JP2001241534A - Power transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an improved power transmission having such a unique combination of a fluid coupling and a wet friction that is able to place the friction clutch in a specified or preset position indifferent of the accuracy of the position in which the power input shaft is installed within the casing of a speed change gear. SOLUTION: The power transmission has a hydraulic coupling actuated by an engine, a wet friction clutch equipped with a clutch outer which is arranged between said hydraulic coupling and speed change gears, and is also fitted to both the output shaft of the hydraulic coupling and the input shaft of the speed change gears by its one end, and a clutch center fitted to the output shaft and other end of the input shaft, and a coupling housing connected to the speed change gear casing that houses said hydraulic coupling and friction clutch. In this power transmission, a thrust shaft is arranged to be positioned in the space between the side of a hub of the clutch center or clutch outer that makes a spline joint with said input shaft and the side of said coupling housing or speed change gear casing facing with the opposite hub side.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a power transmission device, and more particularly, to a power transmission device having a fluid coupling operated by an engine, and a friction clutch disposed between the fluid coupling and a transmission. About.

[0002]

2. Description of the Related Art Fluid couplings have been conventionally used as power transmission couplings for ships, industrial machines, and automobiles. A vehicle power transmission device equipped with a fluid coupling is disclosed, for example, in Japanese Patent Application Laid-Open No. 55-159360. The vehicle power transmission device disclosed in the publication includes a fluid coupling operated by an engine mounted on the vehicle, a friction clutch operatively connected to the fluid coupling, and a transmission operatively connected to the friction clutch. They are arranged in series. A fluid coupling provided in such a vehicle power transmission device includes, for example, a casing connected to a crankshaft (an input shaft as a fluid coupling) of a diesel engine, and a casing provided to face the casing and attached to the casing. And a turbine mounted on an output shaft disposed opposite to the pump and arranged on the same axis as the input shaft, and contains a working fluid for torque transmission. The working fluid generates heat to swirl in a working chamber formed by the pump and the turbine. Therefore, the fluid coupling disclosed in the above publication cools the hydraulic oil by an air cooling system. In addition, a hydraulic fluid circulation type fluid coupling device that circulates the working fluid and radiates heat is also used. On the other hand, a dry single-plate clutch is generally used as a friction clutch disposed between the fluid coupling and the transmission, but a wet friction clutch may be used in consideration of wear of the clutch facing. . The fluid coupling and the wet friction clutch are disposed in the housing.

[0003]

In the power transmission device as described above, the wet friction clutch includes a clutch outer mounted on one of the output shaft of the fluid coupling and the input shaft of the transmission, and the output shaft and the input shaft. And a clutch center mounted on the other side. It is necessary to arrange such a wet friction clutch at a predetermined position. However, when the clutch center or the clutch outer mounted on the input shaft of the transmission is positioned between the input shaft and the clutch center, a mounting error of the input shaft mounted on the case of the transmission affects the arrangement of the wet friction clutch.

[0004] The present invention has been made in view of the above facts, and a main technical problem is to dispose a wet friction clutch at a predetermined position regardless of the mounting accuracy of an input shaft mounted on a transmission case. It is an object of the present invention to provide a power transmission device having a fluid coupling and a wet friction clutch that can be used.

[0005]

According to the present invention, in order to solve the above-mentioned main technical problems, a fluid coupling operated by an engine and a fluid disposed between the fluid coupling and a transmission are provided. A fluid friction clutch including an output shaft of a coupling, a clutch outer mounted on one of the input shafts of the transmission, a clutch center mounted on the output shaft and the other of the input shafts, and the fluid coupling; A fluid coupling accommodating chamber and a friction clutch accommodating chamber in which the wet friction clutch is disposed, and a coupling housing coupled to a case of the transmission;
A thrust bearing is disposed between opposing side surfaces of the clutch center or the clutch outer hub and the coupling housing or the case of the transmission, which are spline-fitted to the input shaft. A power transmission device is provided.

[0006]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A preferred embodiment of a power transmission device constructed according to the present invention will be described below in more detail with reference to the accompanying drawings.

FIG. 1 is a longitudinal sectional view of a power transmission device constructed according to the present invention. The power transmission device shown in FIG. 1 includes a diesel engine 2 as a prime mover, a fluid coupling (fluid coupling) 4, a wet multi-plate friction clutch 8 and a manual transmission 10, which are arranged in series. ing.

