JPH0155689B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a multi-disc friction clutch used in motorcycles, etc., which has a function of reducing the torque transmitted from the rear wheels to the engine during deceleration. This invention relates to a multi-disc friction clutch.

Prior Art The most common power transmission mechanism for motorcycles is one that transmits engine output to the rear wheels via a crankshaft, primary reduction gear, clutch, transmission, and secondary reduction gear. As described above, the reason why the primary reduction gear is provided to increase the reduction ratio is whether the motorcycle engine has high-speed rotation type output characteristics.

Problem to be Solved However, if the reduction ratio is increased, a large engine braking force can be obtained during deceleration driving or until the car stops, but conversely, the torque due to the rotational inertia of the rear wheels is transferred to the engine side. is transmitted to
The engine becomes over-revved. Therefore, the mail order is
In order to alleviate the unnecessarily large engine braking force,
Alternatively, in order to prevent engine overspeed and improve engine durability, an intermediate shaft is provided between the crankshaft and the clutch, and a one-way clutch for slipping is attached to the intermediate shaft. Some of the transmitted torque is released.

However, when an intermediate shaft is provided to limit the transmission torque, the engine becomes larger and the weight of the vehicle increases.

Means for Solving the Problems and Effects The present invention relates to an improvement of a multi-disc friction clutch that overcomes the above-mentioned difficulties, by alternately polymerizing a plurality of clutch discs and clutch plates, and forming the clutch disc into a clutch outer. In the multi-plate friction clutch, the clutch plate is engaged with the axial groove of the clutch center which engages with the axial groove of the clutch center and which meshes with the main shaft. One of the clutch centers located on the main shaft is fitted to the main shaft via a one-way clutch, and the one-way clutch transmits power to the engine output side, and a spring retaining member is arranged adjacent to the outside of the one-way clutch. A disc spring is engaged with the spring holding member and a pressure plate that is fitted onto the main shaft and is located outwardly from the one clutch center, and the washer that is externally fitted on the spring holding member is held in the one direction. Abut against the side of the inner member of the clutch,
A space defined by a plurality of through holes provided in the spring holding member, a plurality of concave grooves provided on the side surface of the inner member, and the washer serves as a lubricating oil supply path, and the lubricating oil is discharged from the end of the main shaft. The lubricating oil is configured to be guided to the one-way clutch along the lubricating oil supply path.

In the present invention, the clutch center is divided into two parts, and the clutch center located on the outside is fitted to the main shaft via a one-way clutch, and the spring holding member and pressure plate fitted to the end of the main shaft shaft are connected to each other. A through hole is formed in the spring holding member, and a plurality of grooves are formed in the side surface of the inner member of the one-way clutch, so that the lubricating oil discharged from the end of the main shaft shaft is passed through the hole. The structure is such that it is guided to the one-way clutch through the hole and groove, so by incorporating the one-way clutch into the multi-plate friction clutch, it is possible to prevent the engine from over-speeding during deceleration. The intermediate shaft on which the clutch was disposed can be omitted, contributing to the reduction in size and weight of the engine.

In addition, a through hole is formed in the spring holding member,
By forming a concave groove on the side surface of the inner member of the one-way clutch, lubricating oil discharged from the end of the main shaft shaft is guided to the one-way clutch, thereby effectively lubricating the one-way clutch. It will be held on. Furthermore, by providing the through hole and groove, a lubricating oil discharge port for the one-way clutch is provided in the main shaft, and an opening is provided that penetrates in the radial direction from within the inner member shaft hole of the one-way clutch. There is no need to take such measures, the processing is simple, and the manufacturing cost is low.

Furthermore, by using a disc spring, compared to the case of using a conventional compression coil spring,
The axial dimension of the multi-disc friction clutch has been reduced, and the internal space has been increased, making it possible to install a one-way clutch.

Embodiment Hereinafter, an embodiment of the present invention illustrated in FIGS. 1 to 28 will be described.

The multi-plate friction clutch 1 is connected to the main shaft of the transmission (hereinafter referred to as
(referred to as a main shaft 40). Driven gear 2 of multi-plate friction clutch 1
is rotatably supported on the main shaft 40 and is engaged with the drive gear 31 of the crankshaft 30. Then, the clutch outer 3 is integrally connected to the driven gear 2,
A plurality of clutch disks 4 are arranged so as to engage with the axial grooves of the clutch outer 3. The clutch disk 4 is arranged so as to overlap alternately with a plurality of clutch plates 7 which are engaged with the outer peripheral grooves of the clutch centers 5 and 6 (see FIGS. 1 and 2).

