JPH0245058B2 - - Google Patents

Description

[Detailed description of the invention] (a) Industrial application field The present invention is applicable to agricultural machinery and construction and civil engineering machinery, which require various speed stages for working speeds, and which require the user to change gears and change forward and backward many times during work. This relates to a transmission system for a traveling work vehicle that requires repeating the same procedure.

(b) Conventional technology The technology of arranging 6 hydraulic clutches in parallel to shift gears into 4 forward gears and 2 reverse gears was developed in the early 19th century.
52-37174 is known to the public,
In addition, the technique of changing the rotation speed after shifting to three forward speeds and one reverse speed in the first stage and high and low speeds in the second stage is also known in Japanese Patent Application Laid-Open No. 54-153957. The technology to further shift into multiple gears in the rear gear was developed in 1982.
A technique such as that disclosed in Japanese Patent No. 90539 is known.

(c) Problems to be solved by the invention However, in the technology described in the above-mentioned Utility Model Application Publication No. 52-37174, six hydraulic clutches are used to obtain six speeds, four forward speeds and two reverse speeds. Therefore, the number of oil passages to be machined increases accordingly.

In addition, since the power is distributed from one input shaft to both the first forward clutch shaft and the second forward clutch shaft, the reduction ratio and gear arrangement must be determined so that the gears on each shaft do not interfere with each other, making it complicated. There was a problem with this.

In addition, three small output gears are fixed on each shaft of the first forward clutch shaft, second forward clutch shaft, and reverse clutch shaft, and these are meshed with one large gear.
There was also the problem that the position of the output shaft was determined.

For the above reasons, the technology described in Utility Model Application Publication No. 52-37174 has a large number of hydraulic clutches and a narrow range of gear ratios, resulting in less freedom in design.
It had a two-speed transmission, reverse and reverse.

Furthermore, in the technology described in Japanese Patent Application Laid-Open No. 54-153957, the front gear changes forward and backward gears, and the rear gear changes height and low gears, and a reverse gear shaft and reverse gear are separately provided to obtain the reverse gear in the front gear. The need arose.

Also, in the technology described in Japanese Utility Model Application Publication No. 56-90539, the front gear performs forward/reverse shifting and the rear gear performs high/low gear shifting, so a reverse gear shaft and a reverse gear are required in the front gear to obtain reverse speed. There was a problem.

The present invention solves these conventional problems.

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

Input shaft 15 and height change shaft 16 connected to the prime mover
The forward rotation shaft 17, the reverse rotation shaft 18, and the output shaft 19 are horizontally mounted in parallel with each other, two gears 30, 33 are fixed on the input shaft 15, and the gears 30, 33 are attached to the height change shaft 16. meshing the two gears 35 and 36,
The gears 35 and 36 can be loosely fitted and fixed to the height change shaft 16 via the hydraulic clutches 23 and 24, and the two gears 34 and 37 are mounted on the height change shaft 16.
The gears 34 and 37 are fixed on the normal rotation shaft 17.
The gears 38, 40 are meshed with each other.
0 to the forward rotation shaft 17 via hydraulic clutches 25 and 26.
The normal rotation shaft 17 can be loosely fitted and fixed on the
A small output gear 39 is fixedly installed on the top, and the small output gear 39
A gear 42 is provided on the reverse rotation shaft 18, which meshes with the large gear 44a on the output shaft 19, and meshes with one of the loosely fitted gears 38, 40 on the forward rotation shaft 17.
is loosely fitted to the reversing shaft 18 via the hydraulic clutch 27.
A small output gear 4 is provided on the reversing shaft 18 and meshes with the large gear 44a on the output shaft 19.
1, and a hydraulic clutch 2 on the height/low speed change shaft 16.
3, 24 and any one of the hydraulic clutches 25, 26, 27 on the forward rotation shaft 17 and the reverse rotation shaft 18 selectively and simultaneously. After the rotation has been shifted high and low on the height change shaft 16, the forward rotation shaft 17 is also used as a reverse gear shaft, and the rotation is further changed to two forward speeds and one reverse speed.

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

FIG. 1 is an overall side view of a combine harvester among agricultural machines.

After the grain rod is raised by the lifting device 3 and the stock part is cut off, it is transferred to the feed chain 8 of the threshing device 9 by the grain transport device 4, and with the stock part being held between the feed chain 8. , the tip of the ear is inserted into the handling barrel and threshed. The waste culm after threshing is guided to a removal rod processing device 11 through a removal rod chain 10.

