JPH01169155A - Power take-off device - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed Description of the Invention] The present invention relates to a multi-stage gear transmission for traveling that changes the speed and transmits power to the traveling wheels, and a power take-off that changes the speed and transmits the power to the power take-off shaft. In a transmission equipped with a multi-stage gear transmission for power extraction, a hydraulic clutch 'aI!' in the multi-stage gear transmission for power extraction. This invention relates to a power extraction device that is equipped with a hydraulic brake to prevent the power extraction shaft from rotating (trailing) during Fi.

"]" A conventional agricultural machine that can be self-propelled by the power of an engine and can also drive a rotary work machine.

For vehicles such as commercial tractors, a power take-off system B as shown in Fig. 1 (see Japanese Patent Publication No. 58-22366) is used.
It was equipped with

In the power take-off device 01 shown in FIG. 1, a coupling 03 is attached to the rear end of a transmission shaft 02 connected to the engine.
The front end of the main shaft 04 is integrally connected via the main shaft 04.
A drive gear 05.06.07 is integrally formed with the drive gear 05.06.07, a power take-off shaft 08 is rotatably supported adjacent to the main shaft 04, and idler gears 09.09. 010. 011 is hydraulic clutch 012゜01
The hydraulic clutch 012.3 is fitted to the power take-off shaft 08 via the clutch 014. 013. By selectively supplying pressure oil to one of gears 014 and 09. 010. 011 is integrally connected to the power take-off shaft 08, and the power take-off shaft 08 is rotationally driven at a required gear ratio.

Further, a hydraulic brake 015 is provided at the front end of the power output shaft 08, and when pressure oil is not supplied to the hydraulic brake 015, the hydraulic brake 015 is in a braking state.
The hydraulic brake 015 is configured to be in a non-braking state when pressure oil is supplied to the hydraulic brake 015.

In the conventional power take-off device 01 shown in FIG. 015, it is not possible to provide a power take-off shaft separate from the power take-off shaft 08 in front of this power take-off device.

In addition, in the above-mentioned known device, since the traveling transmission is disposed in front of the power take-off device, the longitudinal length of the entire device becomes long, making it difficult to reduce the size and weight of the device.

The present invention relates to an improvement of a power take-off device that overcomes such difficulties, and aims to transfer engine power to a multi-stage gear shift WL for traveling.
Passing through E to the traveling heavy wheels 3! At the same time, in a transmission for transmitting power to a power take-off shaft via a multi-stage gear transmission for power take-off, the multi-stage gear transmission for power take-off is adjacent to and parallel to a side of the main shaft of the multi-stage gear transmission for traveling. The main shaft of the device is arranged, and the main shaft for power extraction is equipped with a hydraulic clutch that is detachably connected to the input shaft via a transmission means such as an IFI wheel or a chain sprocket. One power take-off shaft is fitted to one end so as to be relatively rotatable, and a power take-off counter shaft that is connected to the power take-off main shaft in a constant state is adjacent to the side of the power take-off shaft, and the power The multi-stage gear transmission for power extraction is disposed on the opposite side and parallel to the main shaft of the multi-stage gear transmission for traveling, sandwiching the main shaft for extraction, and is connected to the counter shaft for power extraction and the one power extraction shaft. Vt2! A hydraulic brake that does not brake or brake in conjunction with engagement and disengagement of the hydraulic clutch is provided at the end of the countershaft for power extraction on the power extraction main shaft side of the power extraction countershaft, and It is characterized in that the other power take-off shaft is detachably connected to the other end of the main shaft via a dog clutch.

Since the present invention is configured as described above, when the hydraulic clutch is connected after setting the multi-stage gear transmission for power extraction to a required gear ratio while the hydraulic clutch is disengaged, Interlocking with this, the hydraulic brake becomes a non-braking state, and the one power output shaft is rotationally driven at a required speed ratio. In this state, when the dog clutch is connected, the other power take-off shaft is also rotationally driven.

Furthermore, when the hydraulic clutch is disengaged in the output state of the power take-off device, the hydraulic brake is brought into a braking state in conjunction with this, the power take-off counter shaft is braked, and the power take-off multi-gear transmission is Since the main shaft of the power take-off shaft is also braked, even if there is a drag in the hydraulic clutch and the torque of the input shaft is transmitted to the main shaft, the output of the multi-stage gear transmission for power take-off is stopped and the connection of the power take-off shaft is stopped. Rotation is prevented.

