JPH0680331B2 - Friction clutch for automobile - Google Patents

Description

Description: FIELD OF THE INVENTION The present invention relates to a friction clutch for motor vehicles, in particular to a clutch having a flywheel consisting of two flywheels connected to each other via a rotationally elastic vibration damper.

BACKGROUND OF THE INVENTION A friction clutch for motor vehicles, known from DE-A 2931 423, has two essentially ring-shaped baffles connected to one another via a rotary-elastic vibration damper. There is. The first baffle plate fixed to the crankshaft has a bearing additional portion within the range of the inner peripheral surface thereof, and the second baffle plate is supported by the additional portion via a boss member.
This second baffle plate forms the pressure plate unit of the clutch. The second baffle plate is screwed to the boss member of the rotationally elastic vibration damper in its inner peripheral surface range,
The boss member is supported on the bearing addition portion of the first baffle plate via a slide bearing. Further, the plate member of the vibration damper is guided to the first fly plate via the friction mechanism within the range of the outer peripheral surface thereof, and the boss member is fixed in position in the axial direction by the plate member. . Side plates are provided on the boss member on both sides in the axial direction of the plate member. The spring of the vibration damper is located in each window of the plate member and the side plate, and is elastically loaded when both the fly plates (flywheels) rotate relative to each other.

During operation, the temperature of the second baffle, which acts as the corresponding pressure plate for the clutch, rises to about 350 ° C. In the known clutch, its high temperature acts directly on the plain bearing in a very short path. This causes problems with lubrication of the plain bearing. Bearing play is also generated due to the large temperature difference. In addition, the second baffle plate, which acts as a corresponding pressure plate, can be deflected due to this high temperature, and the high bearing forces that result from this deflection can cause damage to the plain bearing in question.

In the friction clutch for motor vehicles known from DE-A 28 26 274, the flywheel consists of two flywheels, which are also connected to each other via a rotationally elastic vibration damper. Also in this bounce plate, the first baffle plate, which is fixed to the crankshaft, holds the bearing addition portion, and the second baffle plate is directly supported by this bearing addition portion via the slide bearing. Therefore, also in this case, the same problem as in the above-mentioned example occurs.

Side plates are arranged on both axial sides of the first baffle plate, and each side plate forms a unit with each other and with the second baffle plate. Within each window of the first baffle plate and both side plates, there are arranged springs of a vibration damper which rotationally elastically interconnect both baffle plates. This vibration damper has a friction damping member designed for load operation. The structure of the clutch plate, which is schematically shown in the specification drawings of this known example, is relatively expensive as viewed from the drawings. This clutch plate has one boss member having a boss flange, and one plate portion plate having two side plates arranged on both sides in the axial direction of the boss flange. This structure is similar to the vibration dampers already used in other clutch plates. The clutch plate of this known clutch has a relatively large moment of inertia and thus causes a load on the synchronizer of the vehicle transmission during switching.

OBJECT OF THE INVENTION The object of the invention is to improve a friction clutch for motor vehicles of the type mentioned at the outset, which has two flywheels which are rotationally elastically interconnected, so as to ensure reliable operation even in the case of large temperature fluctuations inside the clutch. What is needed is to be operable and easy to assemble.

Means for Solving the Problems According to the present invention, the above object is to add a bearing in which an inner plate member is formed separately from the first baffle plate and is detachably coupled to the first baffle plate. Rotatably mounted on the part, the first baffle plate and the bearing addition part having holes aligned with each other through which a common screw for fixing to the crankshaft passes. Resolved

In the friction clutch according to the invention, a vibration damper, which is preferably designed for load operation, is arranged, possibly with its friction damper, between the two baffles in the axial direction. This vibration damper has two outer plate members which are interconnected as a unit and are non-rotatably held by a first baffle plate screwed to a crankshaft, and between the outer plate members. And one inner plate member disposed in the. These plate members are arranged side by side like the conventional vibration damper, and are rotationally elastically supported to each other via a spring. The inner plate member is rotatably supported by the bearing addition portion of the first baffle plate within the range of the inner peripheral surface of the inner plate member. Further, the second baffle plate is fixed to the outer peripheral surface of the inner plate member within the range of the outer peripheral surface thereof. As a result, a relatively long heat transfer path is formed between the second baffle plate and the bearing part of the second baffle plate to the bearing-added part of the first baffle plate. The second baffle plate is used as a corresponding pressure plate for the clutch plate, and any resulting warping action does not impair its bearing. The second baffle plate is preferably connected by screws to the first baffle plate, which allows its assembly, including the other components of the clutch, to be carried out smoothly. Furthermore, it is advantageous if the clutch casing is also fixed to the inner plate member by means of the same screws.

