JPS5919158Y2 - Mission device for traveling work vehicles - Google Patents

Description

[Detailed explanation of the invention] This invention is a mission device of a traveling working vehicle such as a traveling agricultural working vehicle such as a combine harvester or a traveling working vehicle of earth construction such as a wheel loader. The present invention relates to a mission device including a plurality of sets of hydraulic operating mechanisms arranged on a plurality of shafts.

That is, the present invention is intended to provide a novel transmission device for a traveling work vehicle that is devised so that oil supply paths for a plurality of sets of hydraulic operating mechanisms as described above can be easily formed.

Regarding the illustrated embodiment, the configuration of the mission device of the traveling work vehicle according to this invention will be explained. In this embodiment, this invention is combined with a combine harvester as shown in FIG. While running,
Grain culms to be planted in the field are separated by a weed cutting body 2 at the front of the machine, and the planted culms are pulled up by a culm pulling device 3 provided at the front of the machine tilting diagonally backward and upward. The planted culm is harvested at the base of the plant by the cutting blade 4 at the lower front end of the machine, and the cut culm is transported to a position on the side of the machine by the lower transport device 5, and then threshed by the vertical culm transport device 6. A feed chain 8 that supplies to the threshing section 7 and is arranged on one side of the threshing section 7
This is an example implemented in a combine harvester configured to perform threshing while conveying the cut husk rearward at the stock head, and to supply straw exiting the threshing section 7 to a cutter device 10 by 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. 2-4, inside this mission case 11 are a mission input shaft 14, a gear shift shaft 15, two power shift shafts 16 and 17, and a side clutch shaft. 18, a handbrake shaft 19, and left and right mission output shafts 20 are provided in parallel with each other, and the mission input shaft 14 supports the manual pulley 12 on one end thereof, and the input pulley 12 and main clutch 2
1, and the mission input shaft 1.
A gear transmission 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 shafts 16 and 17, and a side clutch shaft 18. The left and right side clutches 24 are on the top, and the left and right side brakes 2 are on the side brake shaft 19.
5 are arranged respectively, and the left and right mission output shafts 20
is a drive wheel 26 that rotationally drives the traveling crawler 1;
At the end of the power shift shaft 16, there is a parking brake 27 configured to expand inward as shown in the figure.
The following hydraulic operating mechanisms are provided on the power shift shaft 16, 17, side clutch shaft 18, and hand brake shaft 19, respectively.

That is, as shown in FIGS. 2 and 3, the gear transmission 22 includes a pair of shift gears 56 and 57 slidably provided on the mission input shaft 14 by spline fitting;
Four speed change gears 58.5 fixed on the gear speed change shaft 15
9.60 and 61, when the shift gear 56a of the shift gear pair 56 is engaged with the transmission gear 58, the first gear is shifted, and when the shift gear 56b of the shift gear pair 56 is engaged with the transmission gear 59, the second gear is shifted. When the shift gear 57a of the gear pair 57 meshes with the speed change gear 60, the third speed is obtained, and when the shift gear 57b meshes with the speed change gear 61, the fourth speed is obtained on the gear change shaft 15. However, the hydraulic clutch type transmission 23 disposed on the rear stage side is provided with four hydraulic clutches 67, 68, 69, 70 distributed over two power shift shafts 16, 17. It is made up of.

That is, as similarly shown in FIGS. 2 and 3, the hydraulic clutch type transmission 23 has an F1 gear 63 loosely fitted on the power shift shaft 16 and meshed with the transmission gear 60 on the gear transmission shaft 15, and a power The gear transmission shaft 15 is loosely fitted onto the shift shaft 17.
The F2 gear 64 is meshed with the upper fixed gear 62, the F3 gear 65 is loosely fitted on the power shift shaft 16 and similarly meshed with the fixed gear 62, and the F1 gear 63 is loosely fitted on the power shift shaft 17. F1, which is a multi-disc hydraulic clutch of a conventional structure, has four idler gears 63-66 with an R gear 66 meshed with each other, and each idler gear 63-66 is disposed on the power shift shaft 16 or 17. There are four hydraulic clutches 67-70 including a hydraulic clutch 67, an F2 hydraulic clutch 68, an F3 hydraulic clutch 69, and an R hydraulic clutch 70, and their engagement selectively shifts each idle gear 63-66 to the power shift shaft 16. or hydraulic clutch 67-70 coupled to 17
It is constructed with the following.

