JPS6048362B2 - Transmission devices for agricultural vehicles, etc. - Google Patents

Description

[Detailed Description of the Invention] (a) Industrial Application Field The present invention is a transmission device for an agricultural mobile vehicle, such as a combine harvester, which performs reaping and threshing operations while traveling on a crawler-type traveling device in soft ground such as paddy fields. It is related to.

(B) Prior Art Techniques related to hydraulic clutch type transmissions that change gears by selectively engaging a plurality of hydraulic clutch devices have been known as transmission devices for mobile vehicles and the like.

For example, Japanese Patent Application Laid-Open No. 47-21834 is available.

However, in the case of the known technique disclosed in JP-A No. 47-21834, in order to enable interlining rotation, the left and right traveling output shafts are shifted by completely different transmission systems, so a hydraulic clutch device is used. Even though eight sets are used, it is possible to rotate the interlining, but only four speeds in total, two forward and two forward speeds, can be changed. In addition, four sets of hydraulic clutch devices must be connected at all times during running, making the configuration of the directional control valve, hydraulic pump device, etc. complicated, large-capacity, and expensive. (■→ Problems to be Solved by the Invention The present invention solves the problems of the conventional known technology, minimizes the number of hydraulic clutch devices, and selectively engages one set of hydraulic clutch devices to achieve forward and backward movement. The configuration is such that it is possible to select the forward gear position and the forward gear position.

This simplifies the structure of the directional control valve, requires a small capacity of the hydraulic pump device, and simplifies the structure of the transmission. In addition, interlining rotation such as that used in construction mechanisms cannot be used in mobile vehicles for paddy fields, such as combines, because there is a risk of making holes in the tiller. Instead, a side clutch device is installed at the bottom of the hydraulic clutch type transmission. A steering shaft equipped with a handbrake device was installed to enable reliable steering and quick gear changes in rice fields.

(-d) Means for Solving the Problems The objects of the present invention are as described above. Next, the structure for achieving the objects will be explained.

Inside the mission case 28, a first intermediate shaft B and a second intermediate shaft C are arranged at two vertices of the base of a substantially isosceles Ξ-gon whose apex is the transmission input shaft A interlockingly connected to the engine 16; A plurality of sets of hydraulic clutch devices are arranged on the first intermediate shaft B and the second intermediate shaft C, respectively, and the drive side of each hydraulic clutch device is always in a transmission state with the speed change input shaft A, and the hydraulic clutch device By selectively coupling one set of them, multi-stage gear shifting for forward and backward movement is possible.
The transmission output shaft D is arranged at the apex of a substantially isosceles Ξ-gon with the intermediate shaft C as the apex of the base, and the gears on the first intermediate shaft B and the second intermediate shaft C and the gears on the transmission output shaft D are connected to each other. meshing, and selective coupling of one set of the plurality of hydraulic clutch devices h on both shafts. The steering shafts 50L, 5 which support side clutches 19, 20 and side brakes 26, 27 are arranged on the lower side of the transmission system of the transmission output shaft D.
0R is arranged and the rotation of the speed change output shaft D is controlled by the steering shafts 50L and 50.
Teeth fitted onto the butt part of R. The power is transmitted to the car 18.

(E) Embodiments and Functions The following is a detailed explanation based on the embodiments shown in the drawings.

The power transmission system diagram shown in FIG. 1 shows the case where the present invention is implemented in a transmission mounted on a combine harvester.
Power is input from the engine 16 through the drive pulley 13, belt 14 and driven pulley 15, and is transmitted from the gear 17 on the speed change output shaft D to the gear 18 on the left and right abutting portions of the steering shafts 50L and 50R. , then left side clutch 1
9 and the sliding of the right side clutch 20, power is connected and disconnected, and the power is transmitted to the left traveling output shaft 22, which is transmitted to the left driving sprocket 21, and the right traveling output shaft 24, which is transmitted to the right driving sprocket 23. ing.

Additionally, side brakes 26 and 27 are arranged on the outer ends of the steering shafts 50L and 50R to apply braking to the left and right separately when the steering by the side clutches 19 and 20 is insufficient.

25 is a parking brake provided on the second intermediate shaft C.

Transmission is transmitted between the main shaft E and the speed input shaft A of the transmission through a gear-type sub-transmission N, and a main clutch 29 is interposed between the driven pulley 15 and the main shaft E, so that the speed of the speed change input shaft A can be freely changed. shall be.

The hydraulic clutch type main transmission M has a transmission case 28 horizontally supporting a transmission input shaft A) a first intermediate shaft B) a second intermediate shaft C) a transmission output shaft D, etc., and positions the transmission case 28 so that the shafts are oriented horizontally. and is fixed to the chassis of the combine harvester.