The bearing addition portion, which is formed separately from the first baffle plate, is provided by the centering member arranged on the first baffle plate, for example, the ring shoulder arranged on the inner peripheral surface of the first baffle plate. It is advantageous to be centered with respect to the flywheel.

Each outer plate member of the vibration damper is connected to one unit and can be fixed to the first baffle plate by, for example, a riveted connection of the outer plate member adjacent to the first baffle plate. Also one of the outer plate members, preferably also the first
The plate member adjacent to the baffle plate has teeth on its inner peripheral surface, which are pivoted into the corresponding teeth of the bearing attachment part which is detachably connected to the first baffle plate. It is also possible for them to be disengaged and thereby significantly facilitate the assembly of the clutch. This allows the vibration damper, including the second baffle plate and the remaining components of the clutch, to be retrofitted to the first baffle plate and the crankshaft with each threaded connection. Aspects according to the invention, which can also be used in other types of automotive clutch plates, having two baffles that are rotationally elastically interconnected relate to a vibration damper. The vibration damper which rotationally elastically interconnects both baffles has one friction damper and is designed exclusively for load operation. However, the clutch plates likewise have vibration dampers designed exclusively for idle operation. This allows both vibration dampers to be optimally designed for their own operating range. Since the vibration damper of the clutch plate is designed exclusively for idling operation, the weight of the clutch plate and thus its moment of inertia can be kept very small. The clutch plate has a boss portion and a ring plate-shaped plate member supported by the boss portion so as to be rotatable relative to the boss portion while holding the clutch lining over a predetermined rotation angle. is doing. The vibration damper for idling has a spring coefficient of values of 0.1 to 0.3 Newton-Mer / grad, so that it is possible to use very small springs.

Due to the limited rotation angle of the plate member with respect to the boss portion, the vibration damper for idling operation is bridged and brought into a non-operating state when shifting to load operation.
According to an advantageous embodiment of the invention for forming this rotation angle limitation, external teeth are arranged on the outer peripheral surface of the boss portion, and internal teeth of the leg fixedly connected to the plate member are external teeth thereof. It fits inside with play in the circumferential direction. The vibration damper for idling operation is fixed to the boss portion on one side and to the leg portion on the other side in order to rotationally and elastically connect the plate member and the boss portion. For this purpose, the bosses project axially from the legs.

According to a suitable embodiment of the vibration damper for idling operation, one boss plate that protrudes from the boss portion in the radial direction and two boss plates that are arranged on both axial sides of the boss plate and are held by the legs are provided. A side plate is provided. This corner side plate is rotatably supported by each boss plate through each spring of the vibration damper for idling operation. Further, in order to keep the weight and the moment of inertia of the clutch plate small, it is advantageous that the outer diameters of the boss plate and the side plate are formed smaller than the inner diameter of the plate member inside the vibration damper for load operation.