Each of these devices is mounted on a crawler-type traveling device, and a transmission device in a transmission case A drives a driving sprocket 2 to drive a crawler device 1.

A shift lever 7 for shifting the first and second hydraulic clutch type transmissions of the transmission case A is protruded above the shift guide plate 6, and is located at a position where the operator on the seat 12 can operate it with his/her left hand. ing. 5 is a control column provided with left and right steering clutch levers, etc.

FIG. 2 is a skeleton diagram of the transmission of the present invention;
FIG. 3 is a side view of the mission case A.

A hydraulic control valve B is placed on the upper processed surface of the transmission case A, and a speed change lever 7 for moving a spool of the hydraulic control valve B also protrudes from there. In the transmission case A, the axes of an input shaft 15, a height change shaft 16, a forward rotation shaft 17, and a reverse rotation shaft 18 are provided in a stepped manner between the pulley shaft 14 and the output shaft 19.

An input V-pulley 2 is attached to one end of the pulley shaft 14.
2 is fixedly installed, and power is transmitted from the engine via a V-belt. A hydraulic pump 13 is fixed to the other end of the pulley shaft 14, and sucks lubricating oil from the transmission case A and supplies it to the hydraulic clutch as pressure oil. A gear sliding type transmission is constructed between the two sliding gears 28a, 28b and internal and external gears 29b, 29a on the pulley shaft 14 and the fixed gears 31, 32, 33 on the shaft 15.

Gear 28b and gear 33 mesh to obtain a low speed of the gear sliding type transmission, gear 28a and gear 32 mesh to obtain a medium speed of the gear sliding type transmission,
Gear 28a meshes with inner gear 29b, and outer gear 29
Since a is meshed with the gear 31, the high speed of the gear sliding type transmission can be achieved.

Operation of these sliding gear transmissions takes place after disengagement of the main clutch device located in front of the input V-pulley 22.

The fixed gears 33 and 30 on the input shaft 15 are the loosely fitted gears 3 of the hydraulic clutches 23 and 24 on the height change shaft 16.
6 and 35 are constantly engaged, and the hydraulic clutch 24
When the clutch 23 is engaged, a high speed of the first hydraulic clutch type transmission is obtained, and conversely, when the hydraulic clutch 23 is engaged, a low speed of the first hydraulic clutch type transmission is obtained.

Fixed gears 37 and 34 on the height change shaft 16 and loosely fitted gears 4 of the hydraulic clutches 26 and 25 on the forward rotation shaft 17
0,38 are always in mesh. Then, when the hydraulic clutch 26 is engaged, the second hydraulic clutch type transmission has a high forward speed, and when the hydraulic clutch 25 is engaged, the second hydraulic clutch type transmission has a low forward speed.

The forward high and low speeds of this second hydraulic clutch type transmission are controlled by a fixed gear 39 through internal and external toothed gears 44b and 44 on the output shaft 19 for the steering brake and clutch.
a is transmitted to the large gear 44a.

A reverse rotation shaft 18 is provided as a bypass between the forward rotation shaft 17 and the output shaft 19. Conventionally, only a reverse rotation gear was loosely fitted on the reverse rotation shaft, but in this embodiment, the reverse rotation shaft 18 is provided with a reverse rotation gear. A hydraulic clutch 27 is provided. A loosely fitted gear 38 on the normal rotation shaft 17;
The loosely fitted gear 42 of the reverse hydraulic clutch 27 is always engaged, the forward rotation shaft 17 also serves as a reverse gear shaft, and reverse rotation is transmitted to the reverse rotation shaft 18.
Reverse rotation is obtained by connecting the hydraulic clutch 27 and is transmitted from the small output gear 41 to the large gear 44a.

When one of the main transmission hydraulic clutches 25, 26, 27 is engaged, the others are disengaged.

The clutch gears 45L and 45R on the output shaft 19 are slid and connected to and disconnected from the internal gear 44b, thereby forming a steering clutch, and the clutch gear 4 is further moved outward.
The steering brake is applied by pressing 5L and 45R.

The clutch gears 45L, 45R are configured to have a wide width, and the fixed gears 47L, 45R are fixed on the shafts 20L, 20R.
It meshes with 47R.

Other fixed gears 48L, 4 on shafts 20L, 20R
Power is constantly transmitted from 8R to fixed gears 49L, 49R on drive sprocket shafts 21L, 21R.