[0008] The power transmission device in the illustrated embodiment comprises:
A joint housing 3 for housing the fluid coupling 4 and the wet multi-plate friction clutch 8 is provided. Joint housing 3
Has a partition wall 31 at one end (left end in FIG. 1) on the engine side and a partition wall 31 on the other end (right end in FIG. 1) on the transmission side. In the illustrated embodiment, the joint housing 3 is integrally formed by aluminum die-casting, and an intermediate wall 32 is provided at a central portion in the axial direction.
And a friction clutch storage chamber 3b. The joint housing 3 thus configured is mounted on the engine 2 side (FIG. 1).
The left end (in FIG. 1) is attached to a housing 22 mounted on the diesel engine 2 by a fastening means such as a bolt 23, and the transmission side (the right end in FIG. 1) is attached to a case 100 of the manual transmission 10 with a bolt 24. Have been.

Next, the fluid coupling 4 will be described with reference to FIG. The fluid coupling 4 is provided in the fluid coupling accommodating chamber 3 a of the coupling housing 3. The fluid coupling 4 in the illustrated embodiment includes a casing 41, a pump 42, and a turbine 43. The casing 41 is provided for the crankshaft 21 of the diesel engine 2 (see FIG. 1).
The drive plate 44 has an inner peripheral portion attached to the outer periphery of the drive plate 44 by bolts 441 and nuts 442. A ring gear 45 for starting is engaged with the drive gear of a starter motor (not shown) on the outer periphery of the drive plate 44.

A pump 42 is provided to face the casing 41. The pump 42 includes a bowl-shaped pump shell 421 and a plurality of impellers 422 radially arranged in the pump shell 421. The pump shell 421 is fixed to the casing 41 by welding or the like. Installed. Accordingly, the pump shell 421 of the pump 42 is connected to the crankshaft 21 via the casing 41 and the drive plate 44. For this reason, the crankshaft 21 functions as an input shaft of the fluid coupling 4.

The turbine 43 is disposed in a chamber formed by the pump 42 and the casing 41 so as to face the pump 42. The turbine 43 includes a bowl-shaped turbine shell 431 disposed to face the pump shell 421 of the pump 42, and a plurality of runners 432 radially disposed in the turbine shell 431. . The turbine shell 431 is attached to a turbine hub 47 spline-fitted to an output shaft 46 disposed on the same axis as the crankshaft 21 as the input shaft by welding or other fixing means.

The fluid coupling 4 in the illustrated embodiment has a lock-up clutch 50 for directly transmitting and connecting the casing 41 and the turbine 43. The lock-up clutch 50 includes the casing 41 and the turbine 4
3 and an outer chamber 40 between the casing 41 and the outer chamber 40.
a and between the inner chamber 40 and the turbine 43.
The clutch disk 51 for forming b is provided. The clutch disc 51 has an inner peripheral edge that is the same as that of the turbine hub 4.
7 is supported so as to be relatively rotatable and slidable in the axial direction, and a clutch facing 52 is attached to a surface facing the casing 41 on an outer peripheral portion thereof.
Further, the inner chamber 4 in the outer peripheral portion of the clutch disk 51
On the 0b side, an annular concave portion 53 is formed, and a plurality of damper springs 55 supported by support pieces 54 are arranged at predetermined intervals in the concave portion 53. On both sides of the plurality of damper springs 55, an input-side retainer 56 attached to the clutch disk 51 is provided so as to protrude therefrom, and between the damper springs 55 is attached to a turbine shell 431 of the turbine 43. The output side retainer 57 is provided to protrude.

The lock-up clutch 50 in the illustrated embodiment is configured as described above, and its operation will be described. When the pressure of the working fluid in the inner chamber 40b is higher than the pressure of the working fluid in the outer chamber 40a, that is, the working fluid supplied by the fluid working means 6 described later is a working chamber 4a formed by the pump 42 and the turbine 43.
When the clutch disk 51 is pressed to the left in FIG. 1 when flowing from the inner chamber 40b to the outer chamber 40a through the inner chamber 40b, the clutch facing 52 mounted on the clutch disk 51 is pressed by the casing 41 and frictionally engaged. Yes (lock-up clutch connection). Therefore, the casing 41 and the turbine 43 are connected to the clutch facing 5
2. Directly drive-coupled via the clutch disk 51, the input side retainer 56, the damper spring 55, and the output side retainer 57. On the other hand, when the pressure of the working fluid in the outer chamber 40a is higher than the pressure of the working fluid in the inner chamber 40b,
That is, the working fluid supplied by the fluid working means 6, which will be described later, passes from the outer chamber 40a to the pump 42 through the inner chamber 40b.
When circulating in the working chamber 4 a formed by the clutch disk 51 and the turbine 43, the clutch disc 51 is pressed rightward in FIG. 1, so that the clutch facing 52 mounted on the clutch disc 51 is in friction with the casing 41. The clutch 41 is not engaged (the lock-up clutch is disconnected), so that the transmission connection between the casing 41 and the turbine 43 is released.

