JPS5857340B2 - Traveling power transmission device for traveling work vehicles - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a traveling power transmission device for an agricultural or other traveling working vehicle.

That is, the present invention provides a side clutch and a side brake provided in this type of traveling power transmission device that are easy to operate, compact, and have a simple structure in a self-propelled working vehicle. The present invention aims to provide a novel driving power transmission device.

The configuration of the traveling power transmission device according to the present invention will be explained with reference to the illustrated embodiment.
As shown in the figure, while the combine harvester, that is, the left and right traveling crawlers 1, moves the machine, the weed cutting body 2 at the front of the machine divides the culm to be planted in the field, and the machine moves diagonally backward and upward in front of the machine. Culm lifting device 3 installed at an angle
At the same time, the planted culm is pulled up at the base of the plant by the cutting blade 4 at the lower front end of the machine body, and the cut culm is transported to a position on the side of the machine body by the lower conveying device 5. After that, the shell culm is fed to the threshing section I by the vertical transport device 6, and threshing is carried out while the cut husk is transported rearward at the base of the stock by the feed chain 8 marked on one side of the threshing section 7. This is an example implemented in a combine harvester configured to supply straw leaving a threshing section 7 to a cutter device 10 by a straw conveying device 9.

A mission case 11 is placed at a suitable location in the front of the combine, and as shown in FIG. As shown in FIG. 2-4, inside this mission case 11 are a mission input shaft 14 and a gear shift shaft 1.
5, the two power shift shafts 16 and 17, the side clutch shaft 18, the hand brake shaft 19, and the left and right transmission output shafts 20 are provided in parallel to each other,
The transmission input shaft 14 supports the input pulley 12 on one end thereof and connects the input 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 shafts 16 and 17, and left and right side clutches 24 are further disposed on the side clutch shaft 18.
On the side brake shaft 19 are left and right side brakes 25.
are respectively arranged, and the left and right mission output shafts 20 are interlocked and connected to a drive wheel 26 that rotationally drives the traveling crawler 1, and the end of the power shift shaft 16 has an inwardly expanding type as shown in the figure. However, the left and right side clutches 24 and the handbrake 25 described above are particularly hydraulically operated as described below.

That is, first, as shown in FIGS. 2 and 4, on the single side clutch shaft 18, a large-diameter input gear 28 is provided at the center, and this input gear 28 is connected to a fifth gear.
As shown in the figure, a pair of fixed gears 29 and 30 on both power shift shafts 16 and 17 are meshed with each other to drive the rotation, and a pair of left and right output gears 31 are provided on the side clutch shaft 18. The left and right side clutches 24 are constructed by disposing between the gears 28 and 31 a multi-disc hydraulic clutch that selectively interlocks and connects the input gear 28 and each output gear 31. be.

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 human power gear 28 is provided so as to be slidably supported only in the axial direction, and the human power gear 28 is provided at the boss portion of each output gear 31.
A friction plate support part 31a that can extend in the direction is formed, and the other friction plate 33 is supported by the support part 31a so that it can only slide freely in the clutch axis direction, and a clutch is provided between the input gear 28 and the left and right output gears 31. Pistons 34 that are slidable along the axial direction are respectively arranged, and oil chambers 35 and 36 are formed on one side and the other side of each piston 34, and the side clutch shaft 18
When supplying pressurized oil to the oil chamber 35 on the input gear 28 side through oil passages 37 and 38 bored in the piston, the piston 34 is moved forward toward the output gear 31, and the friction plates 32 and 33 are brought into pressure contact. The clutch 24 is engaged and the human gear 28 is engaged.
and the output gear 31 are interlocked and connected, and the output gear 31
When supplying pressure oil to the side oil chamber 36, the piston 34 is moved back toward the human gear 28, the pressure contact between the friction plates 32 and 33 is released, and the clutch 24 is disengaged. The left and right side clutches 24 are configured so that the interlocking connection between them is broken.