EXAMPLE The friction clutch for a motor vehicle shown in FIG. 1 has a first baffle plate 1 in the form of a substantially ring plate, in the region of its inner peripheral surface of the baffle plate 1, by means of a screw 3 the car is illustrated. It is fixed to a crankshaft 7 of an internal combustion engine, which is not mounted, which is rotatable around a rotation axis 5. In this first baffle plate 1,
A second flywheel 11 is rotationally and elastically connected via a rotary vibration damper 9 designed for load operation, and a flywheel is formed by the two flywheels 1 and 11.
Furthermore, a pressure plate is provided on the side opposite to the first baffle plate 1 in the axial direction.
13 is arranged, which is axially slidable but pivotable, as is known, for example by means of a tangential strap, not shown, on a second flywheel 11 acting as a corresponding pressure plate. Guided to be impossible. A lining 15 of a clutch plate 17 is fastened between the pressure plate 13 and the second baffle plate 11 when viewed in the axial direction, and a boss member 19 of the clutch plate 17 is shown with a tooth portion 21 in between. It is connected non-rotatably but axially slidably to the inlet shaft 23 of the unincorporated motor vehicle transmission. Further, a clutch casing 25 covering the clutch plate 17 and the pressure plate 13 is connected to the second baffle plate 11, and this clutch casing 25 has a support ribet.
A diaphragm spring 29 is supported via 27. The diaphragm spring 29 has a protrusion on the pressure plate 13 with its outer peripheral portion.
It is in contact with 31 and presses this pressure plate 13 against the second baffle plate 11 via the lining 15. To cut off the clutch, the tongue 33 of this diaphragm spring 29 is moved in the direction of the second baffle plate 11 by means of a clutch breaking mechanism (not shown), whereby the pressure plate 13 is unloaded. It is pulled away from the plate 17.

The rotary vibration damper 9 includes both baffles 1, 1 when viewed in the axial direction.
11 has a ring plate-shaped plate member 35, 37 arranged between 11,
The plate members 35 and 37 are connected to each other via a plurality of webs 39 at a distance. A plate member adjacent to the fly plate 1
35 is fixed to the baffle plate 1 by a rivet 41. Between the two outer plate members 35 and 37 when viewed in the axial direction, a substantially ring-plate-shaped inner plate member 43 is arranged so as to be rotatable relative to the outer plate member. The inner plate member 43 is connected to the baffle plate 1 in the region of its inner peripheral surface via rolling bearings formed by two inclined ball bearings 45, 47 facing each other in the illustrated example. It is rotatably supported by the ring-shaped bearing addition portion 49. The window 51 of the inner plate member 43 and the outer plate members 35, 37
Of the compression coil spring 5 in the windows 53 and 55 aligned with the window 51.
7 are arranged, and this spring 57 includes the plate member 43 and the plate member 35,
It is elastically loaded when it rotates relative to 37. Vibration damper 9
Has several such springs 57, which are distributed circumferentially on approximately one arc of the same diameter.

The inner plate member 43 projects in the radial direction to the outside of the arrangement arc of the spring 57, beyond the outer plate members 35 and 37. In this radially outer region of the plate member 43, the second baffle plate 11 and the clutch casing 25 are screwed by means of a shared screw 59. Bounce plate 11 acting as a corresponding pressure plate
When is heated during operation, the heat transfer from the baffle plate 11 to the inclined ball bearings 45, 47 is almost always performed via the detour passing through the plate member 43. This reduces the heat load on the bearing. Furthermore, this bearing is mechanically isolated from the baffle plate 11, so that the thermal warp of the baffle plate 11 does not affect the bearing.

The bearing adding portion 49 is held on the flywheel 1 by the same screw 3 that fixes the flywheel 1 to the crankshaft 7. In this case, the screw 3 is arranged through the holes 61 and 63 in the baffle plate 1 and the bearing add-on 49 which are aligned with each other. A ring holder 65 is arranged on the inner peripheral surface of the baffle plate 1 for centering the bearing adding portion 49. Further, another ring holder 67 of the bearing adding portion 49 cooperates with the second baffle plate 11 to fix the inner races of the ball bearings 45, 47 in the axial direction. On the inner peripheral surface of the inner plate member 43, there is arranged a ring-shaped bearing flange 69 projecting in the axial direction toward the baffle plate 11.
Thus, the plate member 43 is prevented from tilting and is supported by the outer races of the ball bearings 45, 47 in the radial direction. In order to fix the plate member 43 in the axial direction, a spring ring 71 is mounted in a ring groove on the inner peripheral surface of the bearing flange 69, and this spring ring 71 is mounted on both outer races of the ball bearings 45, 47. Are engaged between. The depth of the annular gear between the outer races is designed so that the spring ring 71 can be inserted into this groove when the bearing flange 69 is installed.