On the other hand, unlike the normal type, the clutch center is divided into two clutch centers 5 and 6, and the clutch center 5 located inward, that is, on the driven gear 2 side, is directly connected to the main shaft 40 by a spline. A one-way clutch 20 (described later) that transmits driving torque to the main shaft 40 is fitted onto the clutch center 6 located adjacent to the outside, and an inner member 25 of this one-way clutch 20 is connected to the main shaft 40.
A spline is fitted to the

Then, adjacent to the outside of the one-way clutch 20, the spring holding member 8 on which the washers 10a and 11 are fitted is fitted onto the main shaft 40, and the outer position, that is, the main shaft 40
A lock nut 9 is screwed onto the shaft end of the shaft. The washer 10a is in contact with the outer surface of the inner member 25 of the one-way clutch 20, and at the same time, the outer peripheral edge is in contact with the inner peripheral surface of the clutch center 6, and the washer 11 is in contact with the outer surface of the clutch center 6. are in contact with each other. In summary, the assembly of the driven gear 2, the clutch centers 5, 6, and the one-way clutch 20 are connected to the main shaft 20 with the lock nut 9 via the spring holding member 8 and washers 10a, 11.
It is attached to.

Further, a cap 42 is fitted onto the end of a lifter rod 41 which is disposed so as to be displaceable in the axial direction, passing through the inside of the hollow main shaft 40.
The shaft cylinder portion 42b of the cap 42 is connected to the main shaft 4.
It is embedded in 0. A lifter plate 13 is pivotally supported on the head 42a of the cap 42 via a bearing 43, and a pressure plate 14 is integrally fitted around the outer periphery of the lifter plate 13.

Furthermore, the spring holding member 8 includes a disc spring 1.
2 is fitted onto the outside, and the outer periphery of the disc spring 12 is connected to the space between the jaw 14a of the pressure plate 14 and the lifter plate 13. The disc spring 12 biases the pressure plate 14 due to the locking relationship between the jaw 8a of the spring holding member 8 and the jaw 14a of the pressure plate 14,
A predetermined pressing force is applied to a plurality of clutch disks 4 and clutch plates 7.

Next, the one-way clutch 20 will be explained.

The one-way clutch 20 includes a pair of ring-shaped frame members 21, a zigzag-shaped wire frame 22 that holds the members 21 facing each other at a predetermined interval, and is supported by the ring-shaped frame members 21 and the wire frame 22, and is supported by the ring-shaped frame members 21 and the wire frame 22. A large number of roller-shaped connecting pieces 24 are arranged along the circumferential direction of the shaped frame member 21, and a ring-shaped tension member that holds the connecting pieces 24 from the outside and presses them against the wire frame 22 with a relatively small pressure. coil spring 23
and an inner member 25 into which an assembly consisting of the members 21, 22, 23, and 24 is fitted (see Figs. 2 to 4). The roller-shaped connecting piece 24 has an eccentric cross section, an inner surface 24a in contact with the wire frame 22 is cylindrical, and an outer surface has a protruding surface 24 that is connected to the clutch center 6 under high pressure.
It forms a special curved surface having a flat surface 24c and a groove 24d having a predetermined depth from the outer surface. The roller-shaped connecting piece 24 is held by the engagement relationship between the groove 24d and the tension coil spring 23 (see FIGS. 3 to 6).

A clutch center 6 is fitted onto the outer periphery of the one-way clutch 20, and when the clutch center 6 rotates in the direction of the arrow in FIGS. 3 and 7, the rotational speed of the clutch center 6 matches the main shaft 40. If the rotational speed of the inner member 25 side is higher than the rotational speed of the inner member 25 side, the protruding surface 24b of the roller-shaped connecting piece 24 is connected to the inner circumferential surface of the clutch center 6 with strong pressure, and conversely, if the rotational speed of the inner member 25 side is higher The roller-shaped connecting piece 24 is rotated slightly so that the flat surface 24c faces the inner surface of the clutch center 6, and the connection between the clutch center 6 and the one-way clutch 20 is broken.

The main constituent members of the multi-plate friction clutch 1 will be explained below.

