JPS62270866A - Oil feeding structure in hydraulic gear shifter - Google Patents

Abstract

PURPOSE:To aim at simplification in a hydraulic pipe line, by inserting a feed oil pipe rotatably in a relative manner along an axial center part, and interconnecting this feed oil pipe to a hydraulic clutch by way of an oil passage in a shaft, in case of a device which installs plural shafts concentrically and also installs the hydraulic clutch on these shafts. CONSTITUTION:A shaft, for example, a first main shift shaft S1 of a hydraulic gear shifter is supported on a bearing in a transmission case, and a clutch shaft 20 of a main clutch 17 is installed on the same shaft at the one end side of this shaft S1. The main clutch 17 is provided with a sprocket 18, where engine power is transmitted, at the driving side. Each of hydraulic gear shifting clutches 40 and 41 of 2-speed and 3-speed is installed in both main shift shafts S1 and S2. In this case, a hole 60 to be interconnected to a hole 59 in an axial direction installed in an axial center part of the clutch 20 is formed at the front end side of the shaft S1, and internal-external two pieces of feed oil pipes 61 and 62 different in diameter are concentrically inserted into both these holes 59 and 60. And, these feed oil pipes 61 and 62 are interconnected to respective hydraulic clutches 40 and 41 via oil passage 51 and 65, etc., inside the shaft S1.

Description

DETAILED DESCRIPTION OF THE INVENTION 3. Detailed Description of the Invention U-vertical delta plate 1 The present invention relates to a transmission device for various vehicles such as automobiles and tractors.

In the above vehicle, in order to effectively utilize the output of the engine, a transmission is installed in the power transmission system that transmits the torque generated by the engine to the drive width, etc. This allows the ratio of rotational speeds to be varied in accordance with driving conditions.

Most of the above-mentioned transmissions have two shafts arranged parallel to each other and are selectively connected through pairs of gears with various tooth ratios. The said gear is connected to the shaft via the hydraulic clutch by engaging a hydraulic clutch mounted on said shaft adjacent to said gear, and in this way connects said gear to the shaft through the gear connected to said shaft. There is one that transmits rotation to monks.

However, in this type of hydraulic transmission, hydraulic oil is supplied to the hydraulic clutch on the shaft through an oil passage drilled in the shaft, so it is necessary to install a hydraulic clutch. An oil inlet must be provided at each shaft angle and each of these oil inlets must be connected to a hydraulic pump. Therefore, the hydraulic piping from the hydraulic pump to each oil inlet becomes complicated, and sufficient space is required for these piping and the oil inlets within the device, which tends to make the entire device large.

-V'' to make 171vP and: Therefore,
In the present invention, in a hydraulic transmission device in which a plurality of shafts are arranged on the same @ line and a hydraulic clutch is provided on at least one shaft, the shaft center portions of adjacent shafts marked with na are aligned in the axial direction. An oil supply pipe is inserted therethrough so as to be rotatable relative to at least one shaft, and the oil supply pipe is communicated with the hydraulic clutch via an oil passage within the shaft.

According to the invention, on all two or more axes,
Hydraulic oil and lubricating oil can be supplied from one end of one shaft through the oil supply pipe inserted through the axial center of these shafts, so the space required for the oil inlet can be reduced to the end of one shaft. It can be organized into sections. Additionally, the number of hydraulic piping from the hydraulic pump to the oil inlet is reduced and simplified, making the entire device more compact. Since the oil supply pipe is inserted through at least some of the shafts so as to be relatively rotatable, each shaft can be rotated independently.

Support iJ Hereinafter, the present invention will be described with reference to illustrated embodiments.

