JP3223779B2 - Double disc clutch device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a double disc clutch device suitable for use in a power transmission system of a vehicle equipped with a high-output engine such as a large truck or a bus.

[0002]

2. Description of the Related Art In a power transmission system of a vehicle equipped with a high-output diesel engine such as a large truck or a bus, a double-plate clutch device having a plurality of clutch disks for transmitting a large torque is used.

A typical structure of a conventional double-plate clutch device will be described with reference to a schematic sectional view of FIG. A double-plate clutch device generally indicated by reference numeral 10 in the drawing includes a flywheel 14 mounted on a crankshaft or input shaft 12 of an engine, and a clutch mounted on a rear end of the flywheel 14 by a number of bolts 16. The cover 18 and the flywheel 1 supported by the clutch cover 18
Pressure plate or intermediate plate 20F and rear pressure plate 2 that rotate integrally with the clutch cover 4 and the clutch cover 18 and are axially displaceable.
And a front pressure plate 20F and a rear pressure plate mounted on an output shaft 22 coaxially disposed with respect to the crankshaft 12 via a spline. 20R, and a driven side including a front clutch disk 24F and a rear clutch disk 24R cooperating with each other, and the output shaft 22 has a drive pinion of a transmission 26, only a part of which is shown. Machine input shaft.

[0004] The front and rear pressure plates 20
The flywheel 14 and the flywheel 14R are supported at one end by a clutch cover 18 and at the other end by a pressure spring 28 contacting the rear pressure plate 20R.
When the clutch is connected, the friction facing 30F mounted on the outer peripheral portion of the front clutch disc 24F is pressed against the opposing friction surface of the flywheel 14 and the rear clutch disc 24F is engaged.
Friction facing 3 mounted on the outer periphery of R
When 0R is pressed against the front pressure plate 20F, the rotational force of the crankshaft, that is, the input shaft 12 is reduced.
The power is transmitted to the drive pinion, that is, the output shaft 22.

[0005] When the clutch is disengaged or released, the release bearing 32 slidably mounted on the output shaft 22 is displaced toward the flywheel 14 by the release fork 34, so that the release lever 36 is moved through the release lever 36. Front and rear pressure plates 20F and 20
R is displaced away from the flywheel 14.

The front and rear clutch discs 20F
And 20R, a hub 38 slidably fitted on the output shaft 22 via a spline, and a hub flange or hub plate 40 protruding from the outer periphery of the hub 38 and extending radially outward. And a clutch plate 42, which is arranged in a freely rotatable manner relative to the hub flange 40 and has the friction facings 30F and 30R mounted on its outer periphery.
Usually, a first-stage or first-stage torsion spring having a small spring constant and a second-stage torsion spring having a large spring constant are interposed between the hub flange 40 and the clutch plate 42, respectively. ing. The first-stage torsion spring operates in the first-stage operation region where the relative rotation angle, that is, the torsion angle between the hub flange 40 and the clutch plate 42 is small and the transmission torque is correspondingly small.
The relative rotation angle between 0 and the clutch plate 42 acts in the second-stage operation region having a large torsion angle exceeding the first-stage operation region.

[0007] In the conventional double-plate clutch device 10 described above,
Each of the clutch discs 24F and 24R has characteristics as shown in the torsion angle-transmitted torque diagram of FIG. 13, and from the neutral position O to the torsion angles θ ₁ , θ ₁ ′ of the first-stage torsion spring. The range from the twist angles θ ₁ , θ ₁ ′ to θ ₂ , θ ₂ ′ is the operation range of the second-stage torsion spring. As shown in the figure, the spring constant of the first-stage torsion spring is set to be extremely small in order to effectively reduce idle noise.

As described above, on the output shaft or drive pinion 22, the front and rear clutch discs 24F and 2F
By arranging the 4Rs side by side, when both clutch disks have substantially the same torsion angle-transmission torque characteristics, the transmission torque T of both clutch disks is added as shown in FIG. Te, the time of maximum twist angle theta ₂ in the operational range of the second stage torsion spring,
Approximately twice the transmission torque capacity should be obtained.