Next, on the side clutch shaft 18, as shown in FIG. 2.4, a large diameter input gear 28 is provided 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
A multi-disc hydraulic clutch for selectively interlockingly connecting the input gear 28 and each output gear 31 is provided between the input gear 28 and each output gear 31.
8. Left and right side clutches 24 are arranged between the left and right side clutches 24.

To explain in more detail, as shown in FIG. 4, the boss portion of the input gear 28 is configured as a clutch housing, and one friction plate 32 is attached to a friction plate support portion 28a extending left and right from the boss portion. The input gear 28 is provided so as to be slidably supported only in the axial direction, and the input gear 28 is attached to the boss portion of each output gear 31.
A friction plate support part 31a is formed that can extend in the direction, and the support part 31a supports the other friction plate 33 so that it can only slide freely in the clutch axis direction. The pistons 34 which are slidable along the clutch axis direction are respectively disposed, oil chambers 35 and 36 are formed on one side and the other side of each piston 34, and an oil passage 37 is bored through the side clutch shaft 18. When supplying pressure oil to the oil chamber 35 on the input gear 28 side via the piston 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, thereby engaging the clutch 24. The input gear 28 and the output gear 31 are interlocked and connected, and when supplying pressure oil 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, the piston 3
4 is moved backward toward the input gear 28, and the friction plate 32.3
The left and right side clutches 24 are configured in such a way that the pressure contact between the input gear 28 and the output gear 31 is released, the clutch 24 is disengaged, and the interlocking connection between the input gear 28 and the output gear 31 is broken.

Furthermore, a plurality of spring housing holes 41 are formed intermittently in the circumferential direction on each surface of the input gear 28, as shown in FIG. As shown in FIG. 4, a compression spring 42 is provided to urge the piston 34 to move forward, and each side clutch or hydraulic clutch 24 is a part of which a part of its engagement force is obtained by the action of this compression spring 42. Even if the hydraulic action on the engagement oil chamber 35 is released in a spring-loaded type, that is, in a state where there is no hydraulic action on the disengagement oil chamber 36, the gap between the two friction plates 32 and 33 will be slightly reduced due to the action of the compression spring 42. The clutch 24 is brought into pressure contact with the engagement force of the compression spring 42 and is configured to transmit a torque smaller than the normal transmission torque of the clutch 24 via the clutch 24. This latter torque determined by the spring force of the side clutch 24 is made approximately equal to the brake capacity of the parking brake 27 located at the front stage of the side clutch 24.

Further, the left and right side brakes 25 on the above-mentioned side brake shaft 19 are also configured to be hydraulically operated as described below.

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 large diameter gear 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 left and right case lids 46 and 47, which extend in opposite directions to form the friction plate support portion 43a, and which are fixed to the transmission case 11 at the end of the handbrake shaft 19, respectively,
Friction plate support parts 46a and 47 that can extend inward of the case 11
a is integrally formed, one friction plate 48 is connected to the friction plate support part 43a, and the other friction plate 49 is connected to the friction plate support part 46a.
, 47a, respectively, so as to be slidable only in the axial direction of the shaft 19, and a cylinder body 50 having left and right cylinder parts 50a is provided on the center part of the handbrake shaft 19. A piston 51 that is slidable in the axial direction of the shaft 19 is disposed on the side, and pressure oil is supplied to the oil chamber 54 behind the piston 51 through oil passages 52 and 53 bored in the handbrake shaft 19 to move the piston 51. When moving forward, the gear 43 is slid in the direction of the end of the shaft 19 via the gear 44 so that pressure contact between the friction plates 48 and 49 is obtained, and the piston 51 is moved in the backward direction via the gears 43 and 44. A compression spring 55 for moving and energizing clutch disengagement is provided on the handbrake shaft 19, and the gear 43 is fixed to the case lid 4 by pressure contact between the friction plates 48 and 49 as the piston 51 moves forward.
6. Selectively fix the left and right mission output shafts 20 to 47.
Therefore, the left and right side brakes 25 are configured as hydraulically operated brakes that selectively brake the left and right axles 26a.

