JPS60128024A - Transmission - Google Patents

Abstract

PURPOSE:To dispense with the disengaging operation of a main clutch even in case of operation on an auxiliary transmission as well as to make this auxiliary transmission operation attainable in the neutral state of a main transmission, by setting up a hydraulic clutch type main transmission at an upper stage and a gear slide type auxiliary transmission at a lower stage separately. CONSTITUTION:Each of hydraulic clutch shafts 2, 3 and 4 pivotally supporting a hydraulic clutch unit is set up in and around an input shaft 1 being projected out of a transmission case 9, while each of locking gears 24, 25 and 70 is tightly installed on top of the input shaft 1. The gear 25 engages each of input fitting gears 29, 30 and 35 at all times, while other input fitting gears 31 and 53 are engaged with the gear 70, thereby making this gear 70 perform main transmission shifting. An auxiliary transmission is constituted between a sliding gear shaft 5 and a counter shaft 6, and a small diametral gear 37 between two-throw sliding gears 38 and 37 on the shaft 5 engages a large diametral one and 40 between two-throw gears 39 and 40 on the counter shaft 6 whereby auxiliary transmission low is secured and with these gears 38 and 39 engaged with each other, auxiliary transmission high is secured, respectively.

Description

DETAILED DESCRIPTION OF THE INVENTION (a) Field of Industrial Application The present invention relates to a transmission device for a mobile vehicle having a crawler type traveling device, such as a combine harvester or a small construction machine.

(B) Prior art The applicant has previously applied for hydraulic clutch type transmissions, but most of them have a gear sliding type auxiliary transmission in the upper stage of the hydraulic clutch type main transmission. It was placed in

Therefore, when performing a sub-shift, it was necessary to disconnect the main clutch device between the engine and the transmission case, and then perform the sub-shift operation. □ However, the advantage of a hydraulic clutch type transmission is that it can change gears without engaging or disconnecting the main clutch device, whereas the gear sliding type sub-shift requires disconnecting the main clutch device. It was a hassle to have to deal with them.

(c) Problems to be Solved by the Invention An object of the present invention is to provide a transmission that includes a hydraulic clutch type main transmission and a gear sliding type auxiliary transmission. This is a modification of the conventional transmission so that the main transmission and auxiliary transmission levers can be operated with a single lever without operating the main clutch. The gear skeleton is configured so that the relationship is reversed and the gear sliding type auxiliary transmission is placed in the lower stage.

In order to enable the sliding gear to slide left and right, especially near the center of the transmission case, the hydraulic clutch device and the input loose gear are made small in diameter, and the output gear near the end of the Mitsushiran case is made large in diameter. It is.

B) Means for Solving the Problems The objects of the present invention are as described above, and the configuration for achieving the objects will now be explained.

A plurality of fixed gears are arranged on the input shaft 1 of the mission case 9, and two sets of hydraulic clutch devices and input loose gears are provided on the plurality of hydraulic clutch shafts arranged around the input shaft 1. , the input loose gear is meshed with one of the fixed gears, and by selectively coupling these hydraulic clutch devices, multiple main speeds including reverse are performed, and the output gear of the hydraulic clutch shaft is Input gear 36 on sliding gear shaft 5 for sub-transmission
, and a sub-shift is performed between the sliding gear on the sliding gear shaft 5 and the fixed gear on the counter shaft 6 below the hydraulic clutch device.

(E) Embodiments and Functions The objects and structure of the present invention are as described above, and the present invention will be explained in detail based on the structure of the embodiments shown in the attached drawings.

FIG. 1 is an overall side view of a combine harvester equipped with a crawler type traveling device.

Although the transmission device of the present invention is mainly a crawler-type traveling device, it is not limited thereto, and can be used in two types such as a tiller, etc.
It is also used in ring-shaped mobile vehicles.

The transmission device in the mission case 9 that drives the crawler-type traveling device 18 with the drive sprocket 10 is the main part of the present invention, and the drive sprocket 10 is attached to the left and right drive shafts 8L and 8R that protrude on both sides of the mission case 9. It is permanently installed.