However, actually, since the spring constant of the first-stage torsion spring is set to be extremely small in order to reduce idle noise, the release lever 36 is rotated to move the rear pressure plate 20R to the flywheel or the torque transmitting member. In the process of displacing the clutch in the axial direction toward 14 and engaging the clutch, the engagement points of the front and rear clutch discs 24F and 24R are
As shown in the torsion angle-transmitted torque characteristic diagrams of FIGS. 15 and 16, the position is shifted from the original middle position, and furthermore, the direction of the shift is unstable and unstable. Therefore, the total torsion angle-transmitted torque characteristics of the front and rear clutch disks 24F and 24R are not constant, and are mainly used during idling operation in which the first-stage torsion spring operates, or when the clutch is released and then re-engaged for shifting. Very loud noises can often occur. In order to prevent the unstable fluctuation during the connection process in the torsion angle-transmission torque characteristic diagram as described above, the spring constant of the first-stage torsion spring may be made sufficiently large to operate as a neutral spring. When the spring constant of the first-stage torsion spring is increased, there is a problem that idle noise increases.

[0010]

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and solves the above-mentioned drawbacks of the conventional double-plate type clutch device, and has a characteristic of a twist angle-transmission torque characteristic at the time of clutch engagement. It is an object of the present invention to provide a clutch device of this kind that can prevent generation of noise based on a stable phenomenon and can effectively reduce idle noise.

[0011]

SUMMARY OF THE INVENTION To achieve the above object, the present invention provides an output shaft that is slidable in the axial direction.
A front clutch disc and a rear clutch disc, which are arranged side by side with relative rotation prohibited in the rotation direction, and a torque transmitting member connected to the input shaft and arranged to face one side of the front clutch disc; A front and rear pressure plate disposed between the front and rear clutch disks and behind the rear clutch disk, respectively, by moving the front and rear pressure plates in the axial direction with respect to the torque transmitting member, In the one configured to connect the input shaft and the output shaft or to cut off the connection between the input shaft and the output shaft, the front and rear clutch discs each have a multi-step transmission torque characteristic with respect to a torsion angle. And the transmission torque characteristic of one of the clutch disks with respect to the torsion angle in the first stage operating region is Proposes a multi-plate clutch device characterized by the transmission torque characteristics for torsional angle in the first stage operation range of the other clutch disc is set to have a torque characteristic of opposite polarities.

In the present invention, the one clutch disk is configured to generate a positive torsion angle with respect to a positive input torque in the first-stage operation region, and the other clutch disk is configured to generate the first-stage operation region. Is preferably configured to generate a negative torsion angle for a positive input torque. Further, in the present invention, the other clutch disk includes a hub slidably fitted on the output shaft, an inner hub flange extending radially outward from the hub and protruding from the hub. An outer hub flange concentrically disposed radially outward of the hub flange and rotatably disposed relative to the inner hub flange; and an inner hub flange interposed between the inner and outer hub flanges. A reversing mechanism for rotating the outer hub flange in the opposite direction when rotated in the direction, a first clutch plate and a first retaining plate disposed on both axial sides with respect to the inner and outer hub flanges, A first-stage torsion spring disposed between the clutch plate and the first retaining plate and the outer hub flange; The disc has a hub slidably fitted on the output shaft, an integral hub flange extending radially outward from the hub, and an axial hub on both sides in the axial direction with the hub flange interposed therebetween. It is preferable to include a first-stage torsion spring disposed between the second clutch plate and the second retaining plate disposed and the integral hub flange.

Further, in the present invention, the reversing mechanism includes external teeth formed on an outer periphery of the inner hub flange,
A pinion rotatably fitted to an internal tooth formed on the inner periphery of the outer hub flange and a stop pin connecting the first clutch plate and the first retaining plate to mesh with the external tooth and the internal tooth. Preferably, the reversing mechanism has one end inserted into a recess in the outer hub flange having an opening in the inner peripheral surface of the outer hub flange, and the other end connected to the inner hub flange. And an operation lever inserted into a recess having an opening in the outer peripheral surface thereof and an intermediate portion rotatably fitted to a stop pin connecting the first clutch plate and the first retaining plate. Can also. Further, it is preferable that the first-stage torsion springs of both the clutch disks have a spring constant that can hold each clutch disk in a neutral state at the start of torque transmission.