A first fixed gear 9 and a second fixed gear 9' are fixed to the speed change input shaft A, and a first hydraulic clutch 1, a first loose gear 5, a third hydraulic clutch 3, and a third hydraulic clutch are fixed to the first intermediate shaft B. The loose-fit gear 7 and the fifth gear 10 are fixed, and the second hydraulic clutch 2, the second loose-fit gear 6, the fourth hydraulic clutch 4, the fourth loose-fit gear 8, and the sixth gear 11 are connected to the second intermediate shaft C. The output gear 12 is fixed to the speed change output shaft D.

The first fixed gear 9 meshes with the first loose-fit gear 5 and the second loose-fit gear 6, the second fixed gear 9' meshes with the third loose-fit gear 7, and the third loose-fit gear 7 In particular, it also meshes with the fourth loose fit gear 8 for reverse movement.

That is, the fourth loosely fitted gear of the fourth hydraulic clutch 4 for reverse does not mesh with the second fixed gear 9', but engages with the third loosely fitted gear 7 for the third forward speed on the first intermediate shaft B. They are always in mesh, and the third loosely fitted gear 7 also serves as a reverse gear. First,
The loosely fitted gears 5, 6, and 7 of the second and third hydraulic clutches are always engaged with the first fixed gear 9 or the second fixed gear 9' on the speed change input shaft A, and the fourth hydraulic clutch is used only for reverse movement. Only the fourth loose-fitting gear 8 of No. 4 is always meshed with the third loose-fitting gear 7 of the third hydraulic clutch 3, and is always in a transmission state with the speed change input shaft A.

The output gear 12 fixed to the speed change output shaft D is meshed with the fifth gear 10 fixed to the first intermediate shaft B and the sixth gear 11 fixed to the second intermediate shaft C, and the hydraulic clutches H2, 3 are engaged.
, 4 by choice i selection combination. The rotation after the gear change that could be
Transmission is always maintained from the intermediate shaft B and the second intermediate shaft C to the variable speed output shaft D. Therefore, in the first forward speed, the first hydraulic clutch 1
When activated, the transmission is transmitted from the transmission input shaft A through the first fixed gear 9, from the first loose gear 5 through the first hydraulic clutch 1, through the first intermediate shaft B, the fifth gear 10) and the output gear 12. The first forward speed is transmitted to the speed change output shaft D. For the second forward speed, when the second hydraulic clutch 2 is operated, the first fixed gear 9,
The transmission is transmitted to the second intermediate shaft C via the second loose-fit gear 6 and the second hydraulic clutch 2, and the second forward speed is transmitted to the variable speed output shaft D via the sixth gear 11 and the output gear 12. For the third forward speed, when the third hydraulic clutch 3 is engaged, the second fixed gear 9' and the third
The three forward speeds are transmitted to the first intermediate shaft B via the loose fit gear 7 and the third hydraulic clutch 3, and then to the variable speed output shaft D via the fifth gear 10 and the output gear 12.

When the fourth hydraulic clutch 4 is engaged, the reverse speed is determined by the second intermediate shaft C via the second fixed gear 9', the third loose-fit gear 7, the fourth loose-fit gear 8, and the fourth hydraulic clutch 4. The output shaft D is rotated in the opposite direction, and the speed change output shaft D is rotated in the opposite direction via the sixth gear IL output gear 12.

Figure 3 shows the four hydraulic clutches 1, 2, 3, and
4, 30 is an oil tank, 31 is a strainer, 32 is a hydraulic pump device, 33 is a relief valve, 34 is a first directional control valve, 35 is a second directional control valve, 36 is an oil tank. In the position shown in FIG. 3, the first directional control valve 34 is in a neutral position by connecting HO and H6 and making all hydraulic clutches inactive, and when moved in the P1 direction, it connects H4 and HO in sequence. When the fourth hydraulic clutch 4 is actuated and the vehicle is moved to the reverse position, and the vehicle is moved in the P2 direction, H5 and HO are communicated to supply hydraulic pressure to the second direction control valve 35, and the vehicle is located in the forward position.

The second direction control valve 35 is in the position shown in FIG.
5 and H3 are communicated to operate the third hydraulic clutch 3 to reach the 3rd forward speed position, and when moved in the Q2 direction, H5 and H2 are communicated to operate the 2nd hydraulic clutch 2 and the position is to the 2nd forward speed position. Therefore, when moving in the Q1 direction, H5 and H1
The first hydraulic clutch 1 is activated by communicating with the first hydraulic clutch 1, and the first forward speed position is established. Therefore, by moving the first direction control valve 34, switching between forward, neutral, and reverse is performed, and the first direction control valve 34
Only in the forward position, switching between 1st forward speed, 2nd forward speed, and 3rd forward speed is possible by moving the second directional control valve 35.