The rotary vibration damper 9 has a plurality of friction mechanisms, which act in a known manner depending on the relative rotation angles of both baffles 1, 11. The first friction mechanism 73 is arranged within the bearing flange 69. This mechanism 73 includes a friction ring 75 arranged between the fly plate 1 and the plate member 43 when viewed in the axial direction, and a ring arranged between the friction ring 75 and the plate member 43 when viewed in the axial direction. The pressing plate 77 and the disc spring 79 tightened between the pressing plate 77 and the plate member 43 are provided. While the friction mechanism 73 is effective at all relative rotation angles of the baffles 1 and 11, another friction mechanism 81 starts only when the relative rotation angle between the baffles 1 and 11 exceeds a predetermined value. It becomes effective. The friction mechanism 81 has a control disc 83 arranged between the plate members 35 and 43 when viewed in the axial direction, and the control arm 85 of the control disc 83 is arranged in a conventional manner. The insertion angle is limited, and the mechanism 81 further includes plate members 37 and 43 when viewed in the axial direction.
It has a pressing plate 87 disposed between and. This pressing plate
87 may optionally be formed as a control disc.
The control disc 83 has an axial tongue 89 that passes through the window 51 of the plate member 43. A disc spring 91 is tightened between the free end of the tongue piece 89 and the pressing plate 87.
Thus, the control disk 83 is pressed against the plate member 35 and the pressing plate 87 is pressed against the plate member 37 for the formation of the friction torque. Other structures are possible for this friction mechanism.

Further, the flywheel 1 holds a starter tooth ring 93.

FIG. 3 shows an embodiment of the variation of the automobile friction clutch according to the present invention. The main points of this example different from the clutch of FIG. 1 are the mounting method of the load vibration damper and the idling operation. The designed vibration damper is additionally arranged on the clutch plate.

The motor vehicle friction clutch shown in FIG. 3 also has a first baffle plate 101, which is substantially ring-shaped, which is shown within the inner peripheral surface of the vehicle by means of a screw 103. It is fixed to a crankshaft 107, which is rotatable about an axis of rotation 105, of an internal combustion engine that is not installed. A second baffle plate 111 is rotationally elastically connected to the first baffle plate 101 via a rotary vibration damper 109 designed for load operation. Further, a pressure plate 113 is arranged on the side opposite to the first baffle plate 101 in the axial direction, and the pressure plate 113 is arranged.
Is known, for example by means of a tangential strap (not shown) or the like, a second baffle plate 11 acting as a corresponding pressure plate.
1, the guide is slidable in the axial direction but not rotatable. A lining 115 of a clutch plate 117 is fastened between the pressure plate 113 and the second baffle plate 111 when viewed in the axial direction, and a boss 119 of the clutch plate 117 is shown via a tooth 121. Not connected to the inlet shaft 123 of a vehicle transmission which is not rotatable but slidably in the axial direction. Further second
A clutch casing 125 that covers a clutch plate 117 and a pressure plate 113 is coupled to the baffle plate 111, and a diaphragm spring 129 is supported by the clutch casing 125 via a support rivet 127. Diaphragm spring 129
Is in contact with the projection 131 of the pressure plate 113 with its outer peripheral portion, and the pressure plate 113 is pressed against the second baffle plate 111 via the lining 115. For blocking the clutch, the tongue 133 of the diaphragm spring 129 is moved towards the second baffle plate 111 by means of a clutch blocking mechanism, not shown, whereby the pressure plate 113 is unloaded. Separated from 117.

The vibration damper 109, which rotationally elastically interconnects both baffles 101, 111, is designed only for load operation.
The boss 119 of the clutch plate 117 is divided in the radial direction as will be described later, and the respective boss portions are rotationally and elastically connected to each other via a vibration damper 134 designed for idling operation. By thus disposing the two vibration damping mechanisms 109, 134 separately for the flywheel formed by both of the flywheels 101, 111 and the clutch plate 117, each vibration damping mechanism has its corresponding operating range. Can be optimally designed for. The springs of the vibration damper 109 for load operation have a relatively large radial distance with respect to the axis of rotation 105, preferably the clutch lining 115.
Are arranged with a distance corresponding to or greater than the radial distance with respect to the axis of rotation 105. Therefore, a relatively large space is available for mounting the idling vibration damper 134. Clutch board 117
Has a much smaller weight and moment of inertia than conventional clutches that dampen rotational vibrations, and therefore relatively less load on the synchronizer of the vehicle transmission. The spring coefficient of the vibration damper for idling can be very small, for example 0.1 to 0.3 newton meters / gra
It is the size of d.