Each piece of equipment in a combine harvester is mounted on a crawler-type traveling device. A grass dividing plate 13 protrudes from the tip, and after the grass is divided by the grass dividing plate 13, the lodging culm is raised by a pulling device 12. At the same time, the reaping device 15 harvests the stock base, and the stock base transport device 14 transports the stock to a lower level of the vertical transport device 16.

The length of the culm is adjusted by the vertical conveyance device 16, and then transferred to the feed chain 27 of the threshing device 19. The tip of the ear is transferred to the upper conveying device 2.
At step 3, the grains are transported to the inlet of the handling drum of the threshing device 19. The husks are threshed in the threshing device 19, and the waste culms are conveyed to the waste culm processing device 21 by the culm removal chain for processing.

Fig. 2 is a sectional view of the inside of the mission case 9 showing the main parts of the present invention, Fig. 3 is a transmission line diagram, and Fig. 4 is a cormorant miss. FIG. 1 is a drawing showing the arrangement of the shafts of the four case 9, and FIG.

An input pulley 62 is provided at the end of the input shaft l protruding from the upper part of the mission case 9.
Power is transmitted from the engine to 62 by a V-belt.

As shown in FIG. 4, hydraulic clutch shafts 2, 3, and 4 for supporting a hydraulic clutch device are arranged around the input shaft l. Three fixed gears 24, 25, and 70 are fixedly installed on the input shaft 1, and are constantly meshed with the gears of the hydraulic clutch device on the hydraulic clutch shafts 2, 3, and 4. First, the small-diameter fixed gear 25 on the input shaft has an input fitted gear 29 of the hydraulic clutch device 47 on the hydraulic clutch shaft 2 and an input loosely fitted gear 30 of the hydraulic clutch device 49 on the hydraulic clutch shaft 3. and,
A gear with the same number of teeth as the input loose fit gear 35 of the hydraulic clutch device 51 on the hydraulic clutch shaft 4 is always in mesh.

There is.

Moreover, the fixed gear 70 of the middle diameter on the input shaft 1 is the same as the input fitting gear 31 of the hydraulic clutch device 50 of the hydraulic clutch shaft 3 and the input fitting gear 53 of the hydraulic clutch device 52 of the hydraulic clutch shaft 4. Two gears with the same number of teeth are always in mesh.

Therefore, no matter which hydraulic clutch device 47, 49, or 51 on the hydraulic clutch shafts 2, 3, or 4 is connected, the rotation will be the same, and similarly, even if the hydraulic clutch device 50 or 52 is connected, the rotation speed will be the same. rotation in the same direction. However, the input rotation to the hydraulic latch device 48 on the hydraulic clutch shaft 2 is particularly fast. Among the three fixed gears on the input shaft 1, only one large-diameter fixed gear 24 is always engaged with the input loose gear 28 of the hydraulic clutch device 48, and among the six hydraulic clutch devices, It is designed for particularly fast rotation. This hydraulic clutch device obtains the speed of the fourth forward speed, which is the speed shown in drawings F4 and F8 in FIG.

For F4, Fl is 1.080km/h, F2 is 1.37
9km/h, F3's 1.892km/h, while 5.227km/h and F3's 2.720km/h.
The F8 is configured to a speed of more than h, and the F5 is 1.731 km.
/h, F6 is 2.210km/h, Fl is 3.
The speed is 8.380km/h, which is more than twice the speed of 0.033km+/h.

Fl, F2, and F3 are the speeds for reaping work, and F4 is the speed for stopping the reaping work and traveling.

Therefore, there is no need to change the groove using the speed change lever when moving from reaping work to traveling work, and the work can be performed by only reciprocating one groove in the front and back direction.

Other output gears 26, 32, 33, and 34 of hydraulic clutch shafts 2, 3, and 4 change the forward, reverse, and gear stages.
It is.

First, the output gear 32 of the hydraulic clutch shaft 3 is always engaged with the output gear 33 on the hydraulic clutch shaft 4, so when rotation is not transmitted to the hydraulic clutch shaft 5, the hydraulic clutch shaft 4 acts as a reverse rotation shaft. However, the hydraulic clutch device on the hydraulic clutch shaft 3 is in the first reverse speed and the second reverse speed. That is, the output gears 33 and 34 also serve as reverse idling gears.