Next, in the order of explanation, the configuration of the hydraulic control mechanism attached to the transmission mechanism as described above is illustrated and explained in FIG. 7. The bottom inside the mission case 11 is also used as an oil tank 71, Further, as shown in FIG. 2, two hydraulic pumps 72 and 73 whose pump shafts are directly connected to the transmission manpower shaft 14 are provided.
Pressure oil is supplied from the oil tank 71 to the oil tank 70 by a hydraulic pump 72 through an oil supply circuit 74, and a pressure regulating valve 75
The oil supply circuit 74, whose oil pressure is set at , has a neutral position N where oil is drained from the full hydraulic clutches 67-70, and a neutral position N where oil is supplied to the F□ hydraulic clutch 67 and the other hydraulic clutches 68
．． 69. 70, the forward first speed position F1 performs oil drainage, and the F2 hydraulic clutch 68 is refueled and the other hydraulic clutch 67
, 69.70, the forward second gear position F2 performs oil drainage, and the F3 hydraulic clutch 69 is refueled and the other hydraulic clutch 67
, 68.70, a forward third speed position F3 where oil is drained, and another hydraulic clutch 67 where oil is supplied to the R hydraulic clutch 70,
A switching valve 76 with a reverse position R for draining oil from 68 and 69 is inserted, and hydraulic clutches 67-70
A lubricating oil supply circuit 78 to the hydraulic clutches 67-70 as well as a relief port of the pressure regulating valve 75
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 in the connection circuit between the two, and an accumulator 81 is inserted in the oil supply circuit 74.
is attached.

Also, as mentioned above, it is configured as a hydraulically operated type,
Pressure oil is supplied to the side clutch 24 and the hand brake 25, which are arranged in series with each other, from an oil tank 71 by a hydraulic pump 73 via an oil supply circuit 82. This oil supply circuit 82, which is set by a pressure regulating valve 83, is connected to a left oil supply circuit 82L connected to a left side clutch 24 and a hand brake 25, and a left side oil supply circuit 82L connected to a right side clutch 24 and a hand brake 25, as shown in the figure. The left and right oil supply circuits 82L and 82R are branched into a right oil supply circuit 82R.
Two ports, a pump port and a tank port connected to the tank circuit 84 on the primary side, and a port connected to the supply/discharge circuit 85 communicating with the engagement oil chamber 35 of the side clutch 24 on the secondary side. , a port connected to the supply/discharge circuit 86 communicating with the disengagement oil chamber 36 of the side clutch 24, and a port connected to the supply/discharge circuit 87 communicating with the oil chamber 54 of the side brake 25, respectively. A switching valve 88 provided is connected to the pump port,
Each of the five-port switching valves 88 is particularly one with three positions as shown in the figure, that is, it connects the supply/discharge circuit 85 that leads to the engagement oil chamber 35 of the side clutch 24 to the oil supply circuit 82, and also connects the side clutch 24 to the oil supply circuit 82. A supply/discharge circuit 86 connected to the oil chamber 36 and a supply/discharge circuit 87 connected to the oil chamber 54 of the handbrake 25 are connected to the tank circuit 84, and the side clutch 24 is engaged and the side brake 25 is engaged. Position ■ where 25 is inactive and especially the side clutch 24
A supply/discharge circuit 86 connected to the disengagement oil chamber 36 of the side clutch 24 is connected to the oil supply circuit 82, and a supply/discharge circuit 85 connected to the engagement oil chamber 35 of the side clutch 24 is connected to the oil chamber 54 of the side brake 25. A supply/discharge circuit 87 connected to the tank circuit 84 to disengage the side clutch 24 and deactivate the handbrake 25; and a supply/discharge circuit connected to the disengagement oil chamber 36 of the side clutch 24. A supply/discharge circuit 87 connected to the circuit 86 and the oil chamber 54 of the handbrake 25
is connected to the oil supply circuit 82 and the side clutch 24
position III, where the supply/discharge circuit 85 connected to the oil chamber 35 is connected to the tank circuit 84, the side clutch 24 is disengaged, and the side brake 25 is actuated.
The position is configured to be selectively switched.

In particular, as shown in Figures 3 and 4 and Figures 8 and 9,
Separate oil passage plates 89 and 90 are fixedly mounted on the outer surface of one side wall and the outer surface of the other side wall of the mission case 11, respectively.