The rotary vibration damper 109 has two baffles 1 when viewed in the axial direction.
It has ring plate-shaped plate members 135 and 137 arranged between 01 and 111, and these plate members 135 and 137 are connected to each other via a plurality of webs 139 at a distance. The plate member 135 adjacent to the fly plate 101 has a tooth portion 141 on its inner peripheral surface.
The plate member 135 is non-rotatably connected to the baffle plate 101 by a method described later by means of 141. An inner ring-shaped plate member 143 is arranged between the two outer plate members 135 and 137 as viewed in the axial direction so as to be rotatable relative to the outer plate member. The inner plate member 143 is rotatably supported by a ring-shaped bearing addition portion 149 connected to the fly plate 101 via a ball bearing 145 in the range of the inner peripheral surface thereof. The window 151 of the inner plate member 143 and the outer plate member 13
A compression coil spring 157 is disposed in each of the windows 153 and 155 of the 5,137 aligned with the window 151.
It is elastically loaded when the 3 and the plate members 135 and 137 rotate relative to each other. The vibration damper 109 for load operation has such a spring 157.
Which are distributed circumferentially on approximately one arc of the same diameter.

The plate member 143 on the inner side is located outside the arc where the spring 157 is arranged,
It projects in the radial direction beyond the outer plate members 135 and 137. In this radially outer region of the plate member 143, the second baffle plate 111 and the clutch casing 125 are screwed by means of a shared screw 159. In FIG. 3, this outer area and the screw 159 are shown in phantom, because they are located offset by a predetermined angle about the axis of rotation 105 with respect to the section shown in solid lines in FIG. Because they are doing it. When the baffle plate 111 acting as a corresponding pressure plate is heated during operation, heat is transferred from the baffle plate 111 to the ball bearings 145 almost only through the path through the plate member 143. This reduces the heat load on the bearing 145. Furthermore, this bearing is mechanically isolated from the baffle plate 111, so that the thermal bow of the baffle plate 111 does not affect the bearing.

The bearing addition portion 149 fixes the flywheel 101 to the crankshaft 107. It is held on the flywheel 101 by the same screw 103. In this case, the screw 103 is arranged through the holes 161 and 163 in the baffle plate 101 and the bearing addition 149 which are aligned with each other. In addition, a ring shoulder (not shown) can be arranged on the inner peripheral surface of the baffle plate 101 for centering the bearing adding portion 149. Another ring holder 167 included in the bearing addition portion 149 is a second baffle plate.
In cooperation with 101 and the spacer ring 168, the inner race of the ball bearing 145 is axially fixed relative to the baffle plate 101. On the inner peripheral surface of the plate member 143, a ring-shaped bearing flange 169 protruding in the axial direction toward the fly plate 111.
The bearing flange 169 prevents the plate member 143 from tilting and is radially supported by the outer race of the ball bearing 145. In order to fix the plate member 143 in the bearing direction, a spring ring 171 is engaged in a ring groove on the inner peripheral surface of the bearing flange 169. This spring ring 171 is located in the outer race groove of the ball bearing 145, the depth of which is such that the spring ring 171 can be completely inserted into this outer race groove when the bearing flange 169 is installed. Is designed to.

