JPS5857339B2 - Side clutch device for traveling work vehicles, etc. - Google Patents

Description

[Detailed Description of the Invention] When the side clutch device of a traveling work vehicle or the like is constructed as a multi-disc hydraulic clutch, advantages such as the operation mechanism of the side clutch device is simplified and the operation becomes easier, The present invention relates to a side clutch device for a traveling work vehicle, etc., which is configured as a multi-plate hydraulic clutch as described above.
The purpose of this is to ensure that the braking action of the parking brake, which is installed prior to this type of side clutch in the travel power transmission path, is guaranteed even when the engine is stopped when oil leaks from the multi-disc hydraulic clutch. It is an object of the present invention to provide a novel side clutch device which is extremely compact and has a small hydraulic system capacity.

Regarding the illustrated embodiment, the configuration of a side clutch device for a traveling work vehicle or the like according to the present invention will be explained. In this embodiment, the present invention is applied to a combine harvester as shown in FIG. While the machine is running, the weed culm to be planted in the field is divided by the weed cutting body 2 in front of the machine, and the culm lifting device 3, which is installed in front of the machine and tilted diagonally backward and upward, separates the husks to be planted in the field. At the same time, the culm is pulled up, and the planted culm is cut at the base of the plant by the cutting blade 4 of the terminal part of the machine body, and the cut culm is transported to the position on the side of the machine body by the lower conveying device 5. The shell culm is supplied to the threshing section 7 by the vertical conveyance device 6, and the cut husk is threshed while being transported rearward by the feed chain 8 disposed on one side of the threshing section 7. The present invention relates to an example implemented in a combine harvester configured to supply straw leaving a straw to a cutter device 10 using a straw conveying device 9.

A mission case 11 is installed at a suitable location at the front of the combine harvester, and as shown in FIG. As shown in FIG.
5, two power shift shafts 16, 17, a side clutch shaft 18, a hand brake shaft 19, and left and right transmission output shafts 20 are provided parallel to each other,
The transmission input shaft 14 supports the manual pulley 12 on one end thereof and connects the manual pulley 12 and the main clutch 21.
The mission input shaft 14
A gear transmission device 22 is disposed between the gear transmission shaft 15 and the gear transmission shaft 15.
A hydraulic clutch type transmission 23 is disposed between the gear transmission shaft 15 and the power shift shaft 16, 17.1. Furthermore, left and right side clutches 24 are mounted on the side clutch shaft 18.
However, left and right handbrakes 25 are respectively arranged on the handbrake shaft 19, and the left and right transmission output shafts 2
0 is interlocked and connected to a drive wheel 26 that drives the traveling crawler 1 one rotation, and a parking brake 27 configured to expand inward is disposed at the end of the power shift shaft 16 as shown in the figure. However, the left and right side clutches 24 described above are particularly configured as multi-plate hydraulic clutches as described below.

That is, as shown in FIG. 2-4, a large-diameter input gear 28 is provided on the side clutch shaft 18 at the center.
As shown in FIG. 5, this input gear 28 is meshed with fixed gears 29 and 30 on both power shift shafts 16 and 17, respectively, and is driven to rotate. , a pair of left and right output gears 31
The gear 2 is provided with a multi-plate two-oil can clutch that selectively interlocks and connects the input gear 28 and each output gear 31.
The left and right side clutches 24 are arranged between 8.31 and 31.

More specifically, as shown in FIG. 4, a cylindrical friction plate support portion 28a extending left and right is formed on the boss portion of the input gear 28, and a central portion in the width direction of the boss portion of the input gear 28 is formed. The left and right clutch housings, which are internally separated from each other, are configured by the boss portion of the input gear 28 itself, and one of the friction plates 32 can be slid only in the clutch axial direction on each of the friction plate supports 28a. At the same time, each output gear (31σ) is provided with a friction plate support portion 31a extending in the direction of the input gear 28 at the boss portion, so that the other friction plate 33 can only be slid on the support portion 31a in the clutch axial direction. Pistons 34 are disposed between the input gear 28 and the left and right output gears 31 and are movable along the clutch axis, and oil chambers 35 are provided on one and other sides of each piston 34.
36 and is bored in the side clutch shaft 18.
When pressurized oil is supplied to the oil chamber 35 on the human gear 28 side via the gears 7 and 38, the piston 34 is moved forward in the direction of the output gear 31, and the friction plates 32 and 33 are brought into pressure contact, causing the clutch 24 to engage. When the human power gear 28 and the output gear 31 are interlocked and the pressure oil is supplied to the oil chamber 36 on the output gear 31 side through the oil passages 39 and 40 bored in the side clutch shaft 18? 1. Piston 34 is human powered gear 28
The left and right side clutches 24 are configured so that when they are moved backward in the direction, the pressure contact between the friction plates 32 and 33 is released, the clutch 24 is disengaged, and the interlocking connection between the input gear 28 and the output gear 31 is severed. It is.

