configured to be rotatable up and down with the rotation shaft 5a as a fulcrum, is fitted into the operation arm rotation groove 3b, and is pivotally mounted.

The rear end of the operation arm 5 has an HS
When the T-type transmission H1 is operating, the end of a low-speed range shifting rod 6 for pivoting the trunnion of the HST transmission H1 is pivotally supported. The operation arm rotation groove 3b is eccentric, and the front is near the rotation shaft 3a and the rear is near the outer circumference of the speed change cam 3. When the operation arm 5 is tilted forward, the front end 5b of the operation arm 5 becomes higher than the rotation shaft 5a, so that the low-speed range shifting rod 6 moves downward, and when the main shift lever 1 is tilted backward, The front end 3b is a rotating shaft 5
a, the low-speed range shifting rod 6 moves upward. Then, the switching configuration of the transmission switching valve V1 is determined based on the position when the main transmission lever 1 is at the neutral position Nu described later, and the elevation width of the transmission rod 4 or the low-speed range transmission rod 6 is changed. When it is within a certain width, the low-speed range hydraulic clutch A is turned on to operate the HST type transmission H1, and when it is more than a certain width, the high-speed range hydraulic clutch B is turned on and the hydraulic clutch type transmission H2 is turned on. Is configured to operate.

On the other hand, in the guide groove 2 shown in FIG. 5, a third forward speed F3, a second forward speed F2, a first forward speed F1, a neutral position Nu, and a first reverse speed R are arranged rearward from the front, and the main speed is changed. By setting the lever 1 at each position, the speed switching valve V2 is set to F3 ·
The hydraulic clutches C1, C2, C3, and R are set to ON or OFF.

In the axle driving apparatus having the above-described structure, the hydraulic clutch is turned on based on the position of the main transmission lever 1.
-Organize the OFF configuration. That is, F1, F2, F3, R
On the high speed side, the low-speed range hydraulic clutch A
F, the high-speed range hydraulic clutch B is turned on, and one of the hydraulic clutches C1, C2, C3, and R in the hydraulic clutch type transmission H2 is turned on. And the main shift lever 1 is
When it is within the HST shift range L shown in FIG. 5, the low-speed range hydraulic clutch A is ON, and the high-speed range hydraulic clutch B is OFF.
Among them, when it is in the neutral position Nu, the other hydraulic clutches C1 to C3 and R are also OFF, and when it is in the forward movement area X, the first-speed hydraulic clutch C1 is ON and the reverse movement area Y
, The reverse hydraulic clutch R is turned on, and in the X and Y ranges, the HST corresponding to the position of the main shift lever 1
The trunnion of the type transmission H1 rotates, and the continuously variable transmission is performed.

The sub-transmission lever 7 can be switched between three stages for low-speed operation, high-speed operation, and traveling while traveling in a field.
When set to F2, F3 and R, the running speed is set according to the set position of the sub-transmission lever 7. When the HST transmission H1 is operated (the low-speed range hydraulic clutch A is ON, and the high-speed range hydraulic clutch B is OFF).
F), the main shift lever 1 is set every time the sub shift lever 7 is set.
Is performed continuously at a speed lower than the speed at the time of F1 or R setting.

Next, an embodiment relating to the improvement of the equalizer of the crawler traveling device in the combine will be described with reference to FIGS.
It will be explained in. Conventionally, in the crawler traveling device 10, one equalizer is attached near the center of the side surface so that the body smoothly travels on unevenness in the field. However, when there is one equalizer, there is a possibility that the machine center of gravity becomes unstable due to the inclination of the equalizer when riding on a convex surface or the like. In order to stabilize the center of gravity, it is conceivable to mount two equalizers. However, if the mounting method is not devised, the number of fixed wheels is reduced accordingly, resulting in frequent pitching during running.