Figures 8 to 15 show clutch center 5.
shows the structure of Boss part 5a of clutch center 5
A plurality of grooves 5b for oil passages oriented in the radial direction are formed on one side. Further, a pair of oil passage through holes 5d are formed penetrating to the ground side at positions sandwiching a plurality of radial ribs 5c provided on the same side. Then, the two clutch plates 7 on the inner side in the axial direction of the main shaft
The ring-shaped engagement piece 5e, in which a large number of grooves 5f are formed, is formed with through-holes 5g and 5h for oil passages passing through the bottom of the groove. They are provided at positions corresponding to the pair of through holes 5d, with an interval of 120° in the circumferential direction. The clutch center 5 is formed with an outer peripheral flange portion 5i which presses the clutch disk 4 and the clutch plate 7 against each other by receiving a pressing force from the pressure plate 14.

Further, the structure of the inner member 25 of the one-way clutch 20 is shown in FIGS. 16 to 18. One side of the inner member 25, that is, the washer 1
Four grooves 25a for oil passages oriented in the radial direction are formed between the grooves 25a and 0a.

The structure of the clutch center 6 is shown in FIGS. 19 to 21. On one side of the clutch center 6, that is, the surface that contacts the washer 10b, four grooves 6a for oil passages oriented in the radial direction are formed. The ring-shaped engagement piece 6b, which is formed with a large number of grooves 6c that engage with the three clutch plates 7 on the outside in the axial direction of the main shaft, has an oil passage through-hole 6d that passes through the bottom of the groove. 6e and 6f are formed at 120° intervals in the circumferential direction.

22 and 23 show the structure of the spring holding member 8. As shown in FIG. An oil passage through hole 8b is formed in the ring-shaped peripheral wall of the spring holding member 8 in the circumferential direction.
They are formed at 120° intervals.

24 and 25 show the structure of the pressure plate 14. Pressure plate 14
A large number of teeth 14c that loosely engage with a large number of grooves 6c in the clutch center 6 are formed on the inner periphery of the outer peripheral edge pressing wall 14b. Furthermore, an oil passage through hole 14d that penetrates from the inner peripheral surface to the outer piece is provided at the position of the jaw 14a that engages with the outer peripheral edge of the disc spring 12.

26 to 28 show the lifter plate 13 fitted inside the pressure plate 144.
It shows a plurality of reinforcing ribs 1 on one side.
3b is formed, and a bearing 43 is fitted onto the boss portion 13a.

Next, the operation of the multi-plate friction clutch 1 will be explained. The clutch 1 is connected and disconnected by a lifter rod 41. That is, when the lifter rod 41 is displaced by a pressing operation at one end (the left end in FIG. 1) of the lifter rod 41, the lifter plate 13 and the plate integrally connected thereto are moved through the cap 42 and the bearing 43. The shear plate 14 moves outward against the elastic force of the disc spring 12, and is held under strong pressure between the pressing wall 14b of the pressure plate 14 and the outer peripheral flange 5i of the clutch center 5. clutch disk 4 and clutch plate 7
is depressurized and the crack is cut off. When the lifter rod 41 is displaced in the opposite direction, the pressure plate 14 moves inward due to the elastic restoring force of the disc spring 12, and the clutch center 5
, the plurality of clutch disks 4 and clutch plates 7 are strongly pressed, resulting in a clutch state.