FIG. 1 is a side view of an agricultural tractor to which the present invention is applied.
1 is the rear wheel, and 2 is the front wheel. Engine 3 is mounted on the front of the vehicle body, and Mitsushicon case 4 is mounted on the rear. The output shaft of the engine 3 is connected to a propeller shut 6 via a reduction gear 5, and the propeller shut 6 extends rearward from the lower part of the vehicle body and is connected to an input @7 of the transmission case 4. The transmission case 4 is fixed to a vehicle body frame 8, a part of which is shown in fragmentary form, and has a built-in hydraulic transmission device, which will be described later. The engine power input to the input shaft 7 is suitably shifted through the hydraulic transmission and then transferred to the rear axle 9, the PTO shaft S4, and the front wheel drive shaft S.
5 is output. The PTO shaft S4 transmits power to a working machine such as a rotary work machine connected to the rear of the tractor. The front wheel drive shaft S5 transmits power to the front wheels 2 via the front wheel drive propeller shaft 10. 11 is a hydraulic cylinder,
The work machine is raised and lowered via the lift arm 12.

13 is a seat, and 14 is a handle.

FIG. 2 is a sectional view showing the power transmission 31 inside the mission case 4. As shown in FIG.

Input @7 coupled to propeller shaft 6 as described above
is rotatably supported by a transmission case 4 and a clutch housing 15 fixed thereto via bearings, and a sprocket 16 is fixed to this input shaft 7. The sprocket 16 transmits engine power to a sprocket 18 provided on a hot multi-plate main clutch 17 via a chain.

As shown in an enlarged view in FIG. 3, the main clutch 17 has a clutch shaft 20 that is pivotally supported by the transmission case 4 via a ball bearing 19, and the sprocket 18 is connected to the clutch @20 by a clutch shaft 20. It is relatively rotatably supported via a bearing 21 . A bottomed cylindrical drive member 23 is fixed to the sprockets 1 to 18 via a spring member 22 in order to absorb the impact when the clutch is connected.
A plurality of drive clutch plates 24 are received on the inner circumferential surface of the clutch plate 3 via splines so as to be displaceable in the axial direction. A driven member 25 having a cylindrical shape at the bottom right is also integrally fixed to the clutch shaft 20 . A plurality of driven clutch plates 26 are received on the outer circumferential surface of the driven member 25 via splines so as to be displaceable in the axial direction, and these driven clutch plates 26 and the driving clutch plates 24 are arranged alternately. Arranged. A disc-shaped pressure contact plate 27 having approximately the same diameter as the flange 25a provided at the end of the driven member 25 is provided so as to rotate integrally with the driven member 25 and to be relatively displaceable in the axial direction. ing.

The press plate 27 has a boss 28 that protrudes through a hole provided in the bottom wall of the driven member 25, and a lifter plate 29 is fixed to the end surface of the boss 28. A coil spring 30 is sandwiched between the lifter plate 29 and the bottom wall surface of the driven member 25, and is normally used in a direction in which the flange 25a of the driven member 25 and the pressure contact plate 27 are brought closer together, that is, the drive clutch plate. A biasing force is applied in the direction of pressing the driven clutch plate 24 and the driven clutch plate 2G together. The lifter plate 29 is connected to the actuating part 32 via the ball itt holder 31.
The actuating member 32 is pressed against the coil spring 30 by a lever 33 and is pressed against the plate 2.
7 side along the clutch shaft 20,
The pressing plate 27 moves away from the seventh flange 25a of the driven member 25, and the pressed state between the drive clutch plate 24 and the driven clutch plate 26 is released. That is, the main clutch 17 is in a disengaged state.

A gear G13 is integrally formed at the end of the clutch shaft 20 that protrudes into the transmission case 4. The end of the first main transmission shaft S1 is also supported coaxially and relatively rotatably via a needle bearing 34 at this end. The first main transmission shaft S1 extends back and forth within the mission case 4, with its other end and intermediate portion supported by ball bearings 35, 35, . . . , respectively.