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A preferred embodiment of the present invention will be specifically described below with reference to FIGS. (Note that members or portions substantially the same as or corresponding to those of the conventional double-plate clutch device described with reference to FIGS. 12 to 16 are denoted by the same reference numerals, and redundant description is omitted.) 1 to 6 show one of the front clutch disk 24F and the rear clutch disk 24R in the conventional double-plate clutch device 10, for example, a clutch disk corresponding to the rear clutch disk 24R.
7 and 8 show a clutch disk corresponding to the other one, for example, the front clutch disk 24F.

As best shown in FIGS. 1 and 2,
The rear clutch disc 24R normally includes a cylindrical hub 38R splined on an output shaft 22 formed of a drive pinion of a transmission, and has an inner periphery extending radially outward on the outer periphery of the hub 38R. The hub flange 40a is formed integrally. An annular outer hub flange 40b is coaxially and rotatably disposed radially outside the inner hub flange 40a. A plurality (four in the illustrated case) of radially inwardly extending projections 44 are provided on the inner periphery of the outer hub flange 40b at appropriate angular intervals (90 in the illustrated case). Except for a portion adjacent to the projection 44, internal teeth 46 are formed on the inner peripheral surface between the projections.

On the outer peripheral surface of the inner hub flange 40a, external teeth 48 are provided on the outer peripheral surface except for a portion facing the projection 44 and portions adjacent to both sides thereof. A first clutch plate 42R and a first retaining plate 50R are disposed on both sides of the inner flange 40a and the outer flange 40b with an appropriate gap in the axial direction. The first clutch plate 42R and the first retaining plate 50R are provided between the inner and outer hub flanges 40a and 40b.
Are integrally connected by a plurality of (four in the illustrated case) stop pins 54 inserted through the arc-shaped voids or grooves 52 formed except for the part. Stop pin 54
The clutch disk 24 shown in FIG.
When R is in a neutral state, it is arranged so as to be located at the center between the protrusions 44. The drive side member including the first clutch plate 42R and the first retaining plate 50R is relatively rotatably supported by the hub 38R via the centering bush 56, as shown in FIG. In order to prevent backlash in the direction, an inner ring 58 and an outer ring 60 made of a resin material such as nylon are provided with an inner hub flange 40a and an outer hub flange 40b, respectively, and the first clutch plate 42R and the It is interposed between one retaining plate 50R.

The stop pin 54 is provided with the internal teeth 46.
A pinion or a small gear 62 meshing with the external teeth 48 is rotatably disposed. A first-stage or first-stage torsion spring 64 having a small spring constant is provided in the arc-shaped space or groove 52 on both sides of the projection 44. The first-stage torsion spring 64 is supported at both ends by a spring retainer 66. The spring retainer 66 has a U-shaped horizontal side 66a and a horizontal side 66a, as is well shown in the perspective view of FIG. It has a vertical side 66b extending in a direction perpendicular to the side 66a, and has a cross shape as a whole. The horizontal side 66a is housed in the arc-shaped space or groove 52, and the end of the vertical side 66b is located in openings 68 and 70 formed in the first clutch plate 42R and the first retaining plate 50R, respectively. It can be accommodated and slidable along the openings 68 and 78. (Note that in order to avoid excessive congestion in the drawing, the illustration of the opening 70 is omitted in FIG. 1 and is shown only in FIG. 3.)

Further, in the inner hub flange 40a, in the neutral state shown in FIG. 1, fan-shaped openings 72 extending substantially symmetrically on both sides around a radial line passing through the center of the projection 44 are formed in the same circle. Multiple on the circumference (4 in the case shown)
And a first clutch plate 40R and a first clutch plate 40R provided on both sides of the inner hub flange 40a.
The retaining plate 50R, the center angle theta ₁ in the clockwise direction in FIG. _', The opening of the short respectively the same center angle in the circumferential direction from only respectively the opening 72 circumferential angle theta ₁ counterclockwise 74
And 76 (see FIG. 4). Opening 74
A second-stage torsion spring 78 is accommodated in the first and second torsion springs 76. Both ends of the second torsion spring 78 are supported by circumferential ends of the openings 74 and 76 via spring retainers 80, respectively. The second stage torsion spring 78 has a spring constant that is sufficiently larger than the first stage torsion spring 64.