On the intermediate wall 32 of the joint housing 3,
Pump housings 61 and 62 are attached by fixing means such as bolts 63. This pump housing 6
A hydraulic pump 60 as a fluid pressure source of the fluid operating means 6 described later is provided in the insides 1 and 62. Each of the pump housings 61 and 62 is provided with a control valve that constitutes a fluid operating unit 6 described later, and has a working fluid passage. The pump hub 4 is mounted on the pump shell 421 of the pump 42 and rotatably supported by the pump housing 61 via a bearing 481.
8 is configured to be rotationally driven. The pump housings 61 and 62 include a hydraulic pump 60.
Is formed with a suction passage 66a communicating with the suction port.
The suction passage 66a communicates with a suction passage 32a provided in the intermediate wall 32 of the joint housing 3. The suction passage 32a is formed integrally with the joint housing 3, and a suction port 32b is opened toward the bottom wall of the friction clutch housing chamber 3b. A filter 67 is mounted on the suction port 32b.

In the illustrated embodiment, a working fluid is housed in a fluid reservoir 30b defined at the bottom of the friction clutch housing chamber 3b, and the working fluid is sucked through a filter 67 by the operation of the hydraulic pump 60. It is supposed to be. Therefore, the fluid storage section 30b of the friction clutch storage chamber 3b functions as a reserve tank that stores the working fluid. As described above, in the illustrated embodiment, the suction passage 32a is provided with the pump housings 61 and 62.
Is provided on the intermediate wall 32 of the joint housing 3 for mounting, so that there is no need to separately provide a suction mechanism for sucking the working fluid stored in the fluid storage portion 30b, and the number of parts can be reduced. Further, the joint of the components constituting the suction mechanism is located at the intermediate wall 32 of the joint housing 3.
And the pump housings 61 and 62 are only joined, so that the number of joints is small and the air suction performance is improved.

An oil seal 48 is provided between the outer peripheral surface of the pump hub 48 and the end of the pump housing 61.
2 are provided. A cylindrical member 64 is provided between the pump hub 48 and the output shaft 46, and the pump 42 and the turbine 43 of the fluid coupling 4 are provided between the cylindrical member 64 and the pump hub 48. A passage 641 communicating with the working chamber 4a is formed. The output shaft 46 is provided with a working fluid passage 461. One end of the passage 461 is open at the left end face in the drawing of the output shaft 46 and communicates with the outer chamber 40a, and the other end is open at the outer peripheral face of the output shaft 46.

Next, the wet multi-plate friction clutch 8 will be described with reference to FIG. Wet multi-plate friction clutch 8
Is disposed in the friction clutch housing chamber 3b of the joint housing 3 and includes a clutch outer 81 and a clutch center 82. The clutch outer 81 is formed in a drum shape, and a hub 811 that is spline-fitted to the output shaft 46 of the fluid coupling 4 is provided on an inner peripheral portion thereof. An inner spline 812 is provided on the inner surface of the outer peripheral portion of the clutch outer 81.
2, a plurality of friction plates 83 are fitted so as to be slidable in the axial direction. Further, an annular cylinder 813 is formed at an intermediate portion of the clutch outer 81, and the annular cylinder 813 is formed.
The inner peripheral wall 814 constituting the pump housing 6
The second boss portion 621 is fitted to the outer peripheral surface so as to be relatively rotatable. In the annular cylinder 813, a pressing piston 84 for pressing the friction plate 83 and a friction plate 87 described later is provided.
Are arranged. The hydraulic chamber 815 formed by the annular cylinder 813 and the pressing piston 84 is provided with a passage 816 provided on an inner peripheral wall 814 of the annular cylinder 813 and the boss 6 of the pump housing 62.
The fluid communication unit 6 communicates with a fluid operating unit 6 through a passage 622 provided in the fluid passage 21. A plate 85 is mounted between the hub 811 of the clutch outer 81 and the pressing piston 84.
And a compression coil spring 86 is disposed between them. Accordingly, the pressing piston 84 is constantly pressed to move leftward in FIG. 2 by the spring force of the compression coil spring 86.