A second main transmission @ adjacent to and parallel to the first main transmission axis S1
S2 is provided. The second main transmission shaft S2 is rotatably supported by the front wall of the transmission case 4 and a bearing wall 36 provided on the transmission case 4 via ball bearings 37 and 38, respectively. A gear G23 that constantly meshes with the gear G13 of the clutch @20 is fixed to the front end of the second main transmission shaft S2. The tooth width G13 and the tooth width G23 have the same diameter, so that the second main transmission shaft S2 can be moved from the clutch shaft 20 to the gear G13. It is rotationally driven via G23 at the same rotational speed as the clutch @20.

The first main shift 'MS1 and the second main shift shaft S2 constitute ITi+ of the hydraulic transmission 39, and the first main shift @S1 is equipped with a 2-speed hydraulic shift clutch 40 and a 3-speed hydraulic shift clutch 41. A low-speed hydraulic transmission clutch 42 and a 4-speed/reverse hydraulic transmission clutch 43 are attached to the second main transmission shaft S2. Since each of these clutches has substantially the same construction, the construction of the two-speed hydraulic transmission clutch 40 will be described in detail with reference to FIG. The 2-speed hydraulic transmission clutch 40 includes a bottomed cylindrical clutch outer member 44 fixed to the first main transmission shaft, and an annular bearing plate 45 is fixed to the M end surface between the clutch outer member 44. ing. Then, on the inner circumferential surface, the receiver faces the plate 45,
Similar to the drive clutch 24 in the first clutch 17, a latch plate 46 is received via a spline so as to be displaceable in the @ line direction. The clutch outer member 44 has a peripheral wall portion 44a, a bottom wall portion 44b, and a first main shift shaft S1.
An annular cylinder portion 47 is formed by a boss portion 44c fitted to the
An operating member 48 is fitted into the cylinder portion 47 in the shape of a piston, and a spring 49 causes the bottom wall portion 4 to
4b. An oil passage 50 is provided in the boss portion 44c to which hydraulic pressure can be supplied between the operating member 48 and the bottom wall portion 44b of the clutch outer member 44, and this oil passage 50 is located within the first main transmission shaft S1. It communicates with an oil passage 51 which is formed in and supplied with oil via a control system from a hydraulic pump which will be described later. A gear G12 is mounted on the needle bearing 5 on the first main transmission shaft S1 adjacent to the clutch outer member 44.
It is rotatably mounted via 2. The gear G12 has a clutch inner member 5 of the 2nd speed pressure transmission clutch 40.
3 is integrally formed and enters into the cylinder portion 47 of the club chia outer member 44. A plurality of clutch plates 54 are received in the axial direction on the outer peripheral surface of this clutch inner member 53 via splines, and these clutch plates 54 and the clutch plates 46 are arranged alternately. When actuating oil is supplied behind the actuating member 48 through the oil passage 51.50 due to the speed change operation, the actuating member 4
8 is pressed by hydraulic pressure and presses the clutch 1i46.
0 to the first main transmission shaft S1. Gear G12
meshes with the gear G22 fixed to the second main transmission shaft S2, so the rotation of the second main transmission shaft S2 is caused by the rotation of the first main transmission shaft S1.
, and a shift to the second speed is performed.

The third speed shift is achieved by connecting the gear G13 to the first main shift shaft S1 via the third speed hydraulic shift clutch 41 and directly transmitting the rotation of the clutch shaft 20 to the first main shift @S1. 1. In this embodiment, the clutch outer member of the third-speed hydraulic transmission clutch 41 is formed integrally with the clutch outer member 44 of the second-speed hydraulic transmission clutch 40. Low-speed (first speed) shifting is performed by a low-speed hydraulic transmission clutch 42. Shifting to the 4th speed is performed via the gear G21 and the gear G11, and the 4th speed and 1p advance hydraulic transmission clutch 43. Gear G24. Reverse gearing is performed via gear Q14, which also serves as 4th gear (rear) W hydraulic gear shifting clutch 43. This is done via a gear G2R1, an idle gear (not shown), and a gear G111. The selector 55 is a selector that is connected to the first main transmission shaft S1 in a manner that selects the gear G14 or the gear G1. The rotation of the first main transmission shaft S1 is transmitted to the auxiliary transmission shaft S3 via the auxiliary transmission 56, and is transmitted to the rear vehicle @9 (FIG. 1) via a differential gear and an Rtn reduction gear (not shown in detail). communicated.