Therefore, focusing on the crawler lug spacing and the movement of the equalizer based thereon, the equalizer is constructed as follows. That is, as shown in FIG. 6, the two equalizers 18 are arranged back and forth with respect to the center of gravity g of the fuselage. On the other hand, the pitch of the core metal 19a of the crawler 19 is p, the arbitrary integers are N and n, the pitch between both wheels of each equalizer 18 is (n + 0.5) p, and the rotation fulcrum of the two equalizers 18 is The pitch between them is (N + 0.5) p. That is, each pitch is shifted by a half pitch with respect to an integral multiple of the pitch of the crawler lugs 19a. With this configuration, as shown in FIG. 7 and FIG.
Since the engagement of the crawler core metal 19a in FIG. 8 is shifted by a half pitch, the inclination of the equalizer is reversed in the front and rear directions. In this case, one equalizer cancels the vibration of the other equalizer, so that pitching during running is eliminated.

Next, an embodiment of a belt disengagement prevention structure in a belt transmission mechanism will be described with reference to FIGS. The belt transmission mechanism is used to drive the input shaft of the axle drive device, the drive input shaft of the transfer device of the reaper, and the like via the belt from the engine drive shaft. The belt was lifted off the belt. However, when the drive shaft is still rotating, the pulley often floats around the loosened belt and comes off from the pulley, and it is very troublesome to re-attach the belt once removed to the pulley. It took. Therefore,
In the present embodiment, a belt presser is provided so as to suppress the loosening of the belt to a certain extent and to fix the belt at a fixed position when the tension clutch is released.

Referring to FIG. 9, the belt 20 is driven by the driven pulley 2 from the driving pulley 21 of the engine driving shaft.
When the belt is driven, a tension clutch 23 formed by pivotally supporting a tension roller 23b on a tension arm 23a is disposed at an ON position in the drawing to hold the belt 20. Note that a lifting arm 23c configured to lift the belt 20 from below is fixedly provided below the tension roller 23b from the tension arm 23a. Also, the driving pulley 2
Belt pressing portions 24 and 25 are provided around the outer sides of the first pulley 22 and the driven pulley 22, respectively, so that the belt does not float beyond a certain width from each pulley. Further, a belt presser 26 that presses the belt 20 from above when the tension clutch 23 is OFF is provided between the upper end of the belt presser 24 on the drive pulley 21 side on the belt winding side and the tension roller 23b. On the other hand, a belt holder 27 having an inverted U-shape is provided at the lower end as shown in FIG. 10 to prevent the belt 20 from coming off in the lateral direction.

In the belt transmission mechanism having the above-described structure, when the tension clutch 23 is lifted to the OFF position, the belt 20 is lifted upward, and is lifted from below by the lifting arm 23c of the tension clutch 23, and is moved to the vicinity thereof. Since the belt presser 26 presses the belt 20 from above, the detached belt 20 does not relax, and therefore, the belt does not twist around the pulleys 21 and 22. Further, the belt holding part 24.2
5 prevents the belt 20 from floating on the outer periphery of each pulley, and the belt presser 27 prevents the belt from coming off on both the left and right sides, so that the belt 20 does not come off when the tension clutch 23 is turned off. .

Finally, the turning operation mechanism of the auger 17 will be described. Conventionally, the auger swivel operation uses an auger swivel motor and a cross lever structure switch ON / OF.
F had done it. That is, when the lever is tilted back and forth, the switch for raising and lowering is turned on to raise or lower.
Then, when tilted left and right, the switch for turning left and right is turned on to turn left or right to drive the motor. According to this method, the operator at the steering unit cannot check the auger position even when looking at the lever on the switchboard, and must always look back and turn the switch ON / OFF while visually observing the auger position. Operation was difficult. Therefore, the turning operation is performed by a joystick lever, and the auger is automatically set at that position only by setting the lever to the target position.

Referring to FIG. 11, the operation shown in FIG.
An auger operation lever 28 of a joystick lever is provided in the direction unit 15 , and a detection signal of the lever position is input to the controller 30. An auger position detection sensor 29, which is a potentiometer, is attached to the auger 17 side, and an auger position detection signal from the sensor is input to the controller 30. Then, the controller 30 drives the auger turning motor M through the relay box 31 so that the auger position detected by the auger position detection sensor 29 matches the target position of the auger input by the auger operation lever 28. The output signal is transmitted. In this way, since the auger is set to the target position simply by setting the lever to the target position at the steering section, the labor for turning while checking the auger position one by one can be saved, and operability can be reduced. It will improve.