As described above, in addition, in the widthwise central portion of the boss portion of the human gear 2B, as shown in FIG. and a spring accommodating hole opening in the other clutch housing are formed to be out of phase with each other.

As shown in FIG. 4, compression springs 42 are housed in the spring housing holes 41 to bias the piston 34 in the forward direction, and therefore the friction plates 32 of the side clutches 24
．． 33 in the direction of clutch engagement.
Each side clutch or hydraulic clutch 24 is a partially spring-loaded type in which a part of its engagement force is obtained by the action of this compression spring 42, that is, oil ( The engagement oil chamber 35 is in a state where there is no action.
Even when the hydraulic pressure is released, the compression spring 42 causes the friction plates 32 and 33 to come into pressure contact with each other with a slight engagement force, and the torque is smaller than the normal transmission torque of the clutch 24 through the clutch 24. The clutch 24 is designed to be able to transmit the torque under the mounting plate, and this latter torque, which is determined by the spring force of the compression spring 42 which shares a part of the clutch engagement force, is transmitted from this side. The brake capacity is set to be approximately equal to the brake capacity of the parking brake 27 located before the clutch 24.

In addition, in the illustrated case, the left and right hand brakes 2 described above are
5 is also constructed as a hydraulically operated type as follows.

That is, as shown in FIGS. 2 and 4, left and right large-diameter gears 43 are loosely fitted onto the side brake shaft 19 and meshed with the left and right output gears 31 on the side clutch shaft 18, respectively. A small diameter gear 44 integrally attached to each of the large diameter gears 43 with a common boss portion is meshed with the large diameter gear 45 on each mission output shaft 20 to perform deceleration transmission to the left and right mission output shafts 20. However, the boss portion of each large diameter gear 43 is connected to the small diameter gear 44.
The friction plate support portion 43a extends in the opposite direction, and the mission case 1 is attached to the end of the handbrake shaft 19.
Friction plate supports 46a and 47 that can extend inward to the tooth 11 are attached to the left and right case lids 46 and 47 fixed to the teeth 11, respectively.
a are integrally formed, one friction plate 48 is connected to the friction plate support part 43a, the other friction plate 49 is connected to the friction plate support part 46a,
A cylinder body 50 is provided on the central part of the handbrake shaft 19 and has left and right cylinder parts 50a. 19 A piston 51 that is slidable in the axial direction is disposed, and pressure oil is supplied to an oil chamber 54 behind the diagnosis piston 51 through oil passages 52 and 53 bored in the handbrake shaft 19 to advance the piston 51. Time is gear 44
The gear 43 is slid toward the end of the shaft 19 through the gears 43 and 44, so that the friction plates 48 and 49 are pressed against each other, and the piston 51 is moved in the backward direction through the gears 43 and 44. A compression spring 55 is provided on the handbrake shaft 19, and the gear 43 is fixed by pressure contact between the friction plates 48 and 49 as the piston 51 moves forward.
7 selectively fixed at 161, left and right output shafts 20,
Therefore, the left and right side brakes 25 are configured as Tomata clutch type brakes that selectively brake the left and right axles 26a.

Next, the general configuration of the gear transmission 22 and the hydraulic clutch type transmission 23 described above will be explained with reference to FIGS.
The shift gear pair 56 and 57 are slidably provided on the gear shift shaft 15 by spline fitting, and the shift gears 58, 59, 60, and 61 are fixed on the gear shift shaft 15. When the shift gear 56a of the shift gear pair 56 is meshed with the transmission gear 58, the gear is set to 1st speed, when the shift gear 56b is meshed with the transmission gear 59, the gear is set to 2nd gear, and the shift gear 57a of the shift gear pair 57 is meshed with the transmission gear 60. And 3 speed?
When the shift gear 57b is engaged with the speed change gear 61, 4th gear is set.
Each of them is configured to be obtained on the gear transmission shaft 15.