The clutch center 82 is formed in a disk shape, and a hub 821 that is spline-fitted to the input shaft 101 of the transmission 10 is provided on an inner peripheral portion thereof. An external spline 822 is provided on the outer peripheral surface of the clutch center 82, and a plurality of friction plates 87 are fitted to the external spline 822 so as to be slidable in the axial direction. The plurality of friction plates 87 mounted on the clutch center 82 and the plurality of friction plates 83 mounted on the clutch outer 81 are arranged alternately. In the illustrated embodiment, a thrust bearing 880 is disposed between the hub 821 of the clutch center 82 and the opposing side surfaces of the partition wall 31 of the joint housing 3. In the illustrated embodiment, the thrust bearing 880 is connected to the partition wall 31.
Is fitted in the annular concave portion 31a provided in the first portion. Accordingly, the side of the hub 821 facing the partition wall 31 is brought into contact with the thrust bearing 880 fitted in the annular concave portion 31a provided in the partition wall 31, thereby forming the clutch center 82.
Can be positioned with respect to the joint housing 3. The hub 821 of the clutch center 82, the hub 811 of the clutch outer 81, and the output shaft 46 of the fluid coupling 4
A thrust bearing 881 is provided between the opposing side surfaces of the clutch outer 81 and the hub 811 of the clutch outer 81.
A thrust bearing 882 is also provided between the pump housing 62 and the boss 621 of the pump housing 62.

The wet multi-plate friction clutch 8 in the illustrated embodiment is constructed as described above, and a thrust bearing 880 is provided between the hub 821 of the clutch center 82 and the opposing side surfaces of the partition wall 31 of the joint housing 3. Since it is disposed, the side surface of the hub 821 is
, The clutch center 82 can be positioned with respect to the joint housing 3. For example,
Hub 8 that is spline-fit with input shaft 101 of transmission 10
If the input shaft 21 is configured to be positioned with respect to the input shaft 101, and the mounting position of the input shaft mounted on the casing or the joint housing 3 of the transmission shifts in the axial direction (left and right direction in FIG. 2), the hub 821, that is, the position of the clutch center 82 is shifted in the axial direction. If the position of the clutch center 82 is shifted to the transmission side (the right side in FIG. 2), when the clutch outer 81 and the pump housing 62 are assembled, play occurs between them. On the other hand, the position of the clutch center 82 is on the fluid coupling 4 side (the left side in FIG. 2).
When the clutch outer 81 and the pump housing 62 are assembled, the intermediate wall 3
A gap is created between the pump housing 2 and the pump housing 62. Thus, the hub 821 of the clutch center 82 is connected to the transmission 10
In the case where the positioning is performed with respect to the input shaft 101, the mounting error of the input shaft affects the arrangement of the wet friction clutch. However, in the illustrated embodiment, since the thrust bearing 880 is provided between the opposing side surfaces of the hub 821 of the clutch center 82 and the partition wall 31 of the joint housing 3, the clutch center 82 has the side surface of the hub 821. Since the clutch center 82 can be positioned with respect to the joint housing 3 by contacting the thrust bearing 880, the clutch center 82 is always located at a predetermined position with respect to the joint housing 3 even if the mounting position of the input shaft 101 is shifted in the axial direction. can do. As described above, since the clutch center 82 can always be arranged at a predetermined position with respect to the joint housing 3, the wet multi-plate friction clutch 8 can be assembled by assembling the clutch outer 81 and the pump housing 62 with the clutch center 82 as a reference. It can be assembled at a predetermined position.

In the illustrated embodiment, an example is shown in which the thrust bearing 880 is disposed between the hub 821 of the clutch center 82 and the partition wall 31 of the joint housing 3, but the partition wall 31 is not provided. In the case of the joint housing, a thrust bearing 880 is provided between an end wall of a case 100 of the manual transmission 10 described later and a hub 821 of the clutch center 82. In the illustrated embodiment, the thrust bearing 880 is provided between the hub 821 of the clutch center 82 and the partition wall 31 of the joint housing 3, but the clutch outer 81 is connected to the input shaft of the transmission 10. 101 and the clutch center 82 is connected to the fluid coupling 4
Of the wet friction clutch mounted on the output shaft 64 of the manual transmission 10, the hub 811 of the clutch outer 81 and the partition wall 31 of the joint housing 3 or the case 100 of the manual transmission 10.
A thrust bearing 880 is disposed between the thrust bearing 880 and the end wall.

The wet type multi-plate friction clutch 8 in the illustrated embodiment is constructed as described above. In the state shown in FIG. 1 in which the working fluid is not supplied to the hydraulic chamber 815 by the fluid working means 6 described later, the pressing is performed. The piston 84 is positioned at the left position (disengagement position) by the spring force of the compression coil spring 86. Therefore, the plurality of friction plates 83 and the plurality of friction plates 87 are not pressed, so that the plurality of friction plates 83 and the plurality of friction plates 87 do not frictionally engage with each other, and the output shaft 46 of the fluid coupling 4 Input shaft 1 of transmission 10
01 is interrupted. When the working fluid is supplied to the hydraulic chamber 815 by the fluid working means 6 described later, the pressing piston 84 is moved rightward in FIG. 1 against the spring force of the compression coil spring 86. As a result, the plurality of friction plates 83 and the plurality of friction plates 87 are pressed and frictionally engaged with each other.
Transmitted to the input shaft 101 of the transmission 10 via the clutch outer 81, the plurality of friction plates 83 and 87, and the clutch center 82.