As shown in FIGS. 8-10, the switching valve 76 and its attached mechanism are mounted on one half of the upper surface of the mission case 11, which has a two-part structure with a split surface. A valve mechanism housing 91 for accommodating the switching valve 88 and a valve mechanism housing 92 for accommodating the switching valve 88 and its auxiliary mechanism are fixedly provided on the other parts, respectively,
From the discharge port of the hydraulic pump 72, 73 to the valve mechanism housing 9
1 is formed between the oil passage plate 89 and the outer surface of one side wall of the transmission case 11, and a plurality of oil supply 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 as oil passages. The oil supply path P is formed between the plate 89 and the outer surface of one side wall of the transmission case 11, and the oil supply path P in the latter is connected to a seal housing 93.94 that fits over the shaft end of the power shift shaft 16, 17 and the power shift shaft 16, 17. The hydraulic clutch of the hydraulic clutch type transmission 23 is guided into the plurality of oil chambers R formed between the oil chambers R, and is connected to the hydraulic clutch of the hydraulic clutch type transmission 23 through oil passages (not shown) drilled in the power shift shafts 16 and 17 from within the oil chamber R. 67-70
The clutches 67-70 are guided to supply and discharge hydraulic oil and lubricating oil to the clutches 67-70.

Also, from inside the valve mechanism housing 91 to the valve mechanism housing 92
Inwardly, one oil supply path corresponding to the oil supply circuit 82 is connected to the discharge port of the hydraulic pump 73 and is led from the switching valve 88 in the housing 92 to the end of the side clutch shaft 18 and the side brake shaft 19. A plurality of oil supply passages P' leading to the end are formed between the oil passage plate 90 and the outer surface of the other side wall of the transmission case 11, and these oil supply passages P' are fitted onto the shaft end of the side clutch shaft 18. The oil is guided to both oil chambers 35 and 36 of the left and right side clutches 24 via the plurality of oil chambers R' formed between the seal housing 95 and the side clutch shaft 18 and the oil passages 37-40 of the side clutch shaft 18, and The oil is guided to the oil chambers 54 of the left and right hand brakes 25 through the plurality of oil chambers R'' formed between the shaft end of the hand brake shaft 19 and the case lid 46 and the oil passages 52, 53 of the hand brake shaft 19. ing.

In FIG. 4, reference numerals 96 and 97 are 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 in which the output shaft 20 is fixed and accommodates the output shaft 20.

The above has been explained in detail, but in short, the mission device according to this invention consists of a plurality of sets of hydraulic pressures disposed on a plurality of mutually parallel shafts 16, 17, 18, 19 in a mission case. Actuation mechanism 67, 68.69.
70.24.24.25.25, which is guided to the end of the shaft 16.17.18.19 on the outer surface of one side wall of the mission case 11 and on the outer surface of the other side wall. , separate oil passage plates 89 and 90 are provided to form oil supply passages P and P' for the hydraulic operating mechanism between the outer surface of the side wall of the mission case 11, and the hydraulic operating mechanism 6
7, 68. 69. 70. 24. 24. 25° 25 The above-mentioned plurality of shafts 16.
7.18.19 Oil chambers R, R, R' fitted into the ends of the oil passages for connecting the oil supply passage to the oil passage.

A plurality of oil chamber forming members 93, 94, 95, 46 forming R1/ with the shaft end are attached to the mission case 11.
This structure is characterized by being fixedly installed on the outer surface of one side wall and the outer surface of the other side wall, and has the following advantages.

That is, the mission device of this invention uses two oil passage plates that form an oil supply passage for the hydraulic operating mechanism between the outer surface of the side wall of the mission case, and the two oil passage plates 89.
90 on the outer surface of one side wall of the mission case 11 and the outer surface of the other side wall, the hydraulic operating mechanism 67 on some of the shafts 16 and 17 on which the hydraulic operating mechanism is mounted is installed. , 68.69° 70 from one side of the transmission case 11, and hydraulic actuation mechanisms 24.24° 25, 25 on the other shafts 18, 19 from the other side of the mission case 11. Each of the plurality of shafts is capable of supplying hydraulic oil, and an oil passage connected to the hydraulic operating mechanism thereon is bored. A plurality of oil chamber forming members 93, 94, which are provided in a number corresponding to the number of shafts 16, 17, 18, 19, which form oil chambers for connecting oil passages between the oil chamber forming members,
95.46 are installed separately on the outer surface of one side wall of the mission case 11 and on the outer surface of the other side wall. ' can be easily formed on the outer surface of the mission case 11 while avoiding mutual interference, and in particular can be formed on the outer surface of the side wall of the mission case 11 after being fitted onto the shafts 16, 17, 18° 19. A plurality of oil chamber forming members 93, 94, which are fixedly installed, occupy a large area on the outer surface of the side wall of the mission case because they have a fixing flange portion with an insertion hole for an individual fixture.
Since the 95° 46 is disposed on the outer surface of one side wall of the mission case 11 and the outer surface of the other side wall as described above, they do not interfere with each other, making it extremely easy to form the oil passage. It will become.