Rear clutch disc 2 having the above configuration
As shown in FIG. 2, a plurality of friction facings 30R arranged in a row on the outer periphery of the first clutch plate 42R are provided with a front pressure plate or an intermediate plate, similarly to the conventional double-plate clutch device 10. 20F and the rear pressure plate 20R in cooperation with the flywheel 14 as a torque transmitting member.
, The input shaft, that is, the crankshaft 12 of the engine, and the output shaft, that is, the drive pinion 22, are connected to transmit torque, or the connection between them is cut off.

[0020] The first stage torsion spring 64 has the sufficiently small spring constant K ₁ as compared with the spring constant K ₂ of the second stage torsion spring 78, but the front of the double plate type clutch device 10 of the previous and rear clutch disc 24F And 24R, the spring constant of the first-stage torsion spring is set to be sufficiently larger than the spring constant of the first-stage torsion spring, which is set to be extremely small in order to reduce idle noise.
Therefore, the rear clutch disc 24R is driven on the drive side as shown in FIG. 1 until the friction facing 30R frictionally engages with the rear pressure plate 20R and the transmission of torque is started, not to mention when there is no load. First
The clutch plate 42R and the first retaining plate 50R, and the inner and outer hub flanges 40a and 40b on the driven side are correctly held at the neutral positions, respectively.

The first clutch plate 42R and the first clutch plate 42R
When torque transmission from the retaining plate 50R to the inner and outer hub flanges 40a and 40b is started, as shown, during a positive twist angle θ ₁ (clockwise rotation is positive in FIG. 1). , Only the first stage torsion spring 64 operates, and its compression amount and spring constant K
_The torque corresponding to ₁ is transmitted to the outer hub flange 40b via the protrusion 44. The rotation of the outer hub flange 40b rotates the pinion or pinion 62 via the internal teeth 46, and the inner hub flange 40a rotates in the opposite direction via the external teeth 48 meshing with the pinion or pinion 62, A counterclockwise, that is, negative torque is transmitted to the output shaft, that is, the drive pinion 22 of the transmission, via the 38R.

[0022] Subsequently, the first clutch plate 42R and the first retaining plate 50R is, with respect to forward direction twist angle θ inner hub flange 40a exceed ₁ when relative rotation, the torsion spring 78 of the second stage is compressed ( 4), the compression amount of the spring 78 and the spring constant K
₂ and a hub 3 on the center line of the spring 78
Torque T obtained by multiplying the distance from the center of the 8R is transmitted to the output shaft or the drive pinion 22, twist the angle reaches theta _2, the first clutch plate 42R and the first and the retaining plate 50R, the inner and outer hub flange 40a And 40b rotate integrally. When torque transmission in the opposite direction to the above, that is, negative torque transmission (counterclockwise in FIG. 1) is performed between the driving side and the driven side,
Similarly to the above, the first-stage torsion spring 6 disposed on the opposite side to the above with the projection 44 interposed therebetween until the torsion angle θ ₁ ′.
Until the torsion angle exceeds θ ₁ ′ and reaches θ ₂ ′, the second-stage torsion spring 78 is compressed to transmit negative torque.

FIG. 10 shows the torsion angle-transmission torque characteristic of the rear clutch disk 24R. No friction washers or friction plates are provided between the first clutch plate 42R and the second retaining plate 50R and the inner and outer hub flanges 40a and 40b. Since the rings 58 and 60 made of resin such as nylon for preventing rattling are interposed,
As shown in FIG. 2, the torque characteristic has substantially no hysteresis torque, and the torque changes along a simple straight line.

Next, the front clutch disk 24F is substantially similar in structure to the front or rear clutch disk in the conventional double-plate clutch device 10, and an example of the structure will be described with reference to FIGS. 7 and 8. I do. The clutch disc 24F includes a cylindrical hub 38F spline-connected to the output shaft or the drive pinion 22 of the transmission, and a substantially disk-shaped hub flange 40F is provided on the outer periphery of the hub 38 in a radially outward direction. And are integrally formed. In addition, the hub flange 40
F, a second clutch plate 42F and a second retaining plate 50F with an appropriate gap in the axial direction.
The clutch plate 42F and the retaining plate 50F are integrally connected by a plurality of stop pins 82 arranged at an appropriate angular interval on the same circumference. Although not shown, friction facings 30F divided into a number of segments are arranged in a row on the outer peripheral portion of the second clutch plate 42F.
Cooperates with the flywheel 14 and the front friction plate or the intermediate plate 20F as the torque transmitting member, similarly to the conventional device shown in FIG.