Therefore, when the engine is running, the rotation of the crankshaft 30 is transmitted from the drive gear 31 to the driven gear 2 of the multi-disc friction clutch 1, and the clutch outer 3 is integrally connected to the driven gear 2.
rotates. When the multi-plate friction clutch 1 is in the connected state, power is transmitted to the clutch plate 7 that is frictionally engaged with the clutch disk 4 that engages with a plurality of grooves in the clutch outer 3, and the clutch centers 5, 6 and the clutch plate 7 are engaged with each other. The shear plate 14 and lifter plate 13 rotate integrally. In this state,
The roller-shaped connecting piece 24 of the one-way clutch 20 is strongly pressed between the clutch center 6 and the inner member 25, and the one-way clutch 20 is in the connected state (see FIGS. 3 and 7). The rotational force is transmitted together with the rotational force of the clutch center 5 to the main shaft 40 side, and the rear wheels are driven and rotated via a large number of gear trains, drive chains, etc. in the transmission. During this time, lubricating oil is being discharged from the oil discharge port 50 in the transmission, and this oil is supplied into the main shaft 40 and is discharged to the gears on the main shaft through the plurality of holes 40a. It is also supplied to the multi-plate friction clutch 1. The first oil supply path to the multi-plate friction clutch 1 passes through the bearing part of the driven gear 2 from the opening 40a, through the concave groove 5b of the clutch center 5, through-hole 5d, 5g or 5h, and then to the clutch plate 7. This is the path through which the clutch disk 4 is supplied (see FIG. 2). The second oil supply path includes a through hole 42c of the cap 42 fitted into the shaft end of the main shaft 40, a through hole 8b of the spring holding member 8, and a groove 25 of the inner member 25.
is supplied to the one-way clutch 20 through a passage defined by the groove 6a of the clutch center 6 and the side surface of the washer 10b, and through the through holes 5g and 5h. This is the path through which the clutch plate 7 and clutch disk 4 are supplied. The third oil supply path includes a through hole 42c of the cap 42, a space area defined by the disc spring 12 and the lifter plate 13, a through hole 14d of the pressure plate 14, through holes 6d, 6e of the clutch center 6, After 6f,
This is the path through which the clutch plate 7 and clutch disk 4 are supplied. In this way, lubricating oil is guided through the grooves and through holes formed in each component of the multi-plate friction clutch 1, and the interior of the clutch 1 is effectively lubricated. In particular, Watusha 10
The one-way clutch 20 is assembled by using the spring holding member 8 which holds the one-way clutch 20 and the clutch center 6 via the springs 11 and 11, and the pressure plate 14 via the disk spring 12, and the washer 10a. Since lubricating oil is supplied to the one-way clutch 20, the one-way clutch 20 can also be sufficiently lubricated.

Next, the state during deceleration traveling or until the vehicle stops will be explained. During deceleration driving, so-called engine braking is applied, and due to the rotational inertia of the rear wheels, the rotational speed on the main shaft 40 side decreases.
Since it is larger than the clutch outer 3 side, the clutch center 6 side rotates relative to the one-way clutch 20 in the direction opposite to the arrow in FIGS. 3 and 7, and the roller-shaped connecting piece 24 rotates slightly. The flat surface 24c faces the inner circumferential surface of the clutch center 6, and the one-way clutch 20 is in a disconnected state, so that no rear wheel torque is transmitted to the clutch center 6. Therefore, the torque on the rear wheel side is applied to the clutch via the clutch center 5, the two clutch plates 7 that engage with the clutch center 5, and the three clutch discs 4 that frictionally engage with the clutch plates 7. Although the torque is transmitted to the outer 3 side, slipping occurs because the number of engaged clutch plates 7 and clutch discs 4 that contribute to torque transmission is small. In short, the torque from the rear wheel that exceeds the frictional force obtained by the frictional engagement is released in the multi-disc friction clutch 1. As a result, the engine braking force does not become larger than necessary, and overspeeding of the engine is effectively prevented.

Characteristic points of this embodiment will be described below.

(1) A through hole 8b is provided in the spring holding member 8 that holds the spring 12, and a groove 25a is provided in the side surface of the inner member 25 of the one-way clutch 20.
Furthermore, by providing a groove 6a on the side surface of the clutch center 6, the lubricating oil discharged from the shaft end of the main shaft 40 is guided along the path to the one-way clutch 20, and is discharged from the one-way clutch 20. The lubricating oil can be guided to the clutch plate 7 and clutch disc 4 side, and the one-way clutch 20 can be
can be effectively lubricated.

(2) A one-way clutch 2 is included in the multi-plate friction clutch 1.
0 built-in, it becomes possible to omit the intermediate shaft that was conventionally provided between the crankshaft and the multi-plate friction clutch, which can contribute to making the engine smaller and lighter.

(3) By using the bellows spring 12, the axial dimension of the multi-plate friction clutch 1 is reduced compared to the case where a conventional compression coil spring is used, and the internal space is increased, making it possible to reduce the unidirectional clutch. It became possible to install 20. In addition, in the past, multiple compression coil springs were used and each was fixed with bolts, which resulted in a large number of parts and increased weight. Since the screws 12 are simply disposed using a simple attachment mechanism, the number of parts is small and the device is lightweight.

