JPS628680Y2 - - Google Patents

Description

[Detailed description of the invention] This invention is a mobile work vehicle that requires various speed stages as a working speed, such as agricultural machinery and construction civil engineering machinery, and that requires shifting gears and switching forward and backward many times during work. The present invention relates to a transmission.

Conventionally, a technique is known in which a plurality of hydraulic clutch devices are arranged and one set of the hydraulic clutch devices is selectively coupled to perform a speed change. For example, see Utility Model Publication No. 51-139848.

However, when only one set of hydraulic clutch devices is selectively selected from a plurality of sets as in the known technique, the same number of hydraulic clutch devices as the number of gears is required, and the capacity of the transmission case becomes large. ,
Furthermore, the spool of the hydraulic control valve for selectively operating the hydraulic clutch device is also too long, making it impossible to process it.

In order to enable multi-speed shifting with a hydraulic clutch type transmission, the present invention provides hydraulic clutch type transmissions consisting of multiple sets of hydraulic clutch devices in series and overlapping, and the number of gears is multiplied. Therefore, the structure is such that a greater number of gear stages can be obtained than the number of hydraulic clutch devices.

Furthermore, even if hydraulic clutch type transmissions are arranged in series and overlappingly, if the shift lever that performs gear shifting operations rotates within an H-shaped or U-shaped shift lever guide groove, the shift lever will not rotate linearly. Therefore, the advantage of hydraulic clutch type transmissions, which is the ability to sequentially shift from high speed to low speed by movement, is lost, so the spools provided for each hydraulic clutch type transmission are integrated by a connecting rod, and the linear rotation of the gear lever is changed. This makes it possible to sequentially shift from high speed to low speed.

The purpose of the present invention is as described above, and the structure of the present invention will be explained based on the structure of the embodiment shown in the attached drawings.

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

After the grain culm is pulled up by the pulling device 3 and the stock part is cut, the grain culm is transferred to the feed chain 8 of the threshing device 9 by the grain transport device 4, and the stock part is held between the feed chain 8. Then, the tip of the ear is inserted into the handling barrel and threshed. After threshing, the culm is removed from the culm chain 10.
The culm is then guided to the waste culm processing device 11.

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 rotate the crawler device 1.

A gear shift lever 7 for simultaneously operating the first hydraulic clutch type transmission and the second hydraulic clutch type transmission of the transmission case A is protruded above the gear change guide plate 6, and the operator on the seat 12 can use it with his/her left hand. It is located in a position where it can be operated. Reference numeral 5 indicates a control column provided on the left and right steering clutch levers, etc.

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

A hydraulic control valve B is placed on the upper machined surface of the transmission case A, and a speed change lever 7 for moving a spool of the hydraulic control valve also protrudes from there. Inside the transmission case A, eight axes from the input shaft 14 to the sprocket drive shaft 21 are provided in a stepped manner.

An input V-pulley 22 is fixed to one end of the input shaft 14, and power is transmitted from the engine via a V-belt. A hydraulic pump 13 is fixed to the other end of the input shaft 14, and sucks circulating oil in the transmission case A and supplies it as pressure oil to each hydraulic clutch device. Double sliding gear 2 on input shaft 14
8a, 28b, internal and external gears 29b, 29a, and fixed gears 33, 32, 31 on the second shaft 15, a gear sliding type sub-shift is performed.

The gear 28b and the gear 33 mesh to obtain the low speed of the sub-shift, and the gear 28a and the gear 32 mesh,
The medium speed of the sub-shift is achieved by the gear 28a meshing with the internal gear 29b and the external gear 29a meshing with the gear 31, thereby achieving a high speed of the sub-shift.

These gear sliding sub-shifts are operated by connecting and disconnecting a main clutch device provided in front of the input V-pulley 22.

The hydraulic clutch devices 23, 24 on the transmission shaft 16 constitute a first hydraulic clutch type transmission.

The fixed gears 33, 30 on the second shaft 15 are always in mesh with the loosely fitted gears 36, 35 of the hydraulic clutch devices 23, 24 on the hydraulic clutch shaft 16, and when the hydraulic clutch device 24 is connected, the first The high speed of the hydraulic clutch type transmission is obtained, and conversely, the low speed is obtained by connecting the hydraulic clutch device 23.

Next, the hydraulic clutch type transmission devices 25 and 26 on the hydraulic clutch shaft 17 and the hydraulic clutch device 27 on the hydraulic clutch shaft 18 constitute a second hydraulic clutch type transmission device.