Support 1 Hereinafter, an embodiment of the present invention applied to an agricultural tractor as shown in FIGS. 2 and 3 will be described.

Main clutch cases 2 are located at the front and rear ends of the transmission main case 1, respectively. A sub-mission case 3 is integrally attached, and an input shaft 5 is rotatably connected to the front wall 1a of the main transmission case 1, the end IJ12a of the main clutch case 2, and the rear wall 1b of the main clutch case 1 via bearings 4. supported.

Further, the front end of the input shaft 5 is connected to a crankshaft of an engine (not shown), and a travel drive gear 6 is integrally fitted to the input shaft 5, and a power output drive gear 7 is fitted via a one-way clutch 8. When the input shaft 5 is rotated in one direction, engine power is transmitted to the power take-off drive gear 7 via the one-way clutch 8, but from the power take-off drive gear 7 to the input shaft 5. Torque in one direction is not transmitted.

Furthermore, a main shaft 11 (hereinafter referred to as a main shaft for running) of a traveling multi-gear main transmission 10 is connected to the front wall 1a and the rear wall 1b of the transmission main case 1 via bearings 4 adjacent to the lower side of the input shaft 5.
The input shaft 5 is rotatably supported on the traveling main shaft 11.
A running latch gear 12° that meshes with the running drive gear 6 and the power take-off drive gear 7, respectively, and the power take-off idle gear 1.
3 is rotatably fitted, a tarlatch outer 15 of the running latch 14 is attached to the running latch gear 12, and a clutch inner 16 of the running latch 14 is attached to the running main shaft 11.
In Fig. 2, the clutch lever 17
By the counterclockwise operation, the clutch pressing member 18 is pushed rearward (to the right in FIG. 2), and the moving latch 14 is switched from the connected state to the disconnected state.

Furthermore, the traveling main shaft 11 has a reverse drive gear 19, a 1st speed drive gear 20 rotatably fitted from the rear to the front, and a 2nd speed drive gear 21, and a 3rd speed drive gear 22 are fitted integrally. Mission main case 1
A travel main counter shaft 23 is rotatably supported obliquely above and parallel to the travel main shaft 11 via bearings 4 on the front wall 1a and rear wall 1b of the travel main counter shaft 23, and a reverse driven gear 24 is attached to the travel main counter shaft 23. A first speed driven gear 25 is integrally formed, a second speed driven gear 26, a third speed driven gear 27 are rotatably fitted, and a reverse driven gear 24 is connected to the reverse drive gear 19 via a reverse idle gear r28. In addition, the first speed drive gear 20, the second speed drive gear 21, the third speed drive gear 22, the first speed driven gear 25, the second speed driven gear 26,
A third speed driven gear 27 is engaged.

Moreover, the reverse drive gear 19 of the traveling main shaft 11 is located adjacent to the first speed drive gear 20, and the reverse hydraulic clutch 29 is located adjacent to the first speed drive gear 20.
, a first speed hydraulic clutch 30 is disposed, and a second speed hydraulic clutch 31 and a third speed hydraulic clutch 32 are disposed adjacent to the second speed driven gear 26 and the third speed driven gear 27 of the traveling main counter shaft 23. clutch 29.1
Clutch inner 29a, 3 of quick hydraulic clutch 30
0a is reverse drive gear 19, 1st speed drive gear 2
The clutch inners 31a and 32a of the 2nd speed hydraulic clutch 31 and 3rd speed hydraulic clutch 32 are integrally connected to the 2nd speed driven gear 26 and the 3rd speed driven gear 27, respectively, and the reverse hydraulic clutch 29. 1st speed hydraulic clutch 30. By connecting any one of the 2nd speed hydraulic clutch 31 and 3rd speed hydraulic clutch 32, the running main counter shaft 23 is in reverse rotation, 1st speed, and 2nd speed.

It is designed to be rotationally driven in the third speed state.

In addition, the travel sub-counter shaft 34 of the travel multi-stage gear sub-transmission @33 is integrally connected to the rear end of the travel main counter @23 with a spline 1.
The traveling multi-stage gear auxiliary transmission 'eL33 is a shift gear transmission, and has a model wheel drive shaft 35 outside the traveling auxiliary counter shaft 34. It is provided with an idle shaft 36 and a front wheel drive shaft 37, and rear wheels and front wheels (not shown) are rotationally driven by a traveling multi-stage gear auxiliary transmission 33.