Sub-plates 84 and 86 are provided between the second clutch plate 42F and the hub flange 40F and between the second retaining plate 50F and the hub flange 40F. Are integrally connected by a plurality of stopper pins 88 disposed on the same circumference at appropriate angular intervals. A relatively small spring constant K ₁ ′ is provided between the hub flange 40F and the sub-plates 84 and 86.
A first or first stage torsion spring 90 having a large spring constant K ₂ ′ is provided between the hub flange 40F and the second clutch plate 42F and the second retaining plate 50F. A step torsion spring 92 is provided.

Between the hub flange 40F and the sub-plates 84 and 86, first friction members, that is, friction washers 94 and 96 having a small coefficient of friction, respectively, are sandwiched. One friction washer 96 is a wave washer. The spring 98 is elastically pressed against the hub flange 40F. Further, the sub-plate 84
, 86 and the second clutch plate 42F and the second retaining plate 50F are provided with third friction washers 100 and 10 having a large friction coefficient, respectively.
2 are sandwiched.

In the hub flange 40F, a slot or notch 1 extending in the circumferential direction for accommodating the stopper pin 88 is provided.
04, and the pin 88 and the sub-plates 84 and 86 integral therewith are provided with a twist angle θ in a clockwise direction until the pin 88 contacts the circumferential end wall of the slot or notch 104.
₃ , the hub flange 4 by the twist angle θ ₃ ′ in the counterclockwise direction.
It can rotate relative to 0F. During this relative rotation, the first-stage torsion spring 90 is compressed corresponding to the torsion angle, and the first-stage friction washer 94 is formed.
And friction torque _{h 1} is generated by 96.

Similarly, the sub-plates 84 and 86 include
An elongated hole or notch 106 extending in the circumferential direction for accommodating the stopper pin 82 is provided. The stopper pin 82 and the integral second clutch plate 40F and second retaining plate 50F have a long pin 82. until it abuts against the circumferential end wall of the hole or notch 106, angle theta ₄ twist in a clockwise _direction, by the angle theta _{4 'twisted} in a counterclockwise direction, it is possible to rotate relative to the hub flange 40F. During this relative rotation, the torsion spring 92 of the second stage is compressed correspondingly to the helix angle, also by friction washer 100 and 102 of the second stage, the friction torque h ₂ is caused. The first-stage torsion spring 90 and the second-stage torsion spring 92 are connected to the hub flange 40.
F are accommodated in the openings 108 and 110, respectively, and the second
The clutch plate 42F and the second retaining plate 50F are provided with openings or windows for accommodating the first-stage torsion springs 90 and the second-stage torsion springs 92 corresponding to the openings 108 and 110, respectively.

The front clutch disk 24 having the above-mentioned normal structure
The torsion angle-transmission torque characteristics of F are as shown in FIG. The operating range of the first stage torsion spring 90 is O ~
θ _3, O~θ ₃ ', the rear clutch disc 24R
Are substantially the same as the first-stage operation regions O to θ ₁ , O to θ ₁ ′, and are the operation regions θ _{3 to} θ ₄ , θ of the second-stage torsion spring 92.
Similarly, ₃ ′ to θ ₄ ′ also correspond to the rear clutch disc 24F.
Are set substantially equal to the second-stage operation ranges θ _{1 to} θ ₂ and θ ₁ ′ to θ ₂ ′. The spring constant K ₁ ′ of the first-stage torsion spring 90 is determined not only when there is no load but also when the friction facing 30F mounted on the outer periphery of the second clutch plate 42F makes frictional contact with the contact surface of the flywheel 14 to engage the clutch. Neutral position O until mated or connected
As shown in FIG. 9, the spring constant K ₁ ′ is set to be larger than the spring constant of the first-stage torsion spring in a normal clutch disk that is effective in reducing idle noise. Further, the torque T transmitted by the first-stage torsion spring 90
Is such that the torsion angle θ is a positive torque in the positive operation range, and is slightly larger in absolute value than the negative torque (see FIG. 10) generated in the rear clutch disc 24R at the same torsion angle θ. Is set to