A pump shaft SP is roughly arranged in the mission case 4. A gear G is fixed to the pump shaft SP, and the gear Gp is always meshed with a gear G7 fixed to the input shaft 7. The front end of the pump shaft SP is connected to a hydraulic pump 51, which is a gear pump, for example, which is fixed to the transmission case 4, and the pump 57 is connected to the pump shaft SP.
Driven by P.

A portion of the oil discharged from the hydraulic pump 57 is forced into an oil inlet 58 provided at the front end of the clutch shaft 20 of the main clutch 17 via an oil passage (not shown) provided along the clutch housing 15. be done. As shown in Figure 3,
An axial hole 59 passes through the center of the clutch shaft 20 in the front and back, and a needle bearing 3 is provided at the rear end of the clutch shaft 20.
A hole 60 coaxial with the hole 59 is also provided at the front end portion of the first main transmission @S1 whose front end is pivotally supported via the hole 59. Inside these holes 59 and 60, there are two oil supply pipes 61, inside and outside, with different diameters. f32 are inserted concentrically, and the rear ends of these oil supply pipes 61 and 62 are respectively connected to seal and bearing members 6.
3.64, and is rotatably supported on the first main transmission shaft S1. The front ends of the oil supply pipes 61 and 62 extend to the oil distribution inlet portions 58, each of which has an oil inlet 58a.
, 58b are formed.

The oil supply pipe 61 is provided with a control valve mechanism that responds to a shift operation that transmits rotation from the second main shift shaft S2 to the first main shift shaft S1 through the two-speed hydraulic shift clutch 40. The oil discharged from the hydraulic pump 57 is guided as clutch hydraulic oil from the oil inlet 58a. Similarly, the oil supply pipe 62 is connected to the clutch shaft 20 through the 3rd speed hydraulic transmission clutch 41.
(rotation is transmitted from to the first main transmission shaft S1)! When a speed change operation is performed, the oil discharged from the hydraulic pump 57 is guided as clutch hydraulic oil from the oil inlet 58b. The hydraulic oil led to the oil supply pipe 61 flows through the oil passage 5113 bored in the radial direction inside the first main transmission @S1 and the clutch outer member 44.
2 through the oil passage 50 provided in the boss portion 44C of the
The transmission is guided to the hydraulic transmission clutch 40 and engages the clutch. The hydraulic oil guided to the oil supply pipe 62 flows through the annular passage formed between the oil supply pipe 62 and the oil supply pipe 61 and the hole 6.
0 and the oil supply pipe 61 to the rear through an annular passage formed between the oil supply pipe 61 and an oil passage 65 similar to the oil passage 51 bored in the first main transmission shaft S1, and a third-speed oil pressure transmission. The oil is led to the 3-speed hydraulic transmission clutch 41 through an oil passage 66 provided in the boss portion of the clutch 41, and operates the clutch.

Further, an annular lubricating oil passage 67 is formed between the outer periphery of the oil supply pipe 62 and the inner periphery of the hole 59.
The oil inlet portion 58 also has an oil inlet 58C, through which oil discharged from the hydraulic pump 57 is introduced as lubricating oil. This lubricant is applied to the rear needle bearing 3.
4 to lubricate the bearing. Of course, it is also possible to guide the oil to other parts that require lubrication, such as the needle bearing 21, for example.

Further, the clutch shaft 20 is provided with a radial opening that allows the lubricating oil passage 67 to pass through the main clutch 17, and the oil supplied into the main clutch 17 through this opening causes the drive clutch plate 24 to pass through the lubricating oil passage 67. and driven clutch plate 2
6 is designed to be lubricated.