Next, the power extraction multi-stage gear transmission 40 will be explained.

Main @ 41 of the multi-stage gear transmission 40 for power take-off adjacent to the lower side of the traveling main shaft 11 (hereinafter referred to as the main shaft for power take-off)
is rotatably supported on the front wall 1a and rear wall 1b of the mission main case 1 via bearings 4, and the main shaft 41 for power extraction
is a gear 42 that meshes with the power take-off drive gear 7 of the input shaft 5.
is rotatably fitted.

Also, adjacent to the gear 42 is a hydraulic clutch 43 for power extraction.
The clutch inner 43a of the power extraction hydraulic clutch 43 is formed integrally with the gear 42, and the clutch outer 43b1. Main shaft 41 for tftll force taker ll
is integrally connected to the hydraulic clutch 4 for power extraction.
3 is set to the connected state, the gear 42 and the power take-off main shaft 41 are integrally coupled, and the power take-off main shaft 41 is rotationally driven.

Furthermore, a rear output gear 4 is provided at the rear of the main shaft 41 for power extraction.
4 is integrally formed, and a rear power take-off shaft 45
is fitted so as to be relatively rotatable, and the rear power take-off shaft 45
The rear portion of the transmission sub-case 3 is rotatably supported via a bearing 4 on the rear wall 3a of the sub-mission case 3.

Furthermore, adjacent to the lower side of the rear power take-off shaft 45, the rear power take-off counter shaft 46 is connected to the rear wall 1b of the transmission main case 1 and the rear wall 3a of the transmission sub-case 3 via the bearing 4.
The rear power take-off counter shaft 46 is rotatably supported on the
A counter gear 41 integral with the main shaft 41 is meshed with a rear output gear 44 of the main shaft 41 for power extraction.

In addition, the counter gear 4 is attached to the counter shaft 46 for taking out one part of the power.
Gears 48 with successively smaller diameters than 7. A gear 49 is integrally formed, and a gear 50 meshing with the gear 49 is rotatably fitted to the rear power take-off shaft 45, and a shifter gear 51 is spline-fitted to the rear power take-off shaft 45.

Further, a hydraulic brake 52 is disposed at the front end of the rear power take-off counter shaft 46, and the hydraulic brake 52 is connected to a brake housing 53 that is integrally connected to the rear wall 1b of the transmission main case 1, and slides in the axial direction on the brake housing 53. A brake piston 54 is fitted freely, a brake disc 55 is spline-fitted to the rear power takeoff shaft 46, and a brake disc 55 is locked to the brake housing 53 so as to be able to come into and out of contact with the brake disc 55. A compression coil spring 5 that urges the friction plate 56 and the brake disc 55 and the friction plate 56 to press against each other.
7, and the brake gear 58 formed by the brake housing 53 and the brake piston 54 is communicated with an oil passage 59 in the power take-off main shaft 41 and the rear power take-off shaft 45, and the power take-off hydraulic clutch 43 is also connected to the oil passage. 5
9, and when pressure oil is not supplied to the oil passage 59, the power take-off hydraulic clutch 43 is disconnected and the hydraulic brake 52 is set to a braking state, and the oil passage 59 is in communication with the oil passage 59.
When pressure oil is supplied to the hydraulic clutch 43 for power extraction, the hydraulic clutch 43 is connected and the hydraulic brake 52 is set to a non-braking state.

Furthermore, a front output gear 60 is integrally fitted to the iyi end of the power take-off main shaft 41, and is adjacent to the side of the power take-off main shaft 41, and is located at the front 11a of the transmission main case 1 and the end wall 2a of the main clutch case 2. A ttJ section power take-off shaft 61 is rotatably supported via a bearing 4, and a front output gear 60
A gear 62 meshing with the front power take-off shaft 61 is rotatably fitted to the front power take-off shaft 61, and a dog clutch 63 is spline-fitted to the front power take-off shaft 61 and the gear 62. When the dog clutch 63 is shifted rearward, The front power take-off shaft 61 and the gear 62 are connected, and when the dog clutch 63 is shifted forward, the front power take-off shaft 61 and the gear 62 are disconnected.

Since the embodiment shown in FIGS. 2 and 3 is configured as described above, the input shaft 5 is rotationally driven by the engine (not shown), and a counterclockwise operating force is applied to the clutch lever 11. If not, the running latch 14 is in a connected state, and the torque of the input shaft 5 is applied to the running drive gear 6, the running latch gear 12, and the running latch 14.
is transmitted to the traveling main shaft 11 via the main traveling shaft 11, and the traveling main shaft 11 is rotationally driven.