Furthermore, as shown in FIG. 6, a plurality of spring housing holes 41 are intermittently formed in each surface of the human gear 28 in the circumferential direction. 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 state where there is no hydraulic action on the separation action oil chamber 36 due to the spring-loaded type, the action of the compression spring 42 will cause the friction plates 32, 33 to are brought into pressure contact with a slight engagement force, and the clutch 24 is configured to be able to transmit a torque under the plate which is smaller than the normal transmission torque of the clutch 24 through this clutch 24, This latter torque, which is determined by the spring force of the compression spring 42, is made approximately equal to the brake capacity of the parking brake 27, which is located at the front stage of the side clutch 24.

Furthermore, the left and right hand brakes 25 described above are constructed as hydraulically operated types as follows.

That is, as shown in FIGS. 2 and 4, the single side brake shaft 19 has a single side clutch shaft 18.
- The left and right large diameter gears 43 meshed with the left and right output gears 31 of H are loosely fitted, and each of the large diameter gears 4
Small diameter gear 4 that can be integrally attached to 3 with a common boss part
4 is meshed with the large-diameter gears 45 on each of the mission output shafts 20 to transmit deceleration to the left and right mission output shafts 20. Left and right case lids 46 are made to extend in the opposite direction to the gear 44 and serve as friction plate support portions 43a, and are fixed to the transmission case 11 at the end of the handbrake shaft 19.
, 47, respectively, are integrally formed with friction plate support parts 46a and 47a that can extend inward to the case 11, one friction plate 48 being used as the friction plate support part 43a, and the other friction plate 49 being used as the friction plate support part. 46a and 47a, each of which is slidably supported in the axial direction of the shaft 19, and a cylinder body 50 having left and right cylinder portions 50a is provided on the center of the handbrake shaft 19, and the inside of each cylinder portion 0a is provided. A piston 51 that is slidable in the axial direction of the shaft 19 is disposed at the side, and pressure oil is supplied to an 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 pressed against the friction plates 48 and 49 by the advance of the piston 51.
The left and right side brakes 25 are configured as hydraulically operated multi-plate brakes that are selectively fixed to the fixed case lids 46 and 47 to selectively brake the left and right transmission output shafts 20, and therefore the left and right axles 26a. be.

As shown in FIG. 7, oil is supplied to the side clutch 24 and the side brake 25, which are hydraulically actuated as described above, from an oil tank 71 to a hydraulic pump 73 through an oil supply circuit. This oil supply circuit 82, whose oil pressure is set by a pressure regulating valve 83, is a left oil supply circuit connected to a left side clutch 24 and a side brake 25, as shown in the figure. 82L and a right oil supply circuit 82R connected to the right side clutch 24 and hand brake 25, and this left and right oil supply circuit 82L.

82R each has a pump port and tank circuit 8 on the primary side.
4, the tank port connected to the side clutch 2, and the 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 a supply/discharge circuit 86 communicating with the oil chamber 36 of the handbrake 25, and a port connected to a supply/discharge circuit 87 communicating with the oil chamber 54 of the hand brake 25.
The respective switching valves 88 are connected to the pump port, and each of the five switching valves 88 has three positions as shown in the figure, that is, the side clutch 2
A supply/discharge circuit 85 connected to the engagement oil chamber 35 of No. 4 is connected to the oil supply circuit 82, and a supply/discharge circuit 86 connected to the disengagement oil chamber 36 of the side clutch 24 and the side brake 25.
A supply/discharge circuit 87 connected to the oil chamber 54 is connected to the tank circuit 84.
position I, where the side clutch 24 is engaged and the side brake 25 is deactivated, 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 82. The side clutch 24 is disengaged by connecting the supply/discharge circuit 85 connected to the engagement oil chamber 35 of the side clutch 24 and the supply/discharge circuit 87 connected to the oil chamber 54 of the side brake 25 to the tank circuit 84. position (2) where the side brake 25 is deactivated at the same time as the side clutch 24, and the supply/discharge circuit 86 connected to the disengagement oil chamber 36 of the side clutch 24 and the supply/discharge circuit 87 connected to the oil chamber 54 of the side brake 25. The supply/discharge circuit 85 connected to the oil supply circuit 82 and connected to the engagement oil chamber 35 of the side clutch 24 is connected to the tank circuit 84 to disengage the side clutch 24 and operate the side brake 25. It is configured to be selectively switched to three positions.