In this way, the hydraulic oil or lubricating oil is supplied to each clutch, bearing, etc. provided on the two shafts 20 and 31, which are arranged on the same axis and rotate differently from each other. This can be done by guiding the discharged oil 57 to the only oil inlet 58 provided at the front end of the clutch shaft 20. The oil stored in the used transmission case 4 flows through the oil filter 68 into the piston pipe 69, is sucked into the hydraulic pump 57, and is recirculated.

As described above, in the present invention, a plurality of shafts are arranged on the same axis, and a hydraulic clutch is installed on at least one shaft. An oil supply pipe is inserted into at least one of the shafts so as to be rotatable relative to the shaft center of the shaft in the axial direction, and the oil supply pipe is communicated with the hydraulic latch via an oil passage within the shaft. Therefore, the space required for oil inlets for a plurality of shafts can be consolidated at the end of one shaft, and the number of hydraulic piping from the hydraulic pump to the oil inlet can be reduced and simplified, making the entire device compact. Moreover, each axis can freely rotate relative to each other.

[Brief explanation of the drawing]

FIG. 1 is a side view of an agricultural tractor to which the present invention is applied, FIG. 2 is a sectional view showing a power transmission device of the same tractor, and FIG. 3 is a partially enlarged view of FIG. 2. 1... Rear wheel, 2... Front wheel, 3... Engine, 4...
...Mission case, 5...Reduction gear, 6...Propeller shaft, 7...Input shaft, 8...Vehicle frame, 9...Rear vehicle width, 10...Front wheel drive propeller shaft, 11... Hydraulic cylinder, 12... Lift arm, 13... Seat, 14... Handle, 15...
Clutch housing, 16... Sprocket, 17...
...Main clutch, 18...Sprocket, 19...
Ball bearing, 20...Clutch shaft, 21...Needle bearing, 22...Spring member, 23...Drive member, 24...
... Drive clutch plate, 25... Driven member, 26...
- Driven clutch plate, 27... Pressure plate, 28... Boss, 29... Rick plate, 30... Coil spring, 31... Ball bearing, 32... Operating part, 33...・・・
lever, 34... needle bearing, 35... ball bearing,
36...Bearing wall, 37.38...Ball bearing, 39...
・Hydraulic transmission, 40...2-speed hydraulic transmission Kuratsuji, 4
1: 3-speed hydraulic transmission clutch, 42: Low-speed hydraulic transmission clutch, 43: 4-speed and reverse hydraulic transmission clutch,
44...Cludge outer part, 45...Bracket is plate,
46...Clutch plate, 47...Cylinder part, 48.
... Operating member, 49... Spring, 50... Oil passage, 51... Oil passage, 52... Needle bearing, 53
...Clutch inner part, 54...Clutch plate,
55...Selector, 56...Sub-transmission device, 57.
...Hydraulic pump, 58...Oil inlet section, 59.60...
・Hole, 61° 62...Oil supply pipe, 63...Seal/bearing member, 64...Seal/bearing member, 65.66...
・Oil passage, 67... Lubricating oil passage, 68... Oil filter, 69... Naction vibe, Sl... 1st
Main transmission shaft, SP...Second main transmission shaft, S3...Sub-transmission shaft, S4...PTO axis, S5...Front wheel drive shaft, G.
...Gear, SP...Pump shaft.

Claims (1)

[Claims] In a hydraulic transmission device in which a plurality of shafts are coaxially arranged and a hydraulic clutch is provided on at least one shaft, at least a fuel supply pipe is inserted through the axial center portions of the mutually adjacent shafts in the axial direction. An oil supply structure for a hydraulic transmission, characterized in that the oil supply pipe is inserted into one shaft so as to be relatively rotatable, and the oil supply pipe is communicated with the hydraulic clutch via an oil passage in the shaft.