The wet multi-plate friction clutch 8 in the illustrated embodiment comprises a plurality of friction plates 83 and a plurality of friction plates 8.
In order to cool the working fluid 7, the working fluid circulating through the fluid coupling 4 is supplied by fluid working means 6 described later. A passage 891 is formed between the outer peripheral surface of the output shaft 46 of the fluid coupling 4 and the boss 621 of the pump housing 62, and the passage 891 communicates with the fluid operating means 6 described later. The working fluid supplied to the passage 891 is supplied to the output shaft 46 and the hub 8 of the clutch outer 81.
11 is lubricated between the output shaft 46 and the hub 821 of the clutch center 82 to lubricate the thrust bearing 881, and then supplied to the plurality of friction plates 83 and the plurality of friction plates 87. You. The working fluid supplied to the passage 891 is supplied to the plurality of friction plates 83 and the plurality of friction plates 87 through the passage 817 provided with the clutch outer 81 after lubricating the thrust bearing 882. The output shaft 46 of the fluid coupling 4 is connected to the passage 8.
A passage 463 is provided for communicating between the transmission 91 and a supporting portion that supports the input shaft 101 of the transmission 10. Therefore, passage 8
The working fluid supplied to the lubrication unit 91 lubricates the bearing 108 that rotatably supports the input shaft 101 through the passage 891, and further, the input shaft 101 of the transmission 10 and the clutch center 8.
Lubricate the spline fitting portion with the second bub 821. The working fluid that has lubricated or cooled each part of the wet multi-plate friction clutch 8 is discharged to the friction clutch storage chamber 3b,
It is stored in the fluid storage part 30b functioning as a reserve tank.

Next, the fluid operating means 6 will be described with reference to FIG. The fluid actuating means 6 includes the hydraulic pump 6
0 operates, the working fluid stored in the fluid storage unit 30b functioning as a reserve tank is filtered by the filter 6.
7. The suction passage 32a is sucked through the passage 32a and circulated as described later. The working fluid sucked by the hydraulic pump 60 is discharged to the passage 66b.
The working fluid discharged to the passage 66b is connected to the passage 66 provided on the output shaft 46 via the passage 66c and the lock-up clutch direction control valve 68.
d or a passage 66e communicating with a passage 641 communicating with the working chamber 4a of the fluid coupling 4. In order to apply pilot pressure to the lock-up clutch directional control valve 68, a pilot passage 66f is provided for connecting the passage 66b with the lock-up clutch directional control valve 68. The pilot passage 66f is provided with a lock-up clutch. An electromagnetic switching valve 69 is provided. The lock-up clutch electromagnetic switching valve 69 is energized (ON) by control means (not shown) when the running speed of the vehicle becomes equal to or higher than a predetermined value based on the running speed of the vehicle.

When the lock-up clutch electromagnetic switching valve 69 is deenergized (OFF) as shown in FIG. 2, the pilot passage 66f is closed, and the pilot pressure is applied to the lock-up clutch directional control valve 68. Does not work. Accordingly, the lock-up clutch directional control valve 68 is positioned as shown in FIG. 2, and the passage 66c communicates with the passage 66d, and the passage 66e communicates with the return passage 6.
6g are in communication. As a result, the working fluid discharged into the passage 66b by the hydraulic pump 60 becomes the working chamber formed by the passage 66c, the passage 66d, the passage 461, the outer chamber 40a, the inner chamber 40b of the fluid coupling 4, the pump 42 and the turbine 43. 4a, a passage 641, a passage 66e, a return passage 66g, a check valve 70 and a cooler 71 disposed in the return passage 66g, and circulated to the fluid storage portion 30b.
When the working fluid circulates in this manner, the fluid pressure of the outer chamber 40a is higher than the fluid pressure of the inner chamber 40b, so that the lock-up clutch 50 does not frictionally engage as described above (lock-up clutch is disconnected).