4 is a plan sectional view of the hydraulic control valve B, and FIG. 5 is a plan view of the speed change guide plate 6.

As shown in Figure 4, three spools 50,5
1 and 52 are placed in the hydraulic control valve B, and the three spools are connected to one connecting rod 53 and moved simultaneously, thereby controlling the five hydraulic clutches for the first and second hydraulic clutch type shifting. The vehicle is controlled to have four forward speeds, two reverse speeds, and a neutral position.

The spool 50 plays the role of selecting the hydraulic clutches 23 and 24 for shifting the first hydraulic clutch, and also plays a neutral role of flowing pressure oil to the drain circuit when in the neutral state.
On the spool 51, the pressure oil from the P port continuously flows to the (R1 and R2) ports at two of the seven spool stop positions, and the reverse hydraulic clutch 27 of the second hydraulic clutch type transmission is connected at the second position. However, due to the movement of the spool 50, the hydraulic clutch of the first hydraulic clutch type transmission in the upper position moves the hydraulic clutches 23, 23,
24, so it replaces R2 and R1.

Similarly, in the forward spool 52, pressure oil flows through the (F2/F4) ports at the 2 positions, and (F1/F4)
Pressure oil flows at the F3) port as well at the spool stop position 7, but in this case too, because the spool 50 of the first hydraulic clutch type transmission is alternately switched to the hydraulic clutches 24 and 23, respectively.
It is switching to F2 and F4, then F1 and F3.

By configuring the spool in this way, even if the hydraulic clutches are not arranged in parallel but are arranged in series with the first and second hydraulic clutch type transmission devices, the single connecting rod 53 can move monotonously in one direction. Therefore, as shown in FIG. 5, the shift lever 7 can be used to shift gears in seven positions: R2, R1, N, F1, F2, F3, and F4.

As in the past, if hydraulic clutches are arranged in parallel, it is easy to change the hydraulic pressure by a single linear movement of the gear shift lever, no matter how many hydraulic clutches there are. The width increases by the amount of parallelization.

Furthermore, if the hydraulic clutches are arranged in series, the width of the transmission case becomes narrower, but it becomes troublesome to alternately switch between the upper and lower hydraulic clutches.
Conventionally, the spool was selected using the shift lever by moving the shift lever from side to side.

On the other hand, in this embodiment, when the hydraulic clutch of the second hydraulic clutch type transmission is switched, the hydraulic clutch of the first hydraulic clutch type transmission remains unchanged, and the hydraulic clutch of the first hydraulic clutch type transmission remains unchanged. When the hydraulic clutch of the device is switched, the hydraulic clutch of the second hydraulic clutch type transmission is fixed integrally with the spools so that it does not switch, and the gear can be shifted by linear movement. .

The spool position shown in Figure 4 is forward 4.
The P port of the spool 50 is in the H position.
It flows to the ports for F3, F4, and R2 of the port, passes through the spool 51, and the P port of the spool 52 flows to the port for F2 and F4, which is the h port, and the hydraulic clutches 24 and 26 are connected, and the fourth forward speed is established. It is becoming.

When the connecting rod 53 is moved to the third forward speed position, the spool 50 is the same as the H port, but the spool 5
2 is switched to the l port (F1/F3), hydraulic clutches 24 and 25 are connected, and the third forward speed is established. When the connecting rod 53 is moved to the second forward speed position, the spool 50 switches to the L port for F1, F2, and R1, and the P port of the spool 52 flows to the H port again, and the hydraulic clutches 23 and 26 are connected. 2nd forward speed.

When the connecting rod 53 is moved to the first forward speed position, the spool 50 flows to the L port, the spool 52 changes to the L port, the hydraulic clutches 23 and 25 are connected, and the first forward speed is established.

When the connecting rod 53 is placed in the neutral position, the pressure oil in the spool 52 flows to the N port, and the pressure oil in the spool 52 is confined and no hydraulic clutch is connected.

When the connecting rod 53 is moved to the first reverse speed position, the spool 50 flows to the L port, and the pressure oil in the spool 51 flows to the R port, which is the port for R1 and R2.
The P port to spool 52 is closed. When the connecting rod 53 is moved to the second reverse gear position, the spool 5
0, the flow changes to the H port, and the r of the spool 51
It remains the port.

FIG. 6 shows the destination of the pressure oil of the spool 50 of the first hydraulic clutch type transmission, the main transmission spool 51,
52 shows the destination of the pressure oil for each gear stage.