Actually, as shown in the embodiment, in addition to the hydraulic clutch type transmission 23 equipped with two power shift shafts 16 and 17 each equipped with a plurality of hydraulic clutches, hydraulically operated left and right Side clutch 24 and side brake 25
Separate side clutch shaft 18 and side brake shaft 1
9, the oil chamber forming members 93, 94, 95, 46 are provided only on one side of the mission case 11, instead of being distributed to one side and the other side of the mission case 11 as described above. For example, in the embodiment, an intermediate shaft is inserted between the power shift shafts 16, 17 and the side clutch shaft 18, and the shaft 16, 17 and the shaft 18 are interlocked and connected via the intermediate shaft. .17 and the shaft 18 so that the oil chamber forming members 93, 94, 95, 96 fitted to one end of each shaft 16, 17, 18, 19 do not interfere with each other. In such a case, the mission device becomes larger and the mission structure becomes complicated due to the intermediate shaft and the gears provided thereon, but this invention does not cause such problems. becomes.

Therefore, this invention also allows multiple types of hydraulically operated devices, which are extremely easy to operate because their operation is controlled by valve operation, to be installed in the mission mechanism of a traveling work vehicle without causing any other problems. What makes it possible to adopt
It has become.

[Brief explanation of the drawing]

Figure 1 is a side view of a combine equipped with an embodiment of this invention, Figure 2 is a diagram of the traveling power transmission mechanism of the combine, and Figures 3 and 4 show the upper half of the transmission case of the combine. Figure 5 is a schematic diagram showing the arrangement of gears, Figure 6 is a side view of the main parts, Figure 7 is a vertical cross-sectional development view of the lower half.
The figure is a hydraulic circuit diagram of the same embodiment, Figures 8 and 9 are a right side view and a left side view, respectively, of the mission case shown in Figure 3.4, and Figure 10 is a diagram of the upper mechanism of the mission case. FIG. 11...Mission case, 16.17...
... Power shift shaft, 18 ... Side clutch shaft, 19 ... Side brake shaft, 23 ...
... Hydraulic clutch type transmission, 24 ... Side clutch, 25 ... Side brake, 32,
33...Friction plate, 34...Piston,
35.36...Oil chamber, 3"l, 38...
・Oil passage, 46...Case lid, 48.49...
...Friction plate, 50...Cylinder body, 51...
... Piston, 52°53 ... Oil passage, 54
...Oil chamber, 67, 68.69.70...
・Hydraulic clutch, 89.90... Oil road plate, 91
．． 92... Valve mechanism housing, 93.94...
...Seal housing, 95...Seal housing, between P and P'...Oil supply path, R5R/, R//
...Oil room.

Claims (1)

[Scope of utility model registration request] A mission device is provided with a plurality of sets of hydraulic operating mechanisms disposed on a plurality of mutually parallel shafts in a mission case, and the above-mentioned one is provided on the outer surface of one side wall of the mission case and on the outer surface of the other side wall. Separate oil passage plates are provided that form oil supply passages for the hydraulic operating mechanism guided to the end of the shaft between the outer surface of the side wall of the transmission case, and an oil passage that continues to the hydraulic operating mechanism is provided. A plurality of oil chambers are formed between the ends of the plurality of shafts and are fitted into the ends of the plurality of shafts and form oil chambers for connecting the oil supply passage to the oil passage. A transmission device for a traveling work vehicle, characterized in that members are distributed and fixedly installed on the outer surface of one side wall of the mission case and on the outer surface of the other side wall.