On the other hand, when the lock-up clutch electromagnetic switching valve 69 is energized (ON), the pilot passage 66f is communicated, and pilot pressure acts on the lock-up clutch direction control valve 68 to cause the lock-up clutch direction to change. When the control valve 68 is operated, the passage 66c communicates with the passage 66e, and the passage 66d communicates with the fluid reservoir 65. As a result, the working fluid discharged into the passage 66b by the hydraulic pump 60 is supplied to the working chamber 4a, the inner chamber 40b, the outer chamber 40a, and the passage 46 formed by the passage 66c, the passage 66e, the passage 641, the pump 42 and the turbine 43.
1. Circulated to the fluid reservoir 65 through the passage 66d.
When the working fluid circulates in this manner, since the fluid pressure in the inner chamber 40b is higher than the fluid pressure in the outer chamber 40a, the lock-up clutch 50 is frictionally engaged as described above (lock-up clutch contact). The lock-up clutch electromagnetic switching valve 69 is activated when the working fluid pressure in the passage 66b is lower than a predetermined value and the pilot pressure acting on the lock-up clutch directional control valve 68 is low in the energized (ON) state. , The spool 682 of the lock-up clutch directional control valve 68 is located at the intermediate position,
c is configured to communicate with the passage 66d and the passage 66e. In connection with this operation mode, a bypass passage 66h communicating the passage 66e and the return passage 66g is provided, and a throttle 72 is provided in the bypass passage 66h. Therefore, when the rotation speed of the hydraulic pump 60 is low and the working fluid pressure in the passage 66b is lower than a predetermined value, the working fluid discharged into the passage 66b is supplied to the passage 66c and the passage 6c.
6e, circulated through a bypass passage 66h provided with a throttle 72.

The fluid operating means 6 in the illustrated embodiment
Is a relief passage 6 connecting the passage 66a and the passage 66b.
6j, and a relief valve 73 is disposed in the relief passage 66j. When the lock-up clutch 50 is ON, the relief valve 73 is a fluid pressure required for the clutch facing 52 mounted on the clutch disc 51 to be pressed by the casing 41 and frictionally engaged, for example, 6 kg /. cm2, and when the working fluid pressure in the passage 66b exceeds 6 kg / cm2, the working fluid is passed through the relief passage 66j to the passage 66a.
Return to

The fluid operating means 6 in the illustrated embodiment
Is provided with a passage 66k and a passage 66m for connecting the passages 861 and 622 connected to the hydraulic chamber 815 of the wet type multi-plate friction clutch 8 with the passage 66b. A friction clutch direction control valve 74 is disposed between the passage 66k and the passage 66m. Direction control valve 74 for friction clutch
In order to apply pilot pressure to the
A pilot passage 66n is provided for communicating with the friction clutch directional control valve 74.
An electromagnetic switching valve 75 for a friction clutch is provided at n.
When the solenoid-operated switching valve 75 for the friction clutch is de-energized (OFF), the pilot passage 66n as shown in FIG.
And is configured to shut off the communication of the pilot passage 66n when being energized (ON). In addition,
The direction control valve 74 for the friction clutch blocks the communication between the passage 66k and the passage 66m in a state where the pilot pressure is not applied.
And the passage 66m. Accordingly, when the frictional clutch electromagnetic switching valve 75 is deenergized (OFF), the pilot pressure acts on the friction clutch directional control valve 74, so that the friction clutch directional control valve 74 is connected to the passage 66k and the passage 66m. And communicate with. As a result, the working fluid discharged into the passage 66b by the hydraulic pump 60 is passed through the passage 66k, the passage 66m, the passage 622, and the passage 816 to the hydraulic chamber 815 of the wet multi-plate friction clutch 8.
As described above, the pressing piston 84 is moved rightward in FIG. 1 against the spring force of the compression coil spring 86 as described above, and the plurality of friction plates 83 and the plurality of friction plates 87 are moved. They are pressed and frictionally engage each other. On the other hand, when the electromagnetic switching valve 75 for friction clutch is biased (ON), the communication of the pilot passage 66n is cut off, and the pilot pressure does not act on the directional control valve 74 for friction clutch.
Communication with the passage 66m is interrupted, and
m is opened to the fluid reservoir 30b. As a result, the pressing piston 84 of the wet multi-plate friction clutch 8 is moved leftward in FIG. 1 by the spring force of the compression coil spring 86, so that the frictional engagement between the plurality of friction plates 83 and the plurality of friction plates 87 is performed. Is released.

Control of energizing (ON) and deenergizing (OFF) of the electromagnetic switching valve 75 for the friction clutch is performed by control means (not shown) at the time of shifting of the manual transmission 10.
That is, the wet multi-plate friction clutch 8 in the illustrated embodiment
Constitutes an automatic clutch system, and the control means (not shown) is based on a signal by turning on a shift instruction switch attached to a shift lever (not shown) when the driver performs a shift operation of the manual transmission 10. The friction clutch electromagnetic switching valve 75 is energized (ON) to shut off the power transmission by the wet multi-plate friction clutch 8. Then, the control means (not shown) deactivates (OFF) the electromagnetic switching valve 75 for the friction clutch based on a shift end signal from a shift stroke sensor (not shown) when the shift operation of the transmission is completed.
Then, the wet multi-plate friction clutch 8 is rubbed and engaged.