The front clutch disk 24F as described above
In the double-plate clutch device 10 provided with the rear clutch disk 24R, the first stage torsion springs 64 and 90 of the respective clutch disks are engaged or connected in the clutch disengaged state to start transmission of torque. At this time, there is a sufficient spring constant K that can hold each clutch disc correctly in the neutral state.
₁ and K ₁ ′, when the clutch is engaged, FIG.
As shown in FIG. 1, the torsion angle-transmission torque characteristic of the front clutch disk 24F shown in FIG. 9 and the torsion angle-transmission torque characteristic of the rear clutch disk 24R shown in FIG. It is possible to obtain the torsional angle-transmitted torque characteristics of the double-plate clutch added by equalizing the point O (neutral point).

As is clear from the characteristic diagram of FIG. 11, in the first stage operating region of the front clutch disk 24F, a positive torque is transmitted with respect to a positive torsion angle θ (= O to θ ₃ ), while a rear clutch is transmitted. In the first-stage operation region of the disk 24R, as a result of transmitting a negative torque for the same positive torsion angle θ (= O to θ ₁ ), the illustrated first-stage operation region θ is applied to the output shaft or the drive pinion 22. in O～shita _5, it is transmitted is small positive torque subtracted both the negative twist angle operation range θ = O~θ _{5 'Similarly,} it is the small negative torque is transmitted, the total torque In addition, a twist angle-transmission torque characteristic that is extremely effective in reducing idle noise can be obtained.

The front and rear clutch disks 24
Exceeds the torsional angle is respectively theta ₁ of F and 24R, in the region where the second stage torsion spring 92 and 78 is operated, the torque transmitted in the area of the twist angle θ = θ ₃ ~θ ₄ shown in FIG. 9 And the torsion angle θ = θ shown in FIG.
₁ and the torque transmitted in the region of the through? ₂ are added, as shown in FIG. 11, in the region of the twist angle θ = θ ₅ ~θ _6, sufficient to be requested multi-plate clutch disc 10 A large torque is transmitted, and a large output torque of a high-output engine such as a large truck or a bus can be effectively transmitted to the transmission 26. In order to smooth the torque transmission of the front and rear clutch discs 24F and 24R to the output shaft 22, and to achieve an effective reduction of idle noise, each clutch disc 2
Torsion angle θ ₁ = 4F and 24R to limit the first stage operating range
θ ₃ = θ ₅ , θ ₁ ′ = θ ₃ ′ = θ ₅ ′, θ ₂ = θ ₄ = θ
₆ , θ ₂ ′ = θ ₄ ′ = θ ₆ ′.

FIG. 6 is a front view of a main part showing a modified example of the rear clutch disk 24R shown in FIGS. 1 and 2. In this modification, a lever member 112 is rotatably mounted on a stopper pin 54 that integrally couples the first clutch plate 42R and the first retaining plate 50R, and the lever member 112 has one arm portion thereof. Is inserted into a recess 114 provided in the outer hub flange 40b, and the other arm is inserted into a recess 116 provided in the inner hub flange 40a. In the illustrated neutral position, the lever member 112 is positioned to be substantially radially oriented and the recess 114 accommodates the radially outward and radial arms of the lever member 112. And 116 are formed so as to abut each of the arms with a gentle curved surface.

In this variation, the outer hub flange 4
When 0b rotates in one direction around the axis of the output shaft or the drive pinion 22, the inner hub flange 40a rotates in the opposite direction via the lever member 112 and meshes with the pinion or pinion 62 described above. It is clear that a function equivalent to the reversing mechanism consisting of the internal teeth 46 and the external teeth 48 is achieved. Further, according to this modified example, since there is no need to form the meshing teeth, there is an advantage that the structure is simple and the manufacturing cost can be reduced.

In the above-described embodiment, the front clutch disk 24F is a clutch disk having a normal structure, and the rear clutch disk 24R has reverse torsional angle-transmitting torque characteristics in the first stage operation region with respect to the clutch disk having the normal structure. The clutch disk is arranged to form a double-plate clutch device. Contrary to the above, a clutch disk having a twist angle-transfer torque characteristic opposite to that of the clutch disk of the normal structure is arranged on the front clutch disk 24F. Alternatively, a clutch disk having a normal structure may be arranged on the cooperating rear clutch disk. Also,
In the illustrated embodiment, each clutch disc 24F and 24R includes a first-stage torsion spring having a small spring constant and a second-stage torsion spring that is sufficiently larger than the first-stage torsion spring. Third having a spring constant greater than the spring
Obviously, a step torsion spring can be provided.