[0023]

As described above, the present invention has the following advantages. That is, the traveling transmission is
Since the HST type transmission is configured to operate in the low-speed range and the hydraulic clutch type transmission is configured to operate in the high-speed range, when working in the field with an agricultural machine equipped with the traveling transmission,
When working at low speeds, fine speed adjustment is possible, and safe and efficient work can be obtained. In addition, since the driving is performed in a low speed range, the inferior engine efficiency does not become a problem even in the HST type transmission. There is no need to increase the size of the engine.
In addition, even when a truck is loaded, fine speed adjustment on the step board is possible, so that safety of the worker is maintained and anxiety is eliminated. On the other hand, in the high speed range, the engine efficiency is good,
Since the hydraulic clutch type transmission H2 of the mechanical mechanism operates, efficiency and cost reduction can be realized. In this manner, a favorable traveling transmission that takes advantage of both transmissions and compensates for each other's disadvantages can be obtained.

[Brief description of the drawings]

FIG. 1 is an overall side view of a combine driven by a transmission according to the present invention.

FIG. 2 is a skeleton diagram of the transmission according to the present invention.

FIG. 3 is a hydraulic circuit diagram of the hydraulic clutch.

4 is a side view of the main transmission lever 1. FIG.

FIG. 5 is a plan view of a guide groove 2 showing a speed setting position of the main transmission lever 1.

FIG. 6 is a side view of the combine crawler traveling device.

FIG. 7 is a side view showing the movement of the equalizer 18;

FIG. 8 is a side view of the same.

FIG. 9 is a side view of the belt transmission mechanism that prevents the belt from being loosened when the clutch is switched.

FIG. 10 is a sectional view taken along the line ZZ in FIG. 9;

FIG. 11 is a block diagram showing an auger turning operation mechanism of the combine.

[Description of References] H Travel transmission H1 HST transmission H2 Hydraulic clutch transmission MC Transmission cases A, B, C1, C2, C3, R Hydraulic clutch 1 Main transmission lever 2 Guide groove 3 Transmission cam 4 Transmission rod 5 Operation arm 6 Low speed range shifting rod 9 Axle

──────────────────────────────────────────────────続 き Continuation of the front page (72) Inventor Hideaki Noguchi 428 Enami, Okayama City Inside of Seirai Industry Co., Ltd. (56) References JP-A-52-97519 (JP, A) JP-A-52-109228 (JP, A) JP-A-53-87431 (JP, A) JP-A-59-93558 (JP, A) Japanese Patent Publication No. Sho 53-16750 (JP, B1) Jikken Sho 61-2098 (JP, Y1) (58) Survey Field (Int.Cl. ⁷ , DB name) F16H 47/02 F16H 61/02 F16H 59:06

Claims (1)

(57) [Claims] 1. A low-speed drive for operating an HST transmission (H1).
Speed range hydraulic clutch (A) and hydraulic clutch type transmission
Switching high-speed range hydraulic clutch (B) for (H2) operation
Transmission switching valve (V1)
Speed switching for switching the shift position of the latch type transmission (H2)
A transmission valve (V2);
(V1), speed switching valve (V2), and HST shift
Main operation for operating the trunnion for continuously variable transmission of the device (H1)
Speed lever (1) is provided, and the main shift lever (1)
When it is in the speed range, it is changed by the HST transmission (H1).
If it is on the high-speed side other than the low-speed range,
For changing gears to change gears by H-type gearbox (H2)
The valve (V1) is configured to be switched and the high-speed side
The low-speed range hydraulic clutch (A) is OFF,
The speed range hydraulic clutch (B) is turned on, and the hydraulic clutch type
Hydraulic clutch (C1) (C2) (C
3) Either of (R) is turned ON and at low speed side
Indicates that the low-speed range hydraulic clutch (A) is ON and the high-speed range hydraulic pressure
The clutch (B) is turned off, and within that, the forward constant speed range
(X), the first-speed hydraulic clutch (C1) is
N, reverse hydraulic clutch when in reverse body side area (Y)
(R) is turned on, and at the same time, the
In response, the trunnion of the HST transmission (H1) is turned.
A continuously variable transmission .