The rotary vibration damper 109 for load operation has a plurality of friction mechanisms, which act in a known manner according to the relative rotation angles of both baffles 101, 111. The first friction mechanism 173 is arranged within the bearing flange 169. This mechanism173
Is a friction ring 175 disposed between the flywheel 101 and the plate member 143 when viewed in the axial direction, and a ring-shaped pressing force disposed between the friction ring 175 and the plate member 143 when viewed in the axial direction. Board
177 and a disc spring 179 clamped between the pressing plate 177 and the plate member 143. The pressing plate 177 is non-rotatably connected to the plate member 143 so as to be slidable in the axial direction.
While the friction mechanism 173 is effective at all relative rotation angles of the baffles 101 and 111, the other friction mechanism 181 becomes effective only when the relative rotation angle between the two baffles 101 and 111 exceeds a predetermined value. The friction mechanism 181 includes a control disc disposed between the plate members 135 and 143 when viewed in the axial direction.
183, and the control arm 85 of the control disc 183 limits the insertion angle of the friction mechanism 181 in a conventional manner. Furthermore, the mechanism 181 is arranged such that it is arranged between the plate members 137 and 143 in the axial direction and in some cases also serves as a control plate.
Has 187. The control disc 183 has an axial tongue piece 189 penetrating the window 151 of the plate member 143. A disc spring 191 is clamped between the free end of the tongue piece 189 and the pressing plate 187, and a control disc 183 is attached to the plate member 135 for forming a friction torque by the disc spring 191. On the other hand, the pressing plate 187 is pressed against the plate member 137. Other structures are possible for this friction mechanism. The baffle plate 101 also holds a starter tooth ring 193.

The vibration damper 134 for idling operation is the clutch plate 117.
Located almost entirely within the boss 119 range. The boss 119 has a substantially sleeve-shaped inner boss portion 195 which coaxially surrounds the transmission inlet shaft 123 and which, on its inner jacket wall, is non-rotatable on the tooth 121. It has internal teeth to be engaged so as to be slidable in the axial direction. The outer boss portion 197 that forms the leg of the clutch plate 117 and is fixedly connected to the clutch plate 117 has an inner tooth 199 on its inner peripheral surface that surrounds the boss portion 195.
Engages with the external teeth 201 of the boss portion 195, whereby the boss portion 197 and thus the clutch plate 117, the boss portion 195 and thus the transmission inlet shaft 123, and non-rotatable but circumferential play. Are linked together.

The boss portion 195 projects more than the boss portion 197 when viewed in the axial direction, and holds the boss plate 203 on the side farther from the crankshaft 107. Side plates 205, 2 are provided on both sides of the boss plate 203 in the axial direction.
07 is arranged and its both side plates are joined together in one fixed unit indicated by reference numeral 209. The side plate 205 is fixedly arranged on the boss portion 197. Window of boss plate 203
Windows 213, 215 of the 211 and side plates 205, 207 aligned with the window 211
A compression coil spring 217 is located inside, and the spring 217 is elastically loaded when the boss plate 203 and the side plates 205, 207 move relative to each other, and the clutch plate 117 rotates elastically with the transmission inlet shaft 123 via the boss portions 197, 195. Are linked together. Due to the play between the inner teeth 199 of the boss portion 197 and the outer teeth 201 of the boss portion 195,
The operation rotation angle of the vibration damper 134 for idling operation is limited. When this rotational play is compensated, the vibration damper 134 becomes inactive, and only the vibration damper 109 for load operation becomes effective.

The outer diameters of the boss plate 203 and the side plates 205 and 207 are designed to be smaller than the inner diameter of the plate member 143 in order to reduce the weight and moment of inertia of the clutch plate. Further, the idling vibration damper 134 may have an additional friction mechanism. In the case of a small friction torque, the friction between the side plates 205 and 207 and / or the boss plate 203 and / or the boss portions 195 and 197 is reduced. , The internal friction of the internal teeth 199 and the external teeth 201 is sufficient.

Inner teeth 141 of the plate member 135 are meshed with outer teeth of the bearing adding portion 149 that are open toward the baffle plate 101. This allows the vibration damper 109 for load operation to be manufactured separately and to be coupled to the dam 101 during assembly of the clutch. Similarly, the baffle plate 111, the clutch plate 117, and the pressure plate 113.
Then, the clutch casing 125 having the coupled diaphragm spring 129 can be preassembled and screwed to the plate member 143 when disassembled. By this means assembly is greatly facilitated.