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

First, in the conventional technology described in Japanese Utility Model Application Publication No. 52-37174, six sets of hydraulic However, in the case of the present invention, five hydraulic clutches can provide four forward speeds and two reverse speeds.

That is, the height-low speed change shaft 16 and the normal rotation shaft 17 are connected in series,
By arranging the height change shaft and the reversing shaft 18 in series, four forward speeds and two reverse speeds can be obtained even though there are five hydraulic clutches.

Therefore, the number of hydraulic clutches can be reduced by one, and only five hydraulic clutches are required, and the number of oil passages to be machined is also reduced.

Second, since the forward gear shifts from 1 to 4 are performed where power is transmitted in series from the input shaft to the high/low shift shaft and then to the forward rotation shaft, the range of reduction ratios becomes large and the set gear arrangement also changes. You can do it freely.

Thirdly, since reverse movement is also done in series, the gears have been shifted to high and low gears on the upper side of the transmission, and then the gears are reversed.
Since stages are obtained, the width of the reduction ratio becomes large in this case as well, and the setting can be easily performed.

Fourthly, since the small output gears 39 and 41 are only fixed on the forward rotation shaft 17 and the reverse rotation shaft 18, the output shaft 19
This made the arrangement relatively free.

Fifth, in the conventional technology described in Japanese Patent Application Laid-open No. 54-153957, the front gear changes forward and backward gears, and the rear gear changes high and low gears. It was necessary to provide a separate shaft and reverse gear.

Furthermore, in the technology described in Japanese Utility Model Application Publication No. 56-90539, the front stage performs forward and backward shifting, and the rear stage performs elevation and low shifting, so a reverse gear shaft and a reverse gear are required in the front stage to obtain reverse speed. There was a problem.

In the present invention, since the front stage has a high/low speed shift and the rear stage has a forward/backward gear shift, the forward rotation shaft 17 can also be used as a reverse gear shaft. It could have been omitted.

[Brief explanation of drawings]

FIG. 1 is an overall side view of a combine harvester among agricultural machines, and FIG. 2 is a skeleton diagram of a transmission device of the present invention.
Figure 3 is a side view of transmission case A, Figure 4 is a cross-sectional plan view of the hydraulic control valve, Figure 5 is a plan view of the gear shift lever guide, and Figure 6 is a diagram showing the direction of pressure oil in the hydraulic control valve. It is. A...Mission case, B...Hydraulic control valve,
15...Input shaft, 16...Height/low speed change shaft, 17...
Forward rotation axis, 18...Reverse rotation axis, 19...Output shaft, 2
3, 24, 25, 26, 27...hydraulic clutch.

Claims (1)

[Claims] 1 Input shaft 15 connected to the prime mover and height change shaft 1
6, a forward rotation shaft 17, a reverse rotation shaft 18, and an output shaft 19 are horizontally mounted in parallel with each other, two gears 30, 33 are fixed on the input shaft 15, and a height change shaft 16 is attached to the gears 30, 33. The upper two gears 35, 36 are engaged, and the gears 35, 36 are connected to the hydraulic clutches 23, 24.
The two gears 34,
37 is fixed, and the gears 34 and 37 are meshed with the two gears 38 and 40 on the normal rotation shaft 17, and the gear 3
8 and 40 can be loosely fitted and fixed on the normal rotation shaft 17 via hydraulic clutches 25 and 26, and a small output gear 39 is fixedly installed on the normal rotation shaft 17, and the small output gear 39 is outputted. A gear 42 that meshes with the large gear 44a on the shaft 19 and meshes with one of the loosely fitted gears 38 and 40 on the forward rotation shaft 17 is provided on the reverse rotation shaft 18, and the gear 42 is rotated in reverse rotation via the hydraulic clutch 27. axis 18
A small output gear 41 that meshes with the large gear 44a on the output shaft 19 is fixed on the reversing shaft 18, and either one of the hydraulic clutches 23, 24 on the high/low speed change shaft 16 and hydraulic clutches 25, 26, 27 on the forward rotation shaft 17 and the reverse rotation shaft 18.
Directional switching valves 50, 51, and 52 are provided to selectively and simultaneously connect any one of the
6. A transmission device characterized in that the forward rotation shaft 17 is also used as a reverse gear shaft, and the rotation after being shifted high or low at step 6 is further changed to two forward speeds and one reverse speed.