The fluid operating means 6 in the illustrated embodiment
Is provided with a passage 66p that connects the passage 66b with a passage 891 formed between the outer peripheral surface of the output shaft 46 of the fluid coupling 4 and the boss 621 of the pump housing 62. Therefore, the passage 66b is
The working fluid discharged to the passage 89 passes through the passage 89p through the passage 89p.
1 is always supplied. Therefore, when the hydraulic pump 60 is operated, the working fluid supplied to the passage 891 lubricates the spline fitting portion and the bearings as described above, and the plurality of friction plates 83 and the plurality of It is supplied to the friction plates 87. As described above, the fluid operating means 6 for circulating the working fluid through the fluid coupling 4 includes:
The working fluid lubricates the bearings of the wet multi-plate friction clutch 8 and supplies the cooling fluid to the plurality of friction plates 83 and the plurality of friction plates 87 as a coolant. Accordingly, it is not necessary to separately provide a cooling liquid supply device for cooling the friction plate of the wet multi-plate friction clutch 8, and the working fluid of the fluid coupling 4 supplied to the friction plate has good friction characteristics because of good friction characteristics. Friction clutch characteristics can be maintained.

Next, the manual transmission 10 will be described with reference to FIG. Manual transmission 10 in the illustrated embodiment
Is composed of a parallel shaft type gear transmission, and includes a case 100 and the wet multi-plate friction clutch 8 provided in the case 100.
, An output shaft 102 provided on the same axis as the input shaft 101, and a counter shaft 1 provided in parallel with the output shaft 102.
03. The drive gear 10 is provided on the input shaft 101.
4 are provided, and the output shaft 102 has transmission gears 105a, 1
Are provided, and the synchromesh devices 106a, 106b,... Are provided. The countershaft 103 has the driving gear 10
4 and counter gears 107a, 107b, 107c constantly meshing with the transmission gears 105a, 105b,.
Are provided. The input shaft 101 is
The hole 3 provided in the partition wall 31 of the joint housing 3
11, one end of which is connected to the fluid coupling 4
Is rotatably supported by the output shaft 46 via a bearing 108, and an intermediate portion thereof is rotatably supported by the joint housing 3 via a bearing 109. An oil seal 110 is provided between the input shaft 101 and an inner peripheral surface of a hole 311 provided in the partition wall 31 of the joint housing 3. The oil seal 110 allows the joint housing 3
Of the clutch coolant in the friction clutch housing chamber 3b into the case 100 of the manual transmission 10 and the lubricating oil in the case 100 of the manual transmission 10 from entering the friction clutch housing chamber 3b. Is done.

The power transmission device for a vehicle in the illustrated embodiment is configured as described above, and its operation will be described below. First, the starting operation of the vehicle will be described.
When the diesel engine 2 is started and idling, the electromagnetic switching valve 73 for the friction clutch is deenergized (OFF).
The wet multi-plate friction clutch 8 is frictionally engaged as described above. The lock-up clutch electromagnetic switching valve 69 is deenergized (OFF), and the lock-up clutch 50 of the fluid coupling 4 does not frictionally engage (lock-up clutch is disconnected) as described above. Therefore, the engine 2 is kept idling by the slip of the fluid coupling 4. When the driver turns on a shift instruction switch mounted on a shift lever (not shown) to start the vehicle, the electromagnetic switching valve 73 for the friction clutch is energized (ON) as described above, and the wet multi-plate friction clutch 8 Power transmission is shut off. While the power transmission by the wet-type multi-plate friction clutch 8 is interrupted, a shift operation is performed by the shift lever, and when the manual transmission 10 is turned on to the starting stage, the electromagnetic switching valve 73 for the friction clutch is activated as described above. Discharge (OF
F), and the wet multi-plate friction clutch 8 is frictionally engaged. When an accelerator pedal (not shown) is depressed in this state to increase the engine rotation speed, the driving force generated on the crankshaft 21 (input shaft) of the diesel engine 2 is transmitted to the casing 41 of the fluid coupling 4 via the drive plate 44 as described above. Is transmitted to Since the casing 41 and the pump shell 421 of the pump 42 are integrally formed, the pump 42 is rotated by the driving force. When the pump 42 rotates, the working fluid in the pump 42 flows toward the outer periphery along the impeller 422 due to centrifugal force, and flows into the turbine 43 as indicated by an arrow. The working fluid flowing into the turbine 43 flows toward the center side and is returned to the pump 42 as indicated by an arrow. Thus, the pump 4
When the working fluid in the working chamber 4a formed by the turbine 2 and the turbine 43 circulates in the pump 42 and the turbine 43, the driving torque of the pump 42 is transmitted to the turbine 43 via the working fluid. The driving force transmitted to the turbine 43 is transmitted to the output shaft 46 via the turbine shell 431 and the turbine hub 47, and further transmitted to the transmission 10 via the wet multi-plate friction clutch 8 to start the vehicle. be able to.