In this state of rotational driving of the main shaft 11, if pressure oil is supplied to connect any one of the reverse hydraulic clutch 29, 1st speed hydraulic clutch 30, 2nd speed hydraulic clutch 31, and 3rd speed hydraulic clutch 32, the main shaft 11 will be connected. The counter shaft 23 and the traveling sub-counter shaft 34 rotate in reverse or at 1, 2, and 3 speeds.

Then, when the clutch lever 17 is swung counterclockwise, the running latch 14 is brought into a disconnected state, and the running main shaft 11 is stopped.

Further, when pressure oil is supplied to the oil passage 59 while the input shaft 5 is rotationally driven, the power take-off hydraulic clutch 43 is connected, the hydraulic brake 52 is inactive, and the power take-off main shaft 41 is rotated. Driven.

When the power take-off main shaft 41 is rotationally driven, the shifter gear 51 is moved from the most advanced position (I) to the forward position (I[).
(III) (IV) k, s7rt, kit 49
．． ! : The meshing gear 50 is directly connected to the rear power take-off shaft 45 by the shifter gear 51 and is set to 1st speed, or the shifter gear 51 is not connected to any of them and is set to neutral, or the shifter gear 51 is meshed with the gear 48 and set to 1st speed. The second speed is set, and the rear power take-off shaft 45 is directly connected to the power take-off shaft 41 by the shifter gear 51, and the third speed is set.

Further, when the dog clutch 63 is shifted to the right in a state where the power take-off main shaft 41 is rotationally driven, the gear 62 is directly connected to the front power take-off shaft 61, and the front power take-off @61 is rotationally driven.

When the power take-off main shaft 41 is rotationally driven in this manner, when the pressure oil in the oil passage 59 is discharged, the power take-off hydraulic clutch 43 is disconnected and the hydraulic brake 52 is activated, and the power take-off hydraulic pressure is clutch 43
Even if drag remains in the power take-off multi-gear transmission 40 or rotational inertia acts on the power take-off multi-gear transmission 40, a braking force acts on the rear power take-off counter shaft 46 and the power take-off main shaft 41.
The rear power take-off shaft 45 and the front power take-off shaft 61 are immediately stopped.

Further, a power take-off soil shaft 41 is disposed below and adjacent to and parallel to the traveling main shaft 11 of the traveling multi-stage gear main transmission 10, and a rear power take-off shaft 41 is disposed below and parallel to the traveling sub-counter shaft 34. Since the rear power take-off counter shaft 46 is arranged and the power take-off multi-stage gear transmission 40 is configured in line with the traveling multi-stage gear main transmission 10, the overall length of the transmission does not increase and is made compact.

Furthermore, a hydraulic clutch 43 for power extraction of the multi-stage gear transmission 40 for power extraction is located between the 2nd speed drive gear 21 and the 3rd speed drive gear 22 in the traveling main @b11 of the traveling multi-stage gear main transmission 10, and The extraction hydraulic clutch 43 is connected to the traveling main counter shaft 2 with the traveling main shaft 11 in between.
Because it is arranged on the opposite side of the 2nd speed hydraulic clutch 31 and 3rd speed hydraulic clutch 32, the power take-off hydraulic clutch 43 is not interfered with by the 2nd speed hydraulic clutch 31 and the 3rd speed hydraulic clutch 32, and is connected to the traveling main shaft. 11, and by reducing the cross-sectional area of the transmission main case 1, the transmission can be formed compactly in the vertical and horizontal directions as well.

Furthermore, in the power take-off multi-stage gear transmission 40, a rear power take-off counter shaft 4G is disposed parallel to the rear power take-off shaft 45, and a rear power take-off counter @
Because the hydraulic brake 52 is attached to the @ end of 46,
Front power take-off shafts 61 before and after the main shaft 41 for power take-off.
A rear power take-off shaft 45 can be connected, and the front power can not be taken out from the front and rear ends of the transmission, and the rear power can also be taken out.

In this way, in the present invention, the hydraulic clutch attached to the main shaft for power extraction is detachably connected to the input shaft via a transmission means such as a gear or a sprocket. Therefore, one power take-off shaft and the other power take-off shaft can be arranged at both ends of the power take-off main shaft,
Since power can be extracted from two power extraction shafts, the transmission path is simplified. .