Next, the basic structure of the gear transmission 22 and the hydraulic clutch type transmission 23 will be explained with reference to FIGS.
4, and four shift gears 58, 59, 60, and 61 fixed on the gear shift shaft 15. When the shift gear 56a of the shift gear pair 56 meshes with the speed change gear 58, the first speed is set, and when the cyst gear 56b meshes with the speed change gear 59, the second speed or the shift gear 57a of the shift gear pair 57 meshes with the speed change gear 60. and 3rd speed, or 4th speed when the shift gear 57b is engaged with the speed change gear 61, respectively.

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 17 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 17 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.
F1 hydraulic clutch, which is a multi-disc hydraulic clutch of a conventional structure, is provided with four idler gears 63-66 with a gear 66, and each idler gear 6'3-66 is disposed on the power shift shaft 16 or 17. 67, F2 hydraulic clutch 68, F3 hydraulic clutch 69 and R? A hydraulic clutch 67 which is a 41-t mechanical pressure clutch 67-70 with a hydraulic clutch 70 and selectively connects each free rotating gear 63-66 to the power shift shaft 16 or 17 by its engagement. -70.

Pressure oil is supplied to the hydraulic clutches 67 to 70 in the hydraulic clutch type transmission 23 by a hydraulic pump 72 from the oil tank 71 via an oil supply circuit 74, and the oil pressure is set by a pressure regulating valve 75. The oil supply circuit 74 includes
Neutral position N where oil is drained from all hydraulic clutches 67-70, forward first speed position F1 where oil is supplied to F1 extraction clutch 67 and oil is drained from other hydraulic clutches 68°69.70, and F2 extraction pressure. Forward 2nd speed position F2 where the clutch 68 is refueled and oil is drained from the other hydraulic clutches 68, 69, 70, and F3 extraction clutch 69 is refueled and oil is drained from the other hydraulic clutches 67, 68, 70. A switching valve 76 is inserted that has a forward third speed position F3 and 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.
The oil drain circuit 77 from -70 is connected to the IJ IJ of the pressure regulating valve 75.
- A connection circuit between the oil circuit 77 and a tank circuit 79 which is connected to the lubricating oil supply circuit 78 to the hydraulic clutches 67-70 together with the hydraulic clutch 67-70 and returns the lubricating oil from the hydraulic clutches 67-70 to the oil tank 71 is lubricated. Pressure regulating valve 80 for oil pressure setting
is inserted, and an accumulator 81 is attached to the oil supply circuit 74.

As shown in Figures 3 and 4 and Figures 8-10, an oil passage plate 89 is fixedly mounted on one side of the mission case 11, and an oil passage plate 90 is fixedly attached on the other side. On the upper surface of the mission case 11, a valve mechanism housing 91 for accommodating the switching valve 76 and its auxiliary mechanism is provided on one half of the case 11, which has a two-sided structure with a split surface.
A valve mechanism housing 92 for accommodating the switching valve 88 and its auxiliary mechanism is fixedly provided on the other parts, and the hydraulic pump is directly connected to the mission input shaft 14 as shown in FIG. Oil supply passages leading from the discharge ports 72 and 73 into the valve mechanism housing 91 are formed between the oil passage plate 89 and the outer surface of the transmission case 11, and from inside the valve mechanism housing 91 to the ends of each power shift shaft 16 and 17. A plurality of oil passages P that communicate with each other connect the oil passage plate 89 and the transmission case 11.
The latter oil passage P is formed between the outer surfaces of the seal housing 9 that fits over the shaft ends of the power shift shafts 16 and 17.
3.94 and the power shift shafts 16.17, and an oil passage (not shown) to be drilled from inside the oil chamber R to the power shift shafts 16, 17. The hydraulic oil is supplied to the extraction clutches 67-70 of the hydraulic clutch type transmission 23 through the hydraulic clutch type transmission device 23, and the hydraulic oil is supplied to and discharged from the clutches 67-70, and the lubricating oil is supplied to the clutches 67-70. \
The oil supply circuit 8 is connected to the discharge port of the hydraulic pump 73 from inside the housing 91 to the inside of the valve mechanism housing 92.
A plurality of oil supply passages P' leading from the switching valve 88 in the housing 92 to the ends of the side clutch shaft 18 and the side brake shaft 19 are connected to the oil passage plate 90 and the outer surface of the transmission case 11. These oil supply passages P' are formed between a plurality of oil chambers R' formed between the side clutch shaft 18 and a seal housing 95 fitted into one end of the single side clutch shaft 18. Side clutch shaft 1
The left and right side clutches 2 through the oil passages 37-40 of 8.
4 and the plurality of oil chambers R" formed between one end of the single handbrake shaft 19 and the case lid 46 and the oil passage 52 of the handbrake shaft 19. 53 to the oil chamber 54 of the left and right side brake 25.
being led to.