Further, the output gear 26 on the hydraulic clutch shaft 2 is connected to the sliding gear shaft 5.
The output gear 34 on the hydraulic clutch shaft 4 is also always in mesh with the input gear 36 on the sliding gear shaft 5, but since the gear 26 is thicker and the gear 34 is smaller, the hydraulic The hydraulic clutch devices 47 and 48 on the clutch shaft 2 are in the second forward speed and the fourth speed, and the hydraulic clutch devices 51 and 52 on the hydraulic clutch shaft 4 are in the first and third forward speed.

The first forward speed is transmitted from the fixed gear 25 of the input shaft 1 to the input loose gear 35 on the hydraulic clutch shaft 4, and by connecting the hydraulic clutch device 51, the output gear 34 is transmitted to the fixed gear 35 on the sliding gear shaft 5. The signal is transmitted to the gear 36.

The second forward speed is transmitted from the fixed gear 25 on the input shaft 1 to the input loose gear 29 on the hydraulic clutch shaft 2, and is transmitted from the output gear 26 to the input gear on the sliding gear shaft 5 by connection to the hydraulic clutch device 47. It is transmitted to 36.

The third forward speed is transmitted from the fixed gear 70 on the input shaft 1 to the input loose fit gear 53 on the hydraulic clutch shaft 4, and by the connection of the hydraulic clutch device 52, from the output gear 34 to the input gear on the sliding gear shaft 5. This will be communicated to 36.

The fourth forward speed is transmitted from the fixed gear 24 on the input shaft 1 to the input loose gear 28 on the hydraulic clutch shaft, and by the connection of the hydraulic clutch device 48, the output gear 26 is transmitted to the input gear on the sliding gear shaft 5. This will be communicated to 36.

The reverse first speed is transmitted from the fixed gear 25 on the input shaft 1 to the input loose gear 30 on the hydraulic clutch shaft 3, and the output gear 3 on the hydraulic clutch shaft 3 is transmitted by the hydraulic clutch device 49.
2 to the fixed gear 36 on the hydraulic clutch shaft 5 via the output gears 33 and 34 on the hydraulic clutch shaft 4. The output gears 33 and 34 on the hydraulic clutch shaft 4 also serve as idling gears for reverse movement.

The second reverse speed is transmitted from the fixed gear 70 on the input shaft 1 to the input loose gear 31 on the hydraulic clutch shaft 3, and is transmitted to the output gear 3 on the hydraulic clutch shaft 3 by connection of the hydraulic clutch device 50.
2 is transmitted via the output gears 33 and 34 on the hydraulic clutch shaft 4 to the input gear 36 on the sliding gear shaft 5. Similarly, the output gears 33 and 34 on the hydraulic clutch shaft 4 also serve as idling gears for reverse movement.

Next, a sub-transmission device is constructed between the sliding gear shaft 5 and the counter shaft 6.

By meshing the smaller diameter gear 37 of the twin sliding gears 38 and 37 on the sliding gear shaft 5 with the larger diameter one and 40 of the twin gears 39 and 40 on the counter shaft, a low sub-shift is obtained. When 38 and 39 mesh with each other, a sub-shift height is obtained.

Due to the low sub-shift, 2 reverse speeds and 4 forward speeds, namely R1, R2,
Variable lotus gears of pt-p□2, F3, and F4 are obtained, and R3-R4, F5, F6, Fl, and F8 are obtained depending on the sub-shift height.

The height of this sub-shift is determined by rotating the shift lever 22 left and right to slide the double sliding gears 37 and 38.
If the hydraulic directional control valve is moved by the forward and backward rotation of 2 to select the oil passages of the six hydraulic clutch devices, the speed change guide plate can be configured in an H shape as shown in FIG. When the sub-shift has 3 speeds, it becomes M-type, and when it has 4-speed, it becomes H-type.

On the counter shaft are hydraulic cylinders 61L and 611 for the left and right hydraulic steering clutch devices and hydraulic brake devices. A steering clutch is constructed by sliding the sliding gears 45L and 45R to engage and disengage the internal gears 44L and 44R.

The sliding gears 45L and 45R also serve as holders for the friction plates of the disc brake device, and the hydraulic cylinders 61L and 6
Due to the overlapping lateral movement of 1R, the steering brake devices 46L and 46R gradually operate after the steering clutch is disengaged. 5
4 is a parking brake device.