The hydraulic clutch type transmission 23 also includes a power shift shaft 1
The F1 gear 63 is loosely fitted to the power shift shaft 1T and meshed with the speed change gear 60 on the gear speed change shaft 15, and the F2 gear 6 is loosely fitted to the power shift shaft 1T and meshed with the fixed gear 62 on the gear speed change shaft 15.
4, an F3 gear 65 loosely fitted on the power shift shaft 16 and meshed with the fixed gear 62 on the gear change shaft 15, and an R gear 65 loosely fitted on the power shift shaft 17 and meshed with the F1 gear 63.
4ffi with gear 66! Idle gears 63-66 of il,
An F1 hydraulic clutch 67, an F2 hydraulic clutch 68, and an F3 hydraulic clutch, which are multi-disc hydraulic clutches of a conventional structure, are disposed on the power shift shaft 16 or 17 on each of the free rotating gears 63-66.
A hydraulic clutch 67-70 is connected to a hydraulic clutch 69 and an R hydraulic clutch 70 to selectively shift each idle gear 63-66 to the power shift shaft 16 or 17 by engagement thereof.
The hydraulic clutch 67-70 is coupled to the hydraulic clutch 67-70.

Next, the configuration of the hydraulic side tilting mechanism attached to the transmission mechanism as described above will be explained with reference to FIG.
The lower part inside the mission case 11 is also used as an oil link 71, and as shown in FIG.
21 rigid r meat pressure pump 72, 7 with a pump shaft directly connected to 4
3 is provided, and the supply of pressure oil to the hydraulic clutches 67-70 in the hydraulic clutch type transmission 23 is carried out from the oil tank 71 by a hydraulic pump 72 via an oil supply circuit 74, and The oil supply circuit 74, whose oil pressure is set by a valve 75, includes a full hydraulic clutch 67-
A neutral position N where oil is drained from 70, a forward first speed position F1 where oil is supplied to the F1 hydraulic clutch 67 and oil is drained from the other Yukasa clutches 68, 69, 70, and a forward first speed position F1 where oil is supplied to the F2 hydraulic clutch 68 and others. a forward 2nd speed position F2 where oil is drained from the hydraulic clutches 67, 69, 70 of the F3 hydraulic clutch 69, and a forward 3rd speed position F3 where oil is drained from the hydraulic clutches 67, 68, 70 of the F3 hydraulic clutch 69; A switching valve 76 is inserted that has a reverse position R that supplies oil to the R hydraulic clutch 70 and drains oil from the other hydraulic clutches 67, 68, and 69. , is connected to a lubricating oil supply circuit 78 to the hydraulic clutches 67-70 together with the relief port of the pressure regulating valve 75, and is connected between a tank circuit 79 that returns lubricating oil from the hydraulic clutches 67-70 to the oil tank 71 and the oil drain circuit 77. A pressure regulating valve 80 for setting the lubricating oil pressure is inserted into the connecting circuit, and an accumulator 81 is attached to the oil supply circuit γ4.