4 and 5 show a combine harvester equipped with the horizontal shaft transmission of the present invention, 37 is a reaping device, 38 is a threshing device, 3
Numeral 9 is a grain case, 40 is a seat, 41 is a crawler type traveling device, and 42 is a horizontal shaft transmission device implementing the present invention.
Operating speed, traveling speed, direction of travel, etc. can be changed with simple operations according to field conditions and crop conditions, making the combine harvester extremely easy to operate.

(Effects of the Invention) Since the present invention is configured as described above, it has the following effects.

First, if the left and right travel output shafts are configured to be shifted by completely different hydraulic clutch type transmission systems, as in the conventional technique disclosed in JP-A No. 47-21834, interlining rotation becomes possible. However, the number of hydraulic clutch devices increases, and unless four sets of hydraulic clutch devices are connected at all times, the crawler type traveling device cannot be shifted forward or backward, and the capacity of the hydraulic pump device becomes large. The direction control valve also requires selection and switching of four sets of hydraulic clutch devices at the same time, making it complicated.

In contrast, in the case of the present invention, speed changes including reverse speed changes are performed by selecting one of a pair of hydraulic clutch devices on the first intermediate shaft B and the second intermediate shaft C. This makes it possible to construct a hydraulic clutch type transmission with a simple structure.

Second, on the lower side of the transmission system of the first intermediate shaft B and the second intermediate shaft C, there is a position of the apex of a substantially isosceles Ξ-gon with the first intermediate shaft B and the second intermediate shaft C as the vertices of the base. , the gears on the first intermediate shaft B and the second intermediate shaft C are meshed with the gears on the transmission output shaft D, and one set of the plurality of hydraulic clutch devices on both shafts is arranged. Since the forward/reverse speed change rotation obtained by the selective combination of is collected on the speed change output shaft D, up to the speed change output shaft D,
The transmission system can also be used, the number of hydraulic clutch devices can be reduced, and the configurations of the hydraulic pump device and the directional control valve device can be simplified.

Third, steering shafts 50L and 50R supporting the side clutches 19 and 20 and hand brakes 26 and 27 are arranged on the lower side of the transmission system of the speed change output shaft D, and the rotation of the speed change output shaft D is controlled by the steering shafts 50L and 50R. Gear 1 fitted on the butt part of 50R
8, the power can be divided from the steering shaft to the left and right travel output shafts, and by providing side clutches 19, 20 and side brakes 26, 27 on the steering shaft, it is possible to If the engine speed drops due to the muddy resistance of the crawler-type traveling device and sufficient steering operation is possible, the hydraulic clutch-type transmission immediately lowers the gear to try to get out of the way and prevent the engine from stalling. It can be avoided.

[Brief explanation of the drawing]

FIG. 1 is a power transmission system diagram of the transmission of the present invention, FIG. 2 is a side sectional view of the same transmission, FIG. 3 is an operating hydraulic circuit diagram, and FIG. 4 is a side view of a combine harvester implementing the present invention. Fifth
The figure is also a plan view.

Claims (1)

[Claims] 1. Inside the mission case 28, a first intermediate shaft B and a second intermediate shaft C are arranged at two vertices of the base of a substantially isosceles triangle whose vertices are the transmission input shaft A interlockingly connected to the engine 16; A plurality of sets of hydraulic clutch devices are arranged on the first intermediate shaft B and the second intermediate shaft C, respectively, and the drive side of each hydraulic clutch device is always in a transmission state with the speed change input shaft A,
By selectively coupling one set of the hydraulic clutch devices, multi-stage gear shifting for forward and backward movement is possible. The speed change output shaft D is arranged at the apex of a substantially isosceles triangle with the second intermediate shaft C as the apex of the base, and the gears on the first intermediate shaft B and the second intermediate shaft C and the gears on the speed change output shaft D are arranged. The transmission rotation obtained by selectively engaging one set of the plurality of hydraulic clutch devices on both shafts is collected on the transmission output shaft D, and a side clutch 19, 20
and a steering shaft 50L supporting handbrakes 26 and 27,
50R is arranged and the rotation of the speed change output shaft D is controlled by the steering shaft 50L, 5.
A transmission device for an agricultural vehicle, etc., characterized in that transmission is transmitted to a gear 18 fitted on a butt portion of an 0R.