Fixed gears 37, 34 on the hydraulic clutch shaft 16 and hydraulic clutch device 26 on the hydraulic clutch shaft 17,
No. 25 loosely fitted gears 40 and 38 are always in mesh with each other.
Then, by connecting the hydraulic clutch device 26, the second
The forward speed of the hydraulic clutch type transmission becomes high speed, and the forward speed becomes low when the hydraulic clutch device 25 is connected. This main shift forward high speed and forward low speed are fixed gears 3
9 to 44a of the internal and external gears 44b and 44a on the steering brake/clutch shaft 19.

A reversing hydraulic clutch shaft 18 is provided as a bypass between the hydraulic clutch shaft 17 and the steering brake/clutch shaft 19. Conventionally, only a reversing gear was loosely fitted to the reversing shaft, but in this embodiment, the reversing gear is loosely fitted to the reversing shaft. The reverse hydraulic clutch device 27 is arranged on the reversing hydraulic clutch shaft 18 in order to reduce the number of hydraulic clutch devices and facilitate processing and assembly by dispersing many hydraulic clutch devices without arranging them on one hydraulic clutch shaft. ing. The loose-fit gear 38 on the hydraulic clutch shaft 17 and the loose-fit gear 42 of the reverse hydraulic clutch device 27 are always in mesh with each other. Reverse rotation is achieved by connecting the hydraulic clutch device 27, and the external gear is connected to the fixed gear 41. 44a.

Also in the case of the second hydraulic clutch type transmission, when one of the hydraulic clutch devices 25, 26, 27 is engaged, the other is in the disengaged state.

When the clutch gears 45L and 45R on the steering brake clutch shaft 19 slide and connect and disconnect with the internal gear 44b, they become a steering clutch, and by further pushing the clutch gears 45L and 45R outward, the steering brake is applied. be. clutch gear 45
L and 45R are configured with a wide width, and the shafts 20L and 2
It is constantly meshed with fixed gears 47L and 47R on 0R.

Other fixed gears 48L, 4 on shafts 20L, 20R
The effect is constantly transmitted from 8R to the fixed gears 49L, 49R on the 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.

Three spools 50,5 as shown in FIG.
1 and 52 in the hydraulic control valve B, and the three spools are connected by one connecting rod 53 and moved simultaneously, the two hydraulic clutch devices of the first hydraulic clutch type transmission and the second hydraulic clutch device are connected. A total of five hydraulic clutch devices, three hydraulic clutch devices in two hydraulic clutch type transmissions, are controlled to obtain four forward speeds, two reverse speeds, and neutral.

The spool 50 plays a neutral role in selecting the hydraulic clutch devices 23 and 25 for the first hydraulic clutch type transmission and in flowing hydraulic pressure to the drain circuit when in neutral mode.

Further, the spool 51 is connected to a hydraulic clutch device 27 for reverse movement in the second hydraulic clutch type transmission device.
The pressure oil in the P port is continuously activated at two of the seven spool stop positions, R1,
It flows to the R2 port, and the reverse hydraulic clutch device 27 of the main transmission is connected at the 2nd position. Since the hydraulic clutch devices 23 and 24 of the first hydraulic clutch type transmission device in the upper position are switched by the movement of the spool 50, they replace R1 and R2.

The spool 52 is a hydraulic clutch device 2 for forward height/lowering in a second hydraulic clutch type transmission device.
6,25 selections are made.

Also in the forward spool 52, F2, F4
Pressure oil also flows through the ports at the 2nd position, and at the F1 and F3 ports, pressure oil flows through the 2nd position of the spool at the stop position 7, but in this case, the spools 50 for the first hydraulic clutch type transmission are connected to the respective hydraulic clutch devices 24.
and 23, so F2 and F
4, it is switched to F1 and F3.

By configuring the spool in this way, even if the first hydraulic clutch type transmission and the second hydraulic clutch type transmission are arranged in series without arranging the hydraulic clutch devices in parallel, one Ren 53
As shown in Figure 5, by monotonous movement in one direction, R2, R1,
The shift lever 7 can be used to shift gears in seven positions: N, F1, F2, F3, and F4.

If the hydraulic clutch devices are arranged in parallel as in the past, it is easy to change the hydraulic pressure by a single linear movement of the gear shift lever, no matter how many hydraulic clutch devices there are. As the devices are arranged in parallel, the width becomes wider and each spool becomes longer.

In contrast, in this embodiment, when the hydraulic clutch device of the first hydraulic clutch type transmission is switched, the hydraulic clutch device of the second hydraulic clutch type transmission is not switched, and the second hydraulic clutch device is not switched. When the hydraulic clutch device of the clutch type transmission is switched, the hydraulic clutch device of the first hydraulic clutch type transmission is combined so that it does not switch, and the spool is fixed integrally, so that the gear can be changed by linear movement. It is also true.