On the seventh shaft 7, left and right reduction gear devices 41L, 41R,
42L and 42R are provided, and mesh with final gears 43L and 43R on the eighth shaft 8, which is a drive shaft.

As shown in FIG. 4, hydraulic clutch shafts 2, 3, and 4 are arranged around the input shaft 1, and the gear on the hydraulic clutch shaft 3 meshes with the gear on the input shaft 1 and the hydraulic clutch shaft 4. are doing. The gear on the sliding gear shaft 5 is in a position to mesh with the gears on the hydraulic clutch shaft 4 and the hydraulic clutch shaft 2.

Figure 5 shows a configuration in which the main gear shift and the auxiliary gear shift can be steered with one lever; in a combine harvester, the steering column 17
2 shows a plan view of the speed change guide plate 63 on the side.

If configured in an H-shape with 2201 gear shift levers, it is possible to shift 8 forward gears and 4 reverse gears without operating the main clutch, and if the auxiliary gear is set to 3 gears, it is possible to shift to 12 forward gears and 6 reverse gears. By setting the auxiliary gear to 4 gears and making it H-shaped, 16 forward gears and 8 reverse gears can be achieved without operating the main clutch.

In each of the main transmission grooves in the longitudinal direction, the fastest speed portion is configured to have a running speed that is more than twice as fast as the working speed constituted by the other forward speeds, so the six other main transmissions during traveling are There is no need to move to the ditch and increase the speed with the help of a sub-shift; all you have to do is select the main gear shifting groove in the longitudinal direction, depending on the field conditions, and the rest is done by simply operating the gear shift lever in the longitudinal direction. can be done.

For example, the main transmission groove can be used differently for wet fields and dry fields, or the main transmission groove can be selected depending on the maturity of the culm, the wetness after rain, etc.

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

First, the hydraulic clutch type main transmission is placed in the upper stage and the gear sliding type auxiliary transmission is placed in the lower stage, so there is no need to engage or disconnect the main clutch even when operating the auxiliary transmission. The sub-shift operation can be performed when the device is in the neutral state.

Second, by configuring the sub-shift to be performed only at the neutral position of the main shift, the shift guide plate can be set in an H-shape or H-shape.
If it is a type 1 or H type, it becomes possible to perform the main gear shift and the sub gear shift with a single operation.

3

[Brief explanation of the drawing]

Figure 1 is an overall side view of a combine harvester, which is a mobile vehicle with a crawler-type traveling device. Fig. 2 is a sectional view of the Mitsushiran case, Fig. 3 is a transmission line diagram of the transmission of the present invention, Fig. 4 is a side view of the Mitsushiran case showing the arrangement of the shafts, and Fig. 5
The figure is a plan view of the speed change guide plate. 1...Input shaft 2.3.4...Hydraulic clutch shaft 5.
...Sliding gear 6...Counter shaft 9...Mitsushiran case 24, 25, 70...Fixed gears 26, 32 on the input shaft
・33・34...Output gears 28 and 2 of the hydraulic clutch shaft
9, 30, 31, 35, 53... Input loose gear of hydraulic clutch device 36... Input gear of sliding gear shaft 38, 37... Dual sliding gear 47, 48, 49, 50... 51・52...Hydraulic clutch device applicant Kanzaki Kokyukoki Seisakusho Co., Ltd. Agent Patent attorney Hisashi Yano -Department 4 ■ ■ -148-

Claims (1)

[Claims] A plurality of fixed gears are arranged on the input shaft 1 of the mission case 9, and two sets of hydraulic clutch devices and input loose gears are provided on the plurality of hydraulic clutch shafts arranged around the input shaft 1. , the input loose gear is meshed with one of the fixed gears, and by selectively coupling these hydraulic clutch devices, multiple main speeds including reverse are performed, and the output gear of the hydraulic clutch shaft is Input gear 36 on sliding gear shaft 5 for sub-transmission
A transmission device characterized in that a sub-shift is performed between a sliding gear on a sliding gear shaft 5 and a fixed gear on a counter shaft 6 below the hydraulic clutch device.