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 that is fixed and accommodates the output shaft 20.

Although detailed explanation has been given above, in short, the traveling power transmission device for a traveling work vehicle according to the present invention has a single side clutch shaft 18 located on the front stage side and a single side clutch shaft 18 located on the rear stage side in the traveling power transmission path. A single handbrake shaft 19 is provided above and below parallel to each other, and on the side clutch shaft 18 there are left and right hydraulically actuated side clutches 24 with the shaft 18 as a support shaft. 1
Left and right hydraulically actuated side brakes 25 with the @19 as a spindle are respectively disposed on the 9, and a hydraulic power supply that operates the left and right side clutches 24 and the side brakes 25 in relation to each other is provided. It is constructed with a discharge device and has the following advantages.

That is, the traveling power transmission device of the present invention has the left and right side clutches 24 and the side brakes 25 of a hydraulically operated type, and a hydraulic supply/discharge device that operates these side clutches 24 and side brakes 25 in relation to each other. Since the side clutches and side brakes are provided with Since the brake 25 is provided, the mission period is not expanded unlike when the left and right side brakes are provided on both sides of the left and right side clutches, and the transmission period is reduced, making it more compact. Since the side clutch shaft 18 and the side brake shaft 19 are each configured as a single shaft, the structure itself is already far simplified, and the support shaft 18°1 of each vehicle is
For the left and right side clutches 24 and left and right side brakes 25 provided on the respective vehicles, the oil passages for hydraulic oil are connected from one side of the transmission case to the support shafts 18 and 25, respectively, as shown in the embodiment. 19, which simplifies the structure of the hydraulic oil supply and discharge passages compared to the case where separate support shafts are provided on the left and right sides. The oil passage and brake curved passage can be led to the transmission case side, and in this respect, the device can also simplify the hydraulic oil supply and discharge structure.

[Brief explanation of the drawing]

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 components, FIG. 7 is a hydraulic circuit diagram of the same embodiment, and FIGS. 8 and 9. The figures are a right side view and a left side view of the mission case shown in FIGS. 3 and 4, respectively, and FIG. 10 is a plan view of the upper mechanism of the mission case. 11...Mission case, 18...
Side clutch shaft, 19... Side brake shaft, 24... Side clutch, 25...
Handbrake, 28...Input gear, 31...
...Output gear, 32, 33...Friction plate, 3
4...Piston, 35.36...Oil chamber, 37,38...Oil passage, 43...Large diameter gear, 44...・Small diameter gear, 46, 47...
...Case lid, 48.49...Friction plate, 50.
...Cylinder body, 51 ...Piston, 5
2,53...Oil passage, 54...Oil chamber, 7
3...Hydraulic pump, 82, 82L. 82R... Oil supply circuit, 84... Tank circuit, 85° 86.87... Supply and discharge circuit, 88.
...Switching valve.

Claims (1)

[Claims] 1. In the traveling power transmission path, a single side clutch shaft located on the front stage side and a single hand brake shaft located on the rear stage side are provided vertically parallel to each other, and the corresponding side clutch shaft is provided on the side clutch shaft. The left and right hydraulically operated side clutches are mounted on the shaft, and the left and right hydraulically operated side clutches are mounted on the handbrake shaft. A traveling power transmission device for a traveling work vehicle, which is provided with a hydraulic supply/discharge device that operates a clutch and each side brake in conjunction with each other.