[0036]

As described above, the double-disc clutch device according to the present invention is juxtaposed on the output shaft so as to be slidable in the axial direction and prohibited from rotating in the rotational direction. A front clutch disk, a rear clutch disk, a torque transmitting member connected to the input shaft and disposed opposite to one side of the front clutch disk, and between the front and rear clutch disks and behind the rear clutch disk, respectively. Comprising front and rear pressure plates disposed therein,
The input and output shafts are connected or the input and output shafts are disconnected by moving the front and rear pressure plates in the axial direction with respect to the torque transmitting member. In the front and rear clutch disks, the transmission torque characteristic with respect to the torsion angle is set in multiple stages, respectively, and the transmission torque characteristic with respect to the torsion angle in the first stage operation range of one of the clutch disks is the first stage operation of the other clutch disk. The transmission torque characteristic for the torsion angle in the range is set to have a torque characteristic opposite to the positive and negative, and the neutral position at the time of clutch engagement or connection of the front and rear clutch discs is substantially matched and stable. Since it is possible to obtain a twist angle-transmission torque characteristic, Together may reduce the generation of noise effectively, efficiently is achieved can benefit to reduce the idle noise.

Further, in the above invention, the other clutch disc comprises a hub slidably fitted to the output shaft, and an inner hub flange projecting radially outward from the hub. An outer hub flange concentrically disposed radially outward of the inner hub flange and rotatably disposed relative to the inner hub flange; and an inner hub flange interposed between the inner and outer hub flanges. A reversing mechanism for rotating the outer hub flange in the opposite direction when the hub flange rotates in one direction; a first clutch plate and a first retaining plate disposed on both axial sides with the inner and outer hub flanges interposed therebetween; A first stage torsion spring disposed between the first clutch plate and the first retaining plate and the outer hub flange, and Serial one of the clutch discs, and a hub which is slidably fitted to the output shaft, integral with the hub flange projecting extending radially outwardly from said hub,
The second is disposed on both sides in the axial direction with the hub flange interposed therebetween.
A first stage torsion spring is provided between the clutch plate and the second retaining plate and the integral hub flange. There is an advantage that it is possible to provide a double-plate clutch device having a simple structure capable of effectively preventing an unstable phenomenon at the time of connection to reduce noise and reducing idle noise.

[Brief description of the drawings]

FIG. 1 is a front view (partially cut away) of a main part showing an example of a preferred embodiment of a rear clutch disk in a double-plate clutch device according to the present invention.

FIG. 2 is a sectional view taken along line II-II in FIG.

FIG. 3 is a sectional view taken along line III-III in FIG.

FIG. 4 is a sectional view taken along the line IV-IV in FIG. 1;

FIG. 5 is a perspective view of a spring retainer 66 interposed at both ends of a first-stage spring 64 in FIG. 1;

FIG. 6 is a front view showing an essential part of a modified example of the rear clutch disk shown in FIG. 1;

FIG. 7 is a cross-sectional view of a main part showing an example of an embodiment of a front clutch disk in the double-plate clutch device according to the present invention.

FIG. 8 is a front view (partially cut away) of a main part of the clutch disk shown in FIG. 7;

FIG. 9 is a graph showing a relationship between a torsion angle and a transmission torque characteristic of the front clutch disc shown in FIG. 7;

FIG. 10 is a diagram showing a twist angle-transmitted torque characteristic of the rear clutch disk shown in FIG. 1;

11 is a diagram showing a torsion angle-transmitting torque characteristic of a double disc clutch device in which the rear clutch disc shown in FIG. 1 and the front clutch disc shown in FIG. 7 are combined.

FIG. 12 is a schematic sectional view showing the configuration of a conventional double-plate clutch device.