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

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 52
is switched to the l port for F1 and F3, the hydraulic clutch devices 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 is switched to the ports for F1, F2, and R1 of the L port, the P port of the spool 52 flows again to the H port, and the hydraulic clutch devices 23 and 26 are activated. It connects and becomes the second 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 clutch devices 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 does not connect any hydraulic clutch device.

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 speed position, the flow of the spool 50 changes to the H port, and the spool 51
remains the r port.

In the embodiment, the spool for the second hydraulic clutch type transmission is separated into two spools 51 and 52, but it can be configured into one spool if an oil passage is formed in the spool.

FIG. 6 shows the destination of the pressure oil in the spool 50 of the first hydraulic clutch type transmission and the destination of the pressure oil in the spools 51 and 52 of the second hydraulic clutch type transmission for each gear stage. It is.

As described above, the present invention provides a first hydraulic clutch type transmission and a second hydraulic clutch type transmission which are connected in series to each other, and is capable of switching and controlling the gears of the first hydraulic clutch type transmission. a first spool 50, and a second spool 5 for switching and controlling the gears of the second hydraulic clutch type transmission.
1 and 52 are installed in parallel, combined into one by a connecting rod 53, and each spool is moved in parallel by the same distance.
Since the gear ratios obtained by the combination of the hydraulic clutch type transmission device and the second hydraulic clutch type transmission device are sequentially obtained in ascending order of height, the following effects are achieved.

First, the transmission of the present invention has two sets of hydraulic clutch transmissions, a first hydraulic clutch transmission and a second hydraulic clutch transmission, arranged in series. For example, as in the embodiment, the number of gears of the first hydraulic clutch type transmission is three, including the reverse gear, and the number of gears of the second hydraulic clutch type transmission is two. The total number of gears for both hydraulic clutch type transmissions is:
If the number of gears is 4 forward and 2 reverse, resulting in a total of 6 gears, and the same number of gears is to be obtained by using 1 set of hydraulic clutch devices, the required 6 hydraulic clutch devices will be 5.
It was possible to make it into an individual.

Similarly, if the second hydraulic clutch type transmission has three speeds, nine speeds can be obtained using six hydraulic clutches at the front.
Therefore, the number of hydraulic clutch devices can be reduced, and the transmission case can be constructed more compactly.

Second, the hydraulic control valves for operating the transmission are arranged side by side with spools for both hydraulic clutch type transmissions, and by combining the spools, the two spools move and the speed is changed. Since the configuration is such that the ratios can be obtained sequentially in the order of high and low, even though two sets of hydraulic clutch type transmissions, 1st and 2nd, are provided, the speed can be increased or decreased sequentially by rotating the shift lever. It's something you can go to.

Thirdly, since a plurality of spools are connected by a connecting rod 53 and moved in parallel by the same distance, each spool can be provided with 3 and 4 switching positions, and the hydraulic clutch device can be selected as an alternative. There is no limit to the number of gears, and it is possible to have a large number of gears.

Fourthly, even in the event of dust getting stuck in the spools, each spool is forcibly moved by the same distance in parallel by the connecting rod 53, so that the spools can be operated reliably. As a result, even if the number of hydraulic clutch devices increases and the number of gears increases,
Double engagement of each hydraulic clutch device does not occur.

[Brief explanation of the drawing]

Figure 1 is an overall side view of a combine harvester among agricultural machinery, Figure 2 is a skeleton diagram of the proposed transmission, Figure 3 is a side view of transmission case A, Figure 4 is a plan view of the hydraulic control valve, FIG. 5 is a plan view of the gear shift lever guide, and FIG. 6 is a chart showing the direction of pressure oil of the hydraulic control valve. A...Mission case, B...Hydraulic control valve,
23, 24... First hydraulic clutch type transmission, 25, 26, 27... Second hydraulic clutch type transmission, 50... Spool for first hydraulic clutch type transmission, 51, 52... ... Spool for the second hydraulic clutch type transmission, 53 ... connection rod.

Claims (1)

[Scope of utility model registration request] A first hydraulic clutch type transmission and a second hydraulic clutch type transmission are connected in series to each other. , second spools 51 and 52 for switching and controlling the gear stage of the second hydraulic clutch type transmission are arranged in parallel, integrated by a connecting rod 53, and each spool is moved in parallel by the same distance. A transmission device characterized in that it is configured to sequentially obtain transmission ratios obtained by a combination of a first hydraulic clutch type transmission device and a second hydraulic clutch type transmission device in ascending order of height.