Next, pressure oil is supplied to the side clutch 24 and the side brake 25 from an oil tank 71 by a hydraulic pump 73 via an oil supply circuit 82, and the oil pressure is supplied by a pressure regulating valve 83. This oil supply circuit 8 to be set
2 is branched into a left oil supply circuit 82L connected to the left side clutch 24 and hand brake 25, and a right oil supply circuit 82R connected to the right side clutch 24 and hand brake 25. Each of the left and right oil supply circuits 82L and 82R has two pump boats connected to the primary side and a tank boat connected to the tank circuit 84.
A boat connected to a supply/discharge circuit 85 communicating with the engagement oil chamber 35 of the side clutch 24 on the secondary side, and a supply/discharge circuit 86 communicating with the disengagement oil chamber 36 of the side clutch 24 on the secondary side. Connected boat and handbrake 25
A switching valve 88 each having three boats connected to a supply/discharge circuit 87 communicating with the oil chamber 54 of
The five-port switching valves 88 are connected to each other by the pump boat, and each of the five-port switching valves 88 has three positions as shown in the figure, that is, the supply/discharge circuit 85 connected to the engagement oil chamber 35 of the side clutch 24 is connected to the oil supply circuit. 82 and a supply/discharge circuit 86 connected to the release oil chamber 36 of the side clutch 24; and a supply/discharge circuit 8γ connected to the oil chamber 54 of the side brake 25.
and a position I where the side clutch 24 is engaged and the hand brake 25 is deactivated by connecting the side clutch 24 to the tank circuit 84, and the supply/discharge circuit 86 connected to the disengagement oil chamber 36 of the side clutch 24 is connected to the oil supply circuit. A supply/discharge circuit 85 connected to 82 and connected to the engagement oil chamber 35 of the side clutch 24 and a supply/discharge circuit 87 connected to the oil chamber 54 of the side brake 25 are connected to the tank circuit 84. Position ■ where the clutch 24 is disengaged and the side brake 25 is deactivated, and the disengagement oil chamber 36 of the side clutch 24
The supply/discharge circuit 86 and the oil chamber 5 of the handbrake 25 are connected to
4 is connected to the oil supply circuit 82, and the supply and discharge circuit 85 that is connected to the engagement oil chamber 35 of the side clutch 24 is connected to the tank circuit 84, and the side clutch 24 is disengaged. In addition, the handbrake 25 is configured to be selectively switched to three positions, including a position in which the handbrake 25 is activated.

As shown in Figures 3 and 4 and Figures 8-10, an oil passage plate 89 is fixedly attached to one side of the transmission case 11, and an oil passage plate 90 is fixedly attached to the other side. Further, the upper surface of the mission case 11 has a split surface and has a two-sided structure.
and a valve mechanism housing 91 for accommodating its auxiliary mechanism.
A valve mechanism housing 92 for accommodating the switching valve 88 and its auxiliary mechanism is fixedly provided on the other parts, and the valve mechanism housing 91 is inserted from one outlet of the hydraulic pump 72, 73 into the valve mechanism housing 91. An oil supply passage extending from the oil passage plate 89 and the outer surface of the transmission case 11 is formed between the oil passage plate 89 and the outer surface of the transmission case 11, and a plurality of oil passages P leading from the inside of the valve mechanism housing 91 to the ends of each power shift shaft 16 and 17 are formed between the oil passage plate 89 and the outer surface of the transmission case 11. mission case 11
The latter oil passage P is formed between the outer surfaces of the seal housing 93° 94 that fits into the shaft end of the Parno shift shaft 16° 1T, and the multiple oil chambers R formed between the power shift shafts 16 and 17. The oil is guided from inside the oil chamber R to the hydraulic clutches 67-70 of the hydraulic clutch type transmission 23 via oil passages (not shown) drilled in the power shift shafts 16, 17. The hydraulic oil is supplied and discharged to and from the clutches 67-70, and lubricating oil is supplied to the clutches 67-70, and a passage from the inside of the valve mechanism housing 91 to the inside of the valve mechanism housing 92 is connected to the discharge port of the hydraulic pump γ3. The oil supply circuit 8
One oil supply passage corresponding to 2 is led, and a plurality of oil supply passages P' extending from the switching valve 88 in the housing 92 to the side clutch shaft 18 end and the side brake shaft 19 end are connected to the oil passage plate 90 and the transmission case. These oil supply passages P' are formed between the outer surfaces of the side clutch shaft 18 and the shaft ends of the side clutch shafts 18 and 9. Seal housing 95 and side clutch shaft 1
8 and the side clutch shaft 18
The left and right side clutches 24 via the oil passages 37-40 of
and the plurality of oil chambers R" formed between the shaft end of the handbrake shaft 19 and the case lid 46 and the oil passage 52.5 of the handbrake shaft 19.
3 to the oil chamber 54 of the left and right hand brakes 25.

In FIG. 4, reference numerals 96 and 97 indicate gears that are fitted onto the mission output shaft 20 and the axle 26a and are meshed with each other, constituting the final reduction mechanism, and 98 is a gear whose base end is attached to the mission case 11. This is a final transmission case that is fixed and accommodates the output shaft 20.