Next, the operation of the power transmission device for a vehicle at the time of shifting will be described. When shifting the manual transmission 10 to a predetermined gear while the vehicle is traveling, when the driver turns on a shift instruction switch mounted on a shift lever (not shown), the electromagnetic switching valve 73 for the friction clutch is activated as described above. Energizing (O
N), the power transmission by the wet multi-plate friction clutch 8 is cut off. While the power transmission by the wet-type multi-plate friction clutch 8 is interrupted, a shift operation by the shift lever is performed,
The manual transmission 10 is shifted to a predetermined gear. At this time, the rotation speed of the output shaft 102 and the rotation speed of the predetermined transmission gear 105 are synchronized by the synchromesh 106,
This synchronizing action requires a long time when the rotational inertia of the components of the friction clutch, which is operatively connected to the transmission gear 105, is large (the synchronous load is large). Can be synchronized. However, in the illustrated embodiment, since the clutch center 82 having small rotational inertia (small synchronous load) is mounted on the input shaft 101 that is operatively connected to the transmission gear 105, the synchronizing operation can be performed in a short time. The shift time can be shortened.

As described above, when the rotation speed of the output shaft 102 and the rotation speed of the predetermined transmission gear 105 are synchronized and the shift to the predetermined gear is completed, the electromagnetic switching valve 73 for the friction clutch is activated as described above. The power is released (OFF), and the wet multi-plate friction clutch 8 is rubbed and engaged.

[0034]

Since the power transmission device according to the present invention is constructed as described above, the following effects can be obtained.

That is, according to the present invention, in a power transmission device in which a wet friction clutch is disposed between a fluid coupling and a transmission, a clutch center or clutch of a wet friction clutch that is spline-fitted to an input shaft of the transmission. The thrust bearings are arranged between the opposing side surfaces of the outer hub and the coupling housing or the case of the transmission, so that the clutch center or clutch outer can be connected to the coupling housing or the transmission by contacting the side surfaces of the hub with the thrust bearings. It can be positioned with respect to the machine case. Therefore, a power transmission device having a fluid coupling and a wet friction clutch capable of disposing the wet friction clutch at a predetermined position regardless of the mounting accuracy of the input shaft mounted on the transmission case is obtained.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a power transmission device configured according to the present invention.

FIG. 2 is an enlarged sectional view of a main part of the power transmission device shown in FIG.

FIG. 3 is a fluid circuit diagram of fluid operating means provided in the power transmission device of FIG. 1;

[Explanation of symbols]

2: Internal combustion engine 21: Crankshaft 3: Joint housing 3a: Fluid coupling accommodating chamber 3b: Friction clutch accommodating chamber 30b: Fluid reservoir 4: Fluid coupling 40: Fluid coupling housing 41: Casing 42: Pump 421: Pump shell 422: Impeller 43: Turbine 431: Turbine shell 432: Runner 44: Drive plate 45: Ring gear 46: Output shaft of fluid coupling 47: Turbine hub 48: Pump hub 50: Cuck-up clutch 51: Clutch disk 55: Damper spring 56: Input side retainer 57: Output side retainer 6: Fluid actuating means 60: Hydraulic pump 61, 62: Pump housing 67: Filter 68: Directional control valve for lockup clutch 69: Solenoid switching valve for lockup clutch 70: Check valve 71: Cooler 72: Aperture 7 3: Relief valve 74: Direction control valve for friction clutch 75: Solenoid switching valve for friction clutch 8: Wet multi-plate friction clutch 81: Clutch outer 82: Clutch center 83: Friction plate 84: Pressing piston 86: Compression coil spring 87: Friction Plate 880: Thrust bearing 881: Thrust bearing 882: Thrust bearing 10: Transmission 100: Transmission case 101: Transmission input shaft 102: Transmission output shaft 103: Transmission counter shaft 104: Driving gear 105a, 105b,...: Transmission gear 107a, 107b, 107c,.

Claims (1)

[Claims] A fluid coupling operated by an engine, a clutch outer disposed between the fluid coupling and the transmission, and mounted on one of an output shaft of the fluid coupling and an input shaft of the transmission; A wet friction clutch having an output shaft and a clutch center mounted on the other of the input shaft, a fluid coupling accommodating chamber in which the fluid coupling is disposed, and a friction clutch accommodating chamber in which the wet friction clutch is disposed; And a coupling housing connected to a case of the transmission, wherein the clutch center or the hub of the clutch outer, which is spline-fitted to the input shaft, and the coupling housing or the transmission case. A thrust bearing is arranged between the mutually opposing side surfaces of the power transmission device.