Further, in the present invention, the main shaft of the multi-stage gear transmission for power extraction is disposed adjacent to and parallel to the main shaft of the multi-stage gear transmission for traveling, so that By arranging the multi-stage gear transmission for power take-off adjacent to the power take-off main shaft, the length of the entire transmission can be shortened, and by arranging the traveling main shaft and the power take-off counter shaft as close as possible to the power take-off main shaft. , it is possible to make it smaller and lighter.

Furthermore, in a state in which the multi-stage gear transmission for the power take-off counter on one side and the dog clutch on the other side are set to a state other than neutral, the power take-off counter shaft is braked by the operation of the hydraulic clutch. The power take-off shafts of the two can be forcibly stopped at the same time.

[Brief explanation of the drawing]

FIG. 1 is a longitudinal sectional side view of a conventional power take-off device, FIG. 2 is a longitudinal sectional side view illustrating an embodiment of the power take-off device according to the present invention, and the third factor is a cross-sectional view thereof. 1...Mission main case, 2...Main clutch case, 3...Mission sub case, 4...Bearing, 5...
...Input shaft, 6...Travel drive gear, 7...Power extraction drive gear, 8...One-way clutch, 10...
Traveling multi-stage gear main transmission, 11... Traveling main shaft, 12.
... Latch gear for running, 13... Power extraction idle gear, 14... Latch for running, 15... Clutch outer, 16... Clutch inner, 17... Clutch lever 118... Clutch suppression Part, 19...
Reverse drive gear, 20...1st speed drive gear,
21... 2nd speed drive gear, 22... 3rd speed drive gear, 23... Travel main counter shaft, 24... Reverse driven gear, 25... 1st speed driven gear, 26...
...2nd speed driven gear, 27...3rd speed driven gear,
28... Reverse idle gear, 29... Reverse hydraulic clutch, 30... 1st speed hydraulic clutch, 31...
・2nd speed hydraulic clutch, 32...3rd speed hydraulic clutch, 3
3... Travel multi-stage gear sub-transmission device, 34... Travel sub-counter shaft, 35... Rear wheel drive shaft, 36... Idle shaft, 37... Front wheel drive shaft, 40... Power Multi-stage gear transmission for extraction, 41... Main shaft for power extraction, 42
... Gear, 43 ... Hydraulic clutch for power extraction, 4
4... Rear output gear, 45... Rear power take-off shaft,
4B... Rear power take-off counter shaft, 41... Counter gear, 4g, 49.50... Gear, 51...
Shifter gear, 52... Hydraulic brake, 53... Brake housing, 54... Brake piston, 55...
...Brake disc, 56...Friction plate, 57...
Compression coil spring, 58...Brake chamber, 59.
...Oil passage, 60...Front output gear, 61...Front power take-off shaft, 62...Gear, 63...Dog clutch.

Claims (2)

[Claims] (1) In a transmission that transmits the power of the engine to the running wheels via a multi-stage gear transmission for traveling and to a power extraction shaft via a multi-stage gear transmission for power extraction, the multi-stage gear transmission for traveling The main shaft of the multi-stage gear transmission for power take-off is disposed adjacent to and parallel to the main shaft of the device, and the main shaft for power take-off is connected to an input shaft and a transmission means such as a gear or a chain sprocket. A hydraulic clutch is attached to the hydraulic clutch which can be engaged and disengaged from the main shaft, one power take-off shaft is relatively rotatably fitted to one end of the power take-off main shaft, and the power take-off shaft is connected to the power take-off main shaft in a constant state. A power take-off counter shaft is adjacent to the side of the power take-off shaft, and is disposed parallel to the main shaft of the traveling multi-stage gear transmission on the opposite side of the power take-off main shaft, sandwiching the power take-off main shaft. The power take-off counter shaft and the one power take-off shaft are provided with the power take-off multi-gear transmission, and the power take-off counter shaft end on the power take-off main shaft side of the power take-off counter shaft is provided with the hydraulic clutch. A power extraction device characterized in that a hydraulic brake is provided that does not brake or brake in conjunction with engagement and disengagement, and the other power extraction shaft is detachably connected to the other end of the power extraction main shaft via a dog clutch. Device. (2) The power take-off device according to claim 1, wherein pressure oil is simultaneously supplied to or discharged from the hydraulic clutch and the hydraulic brake through the same hydraulic path.