[Brief description of drawings]

The drawings show a plurality of embodiments of the present invention.
FIG. 1 is a longitudinal sectional view showing an upper half of a friction clutch for an automobile having two flywheels rotationally and elastically connected to each other according to the first embodiment. FIG.
FIG. 3 is a partial cross-sectional view showing an angled position with respect to the drawing, and FIG. 3 shows an upper half of an automobile friction clutch having two rotary plates elastically connected to each other according to a second embodiment. FIG. 1,11,101,111… Bounce plate, 3,59,103,159… Screw, 5,105
… Rotation axis, 7,107… Crankshaft, 9,109… Rotation vibration damper, 13,113… Pressure plate, 15,115… Lining, 17,117… Clutch plate, 19… Boss member, 21,121,141… Teeth, 23,123…
Transmission inlet shaft, 25,125 ... Clutch casing, 27,127
… Support ribets, 29,129… Diaphragm springs, 31,131…
Protrusion, 33,133 ... Tongue, 35,37,43,135,137,143 ... Plate member, 39,139 ... Web, 41 ... Rivet, 45,47 ... Inclined ball bearing, 49,149 ... Bearing addition part, 51, 53, 55, 151, 153, 155, 211, 2
13,215 ... Window, 57,157,217 ... Compression coil spring, 61,63,161,
163 ... hole, 65,67,167 ... ring shoulder, 69,169 ... bearing flange, 71,171 ... spring ring, 73,81,173,181 ... friction mechanism, 75,175 ... friction ring, 77,87,177,187 ... pressing plate, 79,
91,191 ... Disc spring, 83,183 ... Control disc, 85,185 ... Control arm, 89,189 ... Tongue, 93,193 ... Starter tooth ring, 119 ... Boss, 1
25 ... clutch casing, 134 ... vibration damper for idling, 145 ... ball bearing, 168 ... spacer ring,
195,197… Boss part, 141,199… Internal teeth, 201,225… External teeth, 2
03 ... Boss plate, 205,207 ... Side plate, 209 ... Unit

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Bernhard Seering Kyuanatsuha Blumenwück 19 (56) References JP-A-55-20964 (JP, A)

Claims (11)