FIG. 13 is a graph showing desirable torsional angle-transmitted torque characteristics of each of the front and rear clutch disks in the double-plate clutch device shown in FIG. 12;

FIG. 14 is a graph showing desirable torsional angle-transmitted torque characteristics when the front and rear clutch discs are combined in the double-plate clutch device shown in FIG. 12; "

15 is a diagram showing an example of an undesired torsion angle-transmitted torque characteristic that may actually occur in the front and rear clutch discs in the double-plate clutch device shown in FIG. 12;

FIG. 16 is a diagram showing an example of an undesired torsion angle-transmitted torque characteristic that may actually occur in the front and rear clutch discs in the double-plate clutch device shown in FIG. 12;

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 10 ... Double-plate clutch device, 12 ... Crankshaft (input shaft), 14 ... Flywheel (torque transmission member), 18
... clutch cover, 20F ... front pressure plate or intermediate plate, 20R ... rear pressure plate, 22 ... output shaft (drive pinion), 24
F: front clutch disc, 24R: rear clutch disc, 28: pressure spring, 30F and 30R
... friction facing, 32 ... release bearing, 34 ... release fork, 38 ... hub, 40 and 4
0F: hub flange, 40a: inner hub flange, 40
b: outer hub flange, 42F: second clutch plate, 42R: first clutch plate, 46: internal teeth, 48
... external teeth, 50F ... second retaining plate, 50R ...
1st retaining plate, 54 ... stop pin, 62
... Pinion or small gear, 64 ... First stage torsion spring, 66 ... Spring retainer, 78 ... Second stage torsion spring, 84 and 86 ... Subplate, 90 ... First stage torsion spring, 92 ... Second stage torsion spring, 112 ... Lever member , 114 and 116 ... recesses.

Continuation of front page (58) Field surveyed (Int.Cl. ⁷ , DB name) F16D 13/46 F16D 13/64

Claims (4)

(57) [Claims] 1. An output shaft that is slidable in the axial direction,
A front clutch disc and a rear clutch disc, which are arranged side by side with relative rotation prohibited in the rotation direction, and a torque transmitting member connected to the input shaft and arranged to face one side of the front clutch disc; A front and rear pressure plate disposed between the front and rear clutch disks and behind the rear clutch disk, respectively, by moving the front and rear pressure plates in the axial direction with respect to the torque transmitting member, In the one configured to connect the input shaft and the output shaft or to cut off the connection between the input shaft and the output shaft, the front and rear clutch discs each have a multi-step transmission torque characteristic with respect to a torsion angle. And the transmission torque characteristic of one of the clutch disks with respect to the torsion angle in the first stage operating region is Multi-plate clutch device characterized by the transmission torque characteristics for twist angle at the first stage operation range of the other clutch disc is set to have a torque characteristic of opposite polarities. 2. The clutch disk according to claim 1, wherein the one clutch disk is configured to generate a positive torsion angle with respect to a positive input torque in the first-stage operation region, and the other clutch disk is configured to generate a positive input torque in the first-stage operation region. The double-plate clutch device according to claim 1, wherein the clutch device is configured to generate a negative twist angle with respect to torque. 3. The other clutch disk includes a hub slidably fitted on the output shaft, an inner hub flange extending radially outward from the hub, and an inner hub flange. An outer hub flange concentrically disposed radially outward of the hub flange and rotatably disposed relative to the inner hub flange; and an inner hub flange interposed between the inner and outer hub flanges. A reversing mechanism for rotating the outer hub flange in the opposite direction when rotated in the direction, a first clutch plate and a first retaining plate disposed on both axial sides with respect to the inner and outer hub flanges, A first-stage torsion spring disposed between the clutch plate and the first retaining plate and the outer hub flange; The hub is slidably fitted on the output shaft, an integral hub flange extending radially outward from the hub and projecting therefrom, and on both sides in the axial direction with the hub flange interposed therebetween. 3. The vehicle according to claim 1, further comprising a first-stage torsion spring disposed between the second clutch plate and the second retaining plate and the integral hub flange. Double-plate clutch device. 4. The reversing mechanism includes external teeth formed on an outer periphery of the inner hub flange, internal teeth formed on an inner periphery of the outer hub flange, a first clutch plate and a first retaining plate. 4. The double-plate clutch device according to claim 3, further comprising: a pinion rotatably fitted to a stop pin that couples the external teeth and the internal teeth.