[Brief explanation of drawings]

FIG. 1 is a cross-sectional view of a main part of a power unit for a motorcycle equipped with a multi-disc friction clutch according to an embodiment of the present invention, FIG. 2 is an enlarged explanatory view of the multi-disc friction clutch, and FIG. 3 is the same. A partially cutaway explanatory diagram of a one-way clutch built into a multi-disc friction clutch, Fig. 4 is a view taken along the - line in Fig. 3, and Fig. 5 is a view of the roller-shaped connecting piece in the same-direction clutch. 6 is a cross-sectional view taken along the - line in FIG. 5, FIG. 7 is an explanatory diagram showing the operating mode of the same-direction clutch, and FIG. 8 is a side view of one clutch center in the multi-disc friction clutch. Figures 9, 10, and 11 are the - line, - line, and XI in Figure 8.
-XI line cut diagram, Figure 12 is XII- in Figure 11
The XII line arrow view and Figures 13 to 15 are the - line and - line in Figure 12, respectively.
- line cutaway view, FIG. 16 is a side view of the inner member in the one-way clutch, FIG. 17;
Figure 18 is - in Figure 16, respectively.
19 is a side view of the other clutch center in the multi-plate friction clutch, and FIGS. 20 and 21 are cross-sectional views taken along lines - and XI--XI in FIG. 19, respectively.
2 is a side view of the spring holding member in the same multi-plate friction clutch, FIG. 23 is a cross-sectional view taken along the - line in FIG. 22, and FIG. 24 is a side view of the pressure plate in the same multi-plate friction clutch.
25 is a cutaway view taken along the - line in FIG. 24, FIG. 26 is a side view of the lifter plate in the same multi-plate friction clutch, and FIGS. 27 and 28 are the - line in FIG. 26, respectively.
- A cutaway view. DESCRIPTION OF SYMBOLS 1... Multi-plate friction clutch, 2... Driven gear, 3... Clutch outer, 4... Clutch disc, 5... Clutch center, 5a... Boss portion, 5b... Concave groove, 5c... Rib, 5d... ...Through hole, 5e...Engagement piece, 5f...Groove, 5g, 5h...
...Through hole, 5i...Outer flange, 6...Clutch center, 6a...Concave groove, 6b...Engagement piece, 6c...
...Groove, 6d, 6e, 6f...Through hole, 7...Clutch plate, 8...Spring holding member, 8a
...Chin, 8b...Through hole, 9...Lock nut,
10a, 10b, 11...washier, 12...
Belleville spring, 13... Lifter plate, 13a...
Boss portion, 13b...rib, 14...pressure plate, 14a...jaw, 14b...pressure wall, 1
4c...Teeth, 14d...Through hole, 20...One-way clutch, 21...Ring-shaped frame member, 22...Wire frame, 23...Tension coil spring, 24...
...Rolled connection piece, 24a...inner surface, 24b...
Projecting surface, 24c...Flat surface, 24d...Groove, 25
...Inner member, 25a...Concave groove, 30...Crankshaft, 31...Drive gear, 40...
...Main shaft, 40a...Opening hole, 41...Lifter rod, 42...Cap, 42a...Head, 42b...Shaft cylinder part, 42c...Through hole, 43
... Bearing, 50 ... Oil discharge port.

Claims (1)

[Claims] 1 A plurality of clutch disks and clutch plates are alternately overlapped, and the clutch disks are engaged with the axial grooves of the clutch outer, and the clutch plates are engaged with the axial grooves of the clutch center that meshes with the main shaft. In a plate friction clutch, the clutch center is divided into two in the axial direction, and one clutch center located on the main shaft end side is fitted to the main shaft via a one-way clutch, and the one-way clutch transfers the engine output to the main shaft side. A spring holding member is fitted to the main shaft so as to be adjacent to the outside of the one-way clutch, and a pressure plate and the spring holding member are located outside of the one clutch center. A disc spring is engaged with the spring holding member, and a washer fitted onto the spring holding member is brought into contact with the side surface of the inner member of the one-way clutch, and a plurality of through holes provided in the spring holding member are connected to the side surface of the inner member. The provided plurality of concave grooves and the space defined by the washer are used as a lubricating oil supply path, and the lubricating oil discharged from the end of the main shaft is guided to the one-way clutch along the lubricating oil supply path. A multi-disc friction clutch characterized by being configured so as to force the clutch.