[Claims] 1. A friction clutch for an automobile, comprising: a) two baffle plates (1,11; 101,111) which are substantially ring-shaped.
The first baffle plate (1; 101) is formed so that the range of the inner peripheral surface thereof can be coupled to the crankshaft (7; 107) of the internal combustion engine, and the second baffle plate (11; 111) is formed. First baffle (1; 10
1) arranged coaxially alongside the first baffle plate (1; 1)
01) rotatable relative to a common rotation axis (5; 105), and b) a rotary vibration damper that connects both baffles (1,11; 101,111) to each other in a rotationally elastic manner. (9; 109), the rotary vibration damper (9; 109) being arranged between both baffles (1,11; 101,111) seen in the axial direction and being connected to each other,
Two outer ring-shaped plate members (3
5,37; 135,137), the outer plate member (35,3) when viewed in the axial direction.
7; 135,137) and the outer plate member (35,37; 1)
One plate member (43; 143) and a square plate member (35,37,43; 135,137,143) that can rotate relative to the other (35,137)
Are held in the windows (51, 53, 55; 151, 153, 155) of and are elastically loaded when the outer plate member (35, 37; 135, 137) and the inner plate member (43; 143) rotate relative to each other. The spring of (57; 15
7), and c) the second baffle plate (11; 111), first viewed in the axial direction.
The clutch casing (2) arranged on the opposite side of the baffle plate (1; 101) and connected to the second baffle plate (11; 111).
5; 125), and d) the second baffle plate (11; 111) seen first in the axial direction.
Has a pressure plate (13; 113) arranged on the opposite side of the baffle plate (1; 101) and non-rotatably connected to the second baffle plate (11; 111). E) a clutch plate arranged between the pressure plate (13; 113) and the second baffle plate (11; 111) as seen in the axial direction and provided with a clutch lining (15; 115) (17; 117), f) Clutch casing (25; 125) and pressure plate (13; 113)
And the clutch plate (17; 117) by engaging the pressure plate (13; 1).
13) has a clutch spring mechanism (29; 129) for tightening between the second baffle plate (11; 111) and both outer plate members (35,37; 135,137) have a first bounce. It is non-rotatably connected to the plate (1; 101) and the inner plate member (43; 143) is associated with the axis of rotation (5; 105) and the spring (57 of the rotary vibration damper (9; 109). The first baffle (1; 10
In the type rotatably supported by 1), the inner plate member (43; 143) is the first baffle plate (1; 101).
And a first baffle plate (1; 101) which is rotatably supported by a bearing addition portion (49; 149) which is formed separately from and is detachably coupled to the first baffle plate (1; 101). 101) and bearing add-on (49; 149) are aligned holes (61, 63; 161, 163) through which a common screw (3; 103) for fixing to the crankshaft (7; 107) passes. A friction clutch for an automobile, characterized by having: 2. The first baffle plate (1) has a bearing addition portion (4).
The friction clutch according to claim 1, further comprising a centering member for centering 9) relative to the first baffle plate (1). 3. The inner plate member (43; 143) is a bearing addition portion (4).
9; 149), the friction clutch according to claim 1 or 2, which is fixed in position in the axial direction. 4. The clutch casing (25; 125) and the second baffle plate (11; 111) are screwed together by a screw (59; 159) in the range of the outer peripheral surface of the inner plate member (43; 143). The friction clutch according to any one of claims 1 to 3, which is retained. 5. A plate member (35) axially adjacent to the first baffle plate (1) is riveted to the first baffle plate (1). The friction clutch according to claim 1. 6. The inner plate member (143) is first in the axial direction.
Is rotatably supported by a bearing addition portion (149) protruding from the baffle plate (101) toward the second baffle plate (111), and the bearing addition portion (149) has external teeth (225). And
At least one plate member (135) on the outer side has an inner tooth (14) on its inner peripheral surface that non-rotatably engages with the outer tooth (225) of the bearing addition portion.
The friction clutch according to any one of claims 1 to 5, which has 1). 7. An inner plate member (43; 143) has an inner peripheral surface provided with a bearing flange (69; 169) projecting in the axial direction and axially fixedly supported by the bearing addition portion (49,149). The friction clutch according to any one of claims 1 to 6, which comprises the friction clutch. 8. A rotary vibration damper (9; 109) is designed for load operation, and has a friction damper mechanism (73,81; 173,181) designed for load operation, The clutch plate (17; 117) holds the boss portion (195) and the clutch lining (115) and is rotatable relative to the boss portion (195) over a predetermined rotation angle. Part (1
95) and a ring plate-shaped plate member supported by
The plate member and the boss portion (195) are rotationally elastically connected to each other via a second vibration damper (134) designed for idling operation. The friction clutch according to claim 8. 9. The boss portion (195) has external teeth (201) on its outer peripheral surface, and the plate member of the clutch plate has internal teeth (19) on its inner peripheral surface.
9) holding a leg (197) with a tooth (19)
9) is non-rotatably connected to the boss portion (195) with play in the circumferential direction, and the vibration damper (134) for idling operation is connected to the boss portion (195) and the leg portion (197). A friction clutch according to claim 8 which is coupled. 10. A boss portion (195) is provided with a leg portion (19) in the axial direction.
7) projecting beyond and seeing the leg (19
The boss plate (203) is held on the side of 7), and the vibration damper (134) for idling operation is seen in the axial direction. One side plate of ring plate shape on each side of the boss plate (203). (2
05, 207), the two side plates being connected to one unit, and the one side plate (205) is a leg (197).
It is fixed to the boss plate (203) and side plates (205, 207).
A plurality of springs (217) of a vibration damper (134) for idling operation are arranged in each window (211, 213, 215) of
10. The friction clutch according to claim 9, wherein the spring (217) is elastically loaded when the boss portion (195) and the leg portion (197) rotate relative to each other. 11. A vibration damper (13) for idling operation.
The outer diameters of the side plates (205, 207) and the boss plate (203) of 4) are the plate members (14) inside the rotary vibration damper (109) for load operation.
Claim 10 which is smaller than the inner diameter of 3)
The friction clutch according to the item.