Although the details have been explained above, in short, the side clutch device for a traveling work vehicle, etc. according to the present invention is configured as a multi-disc hydraulic clutch, and in particular, the clutch housings of the left and right side clutches 24 are The input gears 28 are separated from each other at the widthwise central portion of the boss portion of the input gear 28 provided on the side clutch shaft 18.
The spring housing hole 41 that opens in one clutch housing and the spring housing hole 41 that opens in the other clutch housing are arranged in the widthwise central part of the boss part itself. Compression springs 42, which are formed with a phase difference between the two sides and move and bias the friction plates 32 and 33 of each side clutch 24 in the clutch engagement direction to share a part of the clutch engagement force, are inserted into each spring housing hole 41. Because of the structure that is characterized by the fact that it is accommodated, it has the following advantages.

That is, the side clutch device of the present invention has a partially spring-loaded type in which the left and right side clutches are multi-disc hydraulic clutches, and a portion of the engagement force is shared by the compression spring 42. Therefore, even when the engine is stopped due to oil leakage from the hydraulic clutch, which is a side clutch, the running power transmission path is cut off by the clutch because some of the clutches are spring-loaded. The action of the spring 42 allows the side clutch 24 to maintain an engaged state in which a certain amount of torque can be transmitted, thereby transmitting torque equivalent to the brake capacity of the parking brake 27 in the front stage. 27 braking action is guaranteed, and in order to guarantee the parking brake braking action when the engine is stopped, the hydraulic side clutch is replaced with a fully spring-loaded type, that is, clutch engagement is performed only by spring load. However, if the clutch is disengaged only by hydraulic action, as in the case of a distant relative, an extremely heavy load is required, and the spring becomes large, making it difficult to fit into a limited space. There is no inconvenience that it becomes impossible to close the clutch, and the side clutch can be constructed compactly. Since the clutch must be disengaged against the load, there is no need to increase the hydraulic load of the flesh pressure clutch and use high hydraulic pressure, and the hydraulic system is simplified with a small capacity. It is something that can be made into something.

Furthermore, in the side clutch device of the present invention, the boss portion of the input gear constitutes the clutch housing of the left and right side clutches, and separate clutch housings are not provided.
The compression spring 42, which has a large number of grooves and has the above-mentioned advantages, is accommodated in the spring housing hole 41 formed in the widthwise center of the boss portion of the input gear 28. Since this device does not require any extra installation space, it is an extremely compact device in itself, although it exhibits the above-mentioned advantages.

[Brief explanation of drawings]

Fig. 1 is a side view of a combine equipped with an embodiment of the present invention, Fig. 2 is a diagram of the traveling power transmission mechanism of the combine, and Figs. 3 and 4 respectively show the upper half of the transmission case of the combine. FIG. 5 is a schematic diagram showing the arrangement of gears, FIG. 6 is a side view of the main parts, FIG. 7 is a curved ball circuit diagram of the same embodiment, and FIG. 8 and FIG. 9 are a right side view and a left side view of the mission ground shown in FIGS. 3 and 4, respectively, and FIG. 10 is a plan view of the upper mechanism of the mission case. 18...Side clutch shaft, 24...
Side clutch, 28... Input gear, 28a.
...Friction plate support part, 31...Output gear,
31a...Friction plate support part, 32, 33...
...Friction plate, 34... Piston, 35.36.
... Oil chamber, 41 ... Spring accommodation hole, 42.
...Compression spring.

Claims (1)

[Claims] 1. A side clutch device configured as a multi-disc hydraulic clutch, in which the clutch housings of the left and right side clutches are internally separated from each other by the widthwise central portion of the boss portion of the input gear provided on the side clutch shaft. The input gear boss is constituted by the input gear boss itself, and a spring housing hole that opens in one clutch housing and a spring housing hole that opens in the other clutch housing are provided in the widthwise central portion of the boss part. Compression springs, which are formed out of phase with each other and which move and energize the friction plates of each side clutch in the clutch engagement direction to bear part of the clutch engagement force, are housed in each of the spring housing holes. A side clutch device for traveling work vehicles that is characterized by: