JPH09222151A - Torque transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To extend the durability and life of a bearing part by reducing a heat load based on the friction clutch operation of a ball bearing part provided between both inertial bodies in a torque transmission having a device for compensating for the torque fluctuation of an internal combustion engine having a flywheel divided into a first inertial body connected to the crankshaft of the internal combustion engine and a second inertial body connecting the input shaft of a transmission. SOLUTION: A cooling through-hole for guiding the flow of cooling air supplied from the friction surface side of a second inertial body 4 to a side opposite the friction surface side of he second inertial body 4 is provided in the second inertial body 4 between a friction surface 4a and a bearing part 15 in a radial direction and the through-hole produces the flow of cooling air along the surface of a surface side facing the second inertial body 4 of a damper device.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION The present invention relates to a rotational impact of an internal combustion engine,
In particular, a torque transmission device having a device for absorbing or compensating for torque fluctuations, the action of a damper device having a force-accumulation member arranged coaxially with each other via a bearing portion, particularly a rolling bearing portion, and acting in the circumferential direction Having at least two inertial bodies that are rotatable relative to each other, one of the two inertial bodies being coupled to the internal combustion engine and the other of the second inertial bodies being frictional. A friction surface that is coupled to the input portion of the transmission through the clutch and that cooperates with the clutch disc, and one inertial member of the inertial members is supported by the other inertial member through the bearing portion. Regarding the type of existing.

[0002]

2. Description of the Related Art In a torque transmission device of this type, it has already been proposed to provide a bearing portion directly between both inertial bodies. One of both races is non-rotatably connected to one inertial body, and the other of the inner and outer races is non-rotatably connected to the other inertial body. According to this type of torque transmission device, a very good cushioning action of the vibration generated between the internal combustion engine of the automobile and the power transmission system can be obtained. Nevertheless, this configuration of the torque transmission device is Due to the short service life of the bearings arranged between the inertial bodies, they have not yet been used in practice in automobile manufacturing. This bearing part is a weak point of such a torque transmission device, because the bearing part already fails relatively early due to unfavorable operating conditions.

[0003]

SUMMARY OF THE INVENTION The object of the present invention is to provide a torque transmission device of the type mentioned at the outset with improved function and higher service life, and in a particularly simple and An object is to provide a torque transmission device that can be manufactured economically.

[0004]

According to the invention, this object is already provided, for example, as a through hole for the assembly, a through hole for the axial passage of an assembly element or the like or an oil drain hole. In addition to the existing through-holes (the last through-hole as the oil drain hole is known in connection with plain bearings, for example from DE-OS 2926012), addition to said through-hole In the second inertial body in the area between the friction surface and the bearing in the radial direction,
A cooling through hole is provided which is emitted from the friction surface side and guides the cooling air flow to the side opposite to the friction surface side.
The solution is achieved by producing a cooling air flow which flows at least mainly along the surface wall of the damper device facing the second inertial body.

[0005]

The through hole allows the air flow to pass from one side of the second inertial body to the other side, thereby reducing the heat load on the bearing. Vents of this kind are required in many torque transmission devices of the type mentioned at the outset. Extensive research has shown that the thermal energy released during clutch operation causes an unacceptable heat load for the bearing life. Particularly when bearings with low bearing play are used, the expansion or contraction difference between the individual components due to the extremely rapid heating and cooling causes the bearing part to bite. The reason is that the air gap of the bearing is
This is because it disappears due to a large temperature difference between the individual bearing components. Furthermore, the measures according to the invention prevent overheating of the bearing lubricants such as oil, grease, etc., which ensures a satisfactory bearing lubrication and thus a long service life of the bearing part.

In particular, the ventilation slit itself extending in the circumferential direction is generally a belt pulley (FR-OS 25).
No. 49559) or a vibration damping damper in a flywheel (DE-OS 2903715). However, they do not protect rolling bearings from thermal overload by providing elongated openings in the structural parts that generate heat by friction. Structural parts which are exposed to large loads thermally and mechanically (due to the operation and disproportion of the friction clutch), in this case second
It is also suggested in FR-OS 2549559 that the cross-section is made smaller by forming an opening elongated in the circumferential direction in the inertial body of DE-OS 2.
It also does not exist in 903715.

According to an advantageous configuration, a web is formed between the through holes which reduces the amount of heat flowing from the friction surface to the bearing.

The through holes are formed so that the cooling air flow flows in from the clutch chamber and flows through the intermediate chamber which is open toward the outside between the two inertia bodies on the internal combustion engine side. Are particularly advantageous.

It is also advantageous in manufacturing, for example, to directly provide the through hole in the structural portion having the friction surface.

The through-holes, which prevent unacceptable heating of the bearing, can advantageously be elongated, in which case the through-holes can be arranged circumferentially. It is also advantageous to form these elongated through holes in a slit shape.

According to a particularly advantageous design of the through hole, the cross section of the through hole extends from the friction surface side of the inertial body to the opposite side. With such a configuration of the through-holes, the through-holes can be formed in the shape of a fan blade, so that these through-holes produce a forced air flow.

A particularly good protection of the rolling bearing against unacceptable heating is to place the through hole adjacent to the bearing part, ie to arrange the through hole in the radial direction near the outer circumference of the rolling bearing. Achieved by

In order to generate a forced air flow, according to another aspect of the invention, the through holes are constructed as follows. That is, the through hole is lower than the friction surface side of the second inertial body, extends over at least part of the radial extension of the friction surface, and extends outward. By configuring the through-hole in this way, the through-hole has a region forming a recess, which extends radially outward in the second inertial body, so that the through-hole has a radius. Directional ventilation or radial airflow can be produced. According to an advantageous configuration of the invention for this purpose, the through-holes, as viewed in radial cross-section, are constructed as follows. That is, the radial inner wall surface of the through hole extends at least approximately in the axial direction starting from the friction surface side of the second inertial body, and the radially outer wall surface radially extends toward the opposite side of the second inertial body. In the direction of the arrow, and extends, for example, in an arc shape outward in the radial direction.

According to an advantageous further development, the through-holes cover 20 to 70% of the angular circumference of the inertial body, particularly preferably at least approximately 50% of the circumference. . The through holes can be evenly distributed on the outer circumference and, in some cases, can be arranged on an imaginary circle of the same diameter.

According to a further advantageous refinement of the invention, the web left between two adjacent through-holes is
It has a circumferential length of 0.5 to 2.5 times the circumferential length of one through hole.

Reducing the amount of heat transferred from the friction surface to the bearing is not only obtained simply by the air flow generated by the through holes, but also by the web between the through holes. Due to the small cross section, it can also be obtained by forming a blocking or throttling part of the heat transfer path. Since the through hole is arranged relatively close to the periphery of the rolling bearing in the radial direction, most of the second inertial body having the friction surface has a radius of the through hole. It will be located outward in the direction or radially outside the inner area of the inertial body surrounding the bearing. Due to this radial distribution of the mass of the second inertial body over the diameter range in which the through holes or webs are provided, the heat generated during the clutch actuation process is It only slightly increases the temperature in the area radially outside the inner area surrounding the bearing. The inner area surrounding the bearing and the bearing are subjected to a very low heat load.

In particular, the damper device comprises an output part which consists of a force-accumulating member and / or a friction device or a sliding device acting in the circumferential direction and which is non-rotatably connected to the second inertia body by means of a rivet pin. In such a torque transmitting device, it is advantageous for the through holes to be arranged between the rivet pins when viewed in the circumferential direction. According to an advantageous configuration, the through-hole is provided at least approximately on a virtual circumference of the same diameter as the rivet pin, and the rivet pin is located between the two through-holes. It is fixed on the web range. In this case, two through holes can be arranged between the two rivet pins when viewed in the circumferential direction. Further, in this case, the web to which the rivet pin is fixed can have a larger circumferential length than the web without the rivet pin. It is also possible for the web with rivet pins to have a circumferential length which is at least approximately twice as long as the web without rivet pins.

According to the arrangement and configuration of the through hole according to the present invention, the air flowing in through the through hole on the friction surface side of the second inertial body is provided with the damper device of the second inertial body. Along the dorsal side, which cools the inertial body as well as the damper device.

According to the present invention, the torque transmitting device having the following structure, that is, the first inertial body has an axial direction addition portion, and the axial direction addition portion axially enters the center hole of the second inertial body. Can be particularly advantageously carried out in a torque transmission device having a structure in which a bearing portion having a rolling bearing is arranged between the axial addition portion and the central hole.

According to an advantageous embodiment of the invention, the through holes and the fixing screws for connecting the torque transmitting device to the internal combustion engine are arranged in different diameter ranges. According to a further advantageous refinement, the second inertial body lies radially outside the fixing screw. According to another advantageous design, the bearing part is arranged radially outside the notch for receiving the fixing screw.

According to a construction which is advantageous from the point of view of structural space, for example, the bearing part formed by the rolling bearing is the only centering / bearing part between the two inertial bodies. In this case, too, it is advantageous if the bearing inner ring is supported on the first inertial body.

It is generally advantageous for the friction surface, the through hole, the bearing part and the notch for the fixing screw to be arranged radially in this order from the outer side to the inner side.

According to a particularly advantageous construction for the service life of the torque transmission device of the present invention, a heat insulating portion is provided between the rolling bearing and the second inertial body.

The thermal insulation can also be provided between the bearing area of the second inertial body and the bearing.

In general, the thermal insulation can be formed by two rings of L-shaped cross section.

According to another advantageous design, one leg of the ring of L-shaped cross section axially covers one of the bearing races and the other leg of the ring is radial. It extends in the other direction of the bearing ring. In this case, it is advantageous if the legs of the ring of L-shaped cross section abut on one of the bearing races for sealing.

According to a further advantageous refinement, the legs of the ring of L-shaped cross section are spring loaded by means of a disc spring towards the bearing race, which disc spring is attached to the transmission input shaft. It is clamped between the second inertial body to be joined and the end region of the radial leg, respectively radially outside and inside.

One inertial body of both inertial bodies has an axial addition portion for axially penetrating into the central hole of the other inertial body, and a bearing portion is arranged and inserted between the addition portion and the hole. In the torque transmission device, it is advantageous to arrange the heat insulating portion between the central hole and the bearing portion.

From the standpoint of reducing structural parts in the torque transmission device of the present invention, it is advantageous for the thermal insulation to serve as the only packing for the bearing.

The invention further comprises at least two inertia bodies which are arranged coaxially to one another via rolling bearing parts and which are rotatable relative to one another against the action of the damper device. One first inertial body is connected to the internal combustion engine, the other second inertial body is connected to the input part of the transmission via a friction clutch and has a friction surface cooperating with the clutch disc, Further, in this case, a through hole for the cooling air flow that flows in from the clutch chamber and flows out on the internal combustion engine side is provided in the second inertial body in the range between the friction surface and the rolling bearing portion in the radial direction. And a heat insulating portion is provided between the rolling bearing portion and the second inertial body,
The present invention relates to a torque transmission device having a device for absorbing or compensating for a rotational shock of an internal combustion engine, especially a torque fluctuation.

In such a torque transmission device, it is advantageous to allow the cooling air flow to flow along the wall surface of the damper device.

[0032]

As can be seen from the drawings, a device 1 for absorbing or compensating for rotational shock of an internal combustion engine, in particular torque fluctuations of the internal combustion engine, comprises a flywheel 2 which comprises two inertial bodies 3. And 4 are divided. The inertial body 3 is fixed to a crankshaft 5 of an internal combustion engine (not shown) via fixing screws 6. A friction clutch 7 is attached to the inertial body 4 by means not shown. A clutch disc 9 is provided between the pressure plate 8 of the friction clutch 7 and the inertial body 4, and this is supported by an input shaft 10 of a transmission (not shown). The pressure plate 8 of the friction clutch 7 is spring-loaded toward the inertial body 4 by a disc spring 12 rotatably supported on the clutch cover 11 (switchable between a clutch engaged position and a clutch disengaged position). . By operating the friction clutch, the inertia body 4 and thus the flywheel 2 of the transmission input shaft 10 are connected and disconnected. Between the inertial body 3 and the inertial body 4 there is provided a damper mechanism in the form of a first damper device 13 and a second damper device 14 connected in series with it, said damper mechanism being an inertial body. Allows relative rotation of 3 and 4.

Both inertial bodies 3 and 4 are rotatably supported by bearings 15 relative to each other. Bearing part 15
Includes a rolling bearing 16 in the form of a single row ball bearing. The outer ring (outer ring ring) 17 of the rolling bearing 16 is a hole 18 of the inertial body 4.
An inner ring (inner race ring) 19 of the rolling bearing 16 has a central cylindrical shape that extends axially to the side opposite to the crankshaft 5 side of the inertial body 3 and penetrates into the hole 18. Is disposed on the pin-shaped portion 20 of the.

The inner ring 19 is press-fitted onto the pin-shaped portion 20 and is axially tightened between the pin-shaped portion 20 or the shoulder 21 of the inertial body 3 and the fixed disk 22. The fixed disk 22 is fixed to the end surface 20 a of the pin-shaped portion 20.

Between the outer ring 17 and the inertial body 4, there are provided rings 25 and 26 having an L-shaped cross section, and these rings are provided on the outer ring 17 from one side, respectively. The legs 25a, 26a of the rings 25, 26, which are L-shaped in cross section, and which face each other in the axial direction, surround the outer ring 17 and engage with it. A part of the leg portions 25b and 26b which are directed inward in the radial direction reaches the inner ring 19 in the radial direction and is axially supported by the inner ring. This allows the legs to simultaneously serve as a sealing member for the bearing 16. In order to ensure a satisfactory sealing of the bearing 16, the radially extending legs 25b, 26b are respectively provided with a force-storing member in the form of a disc spring 27, 28 on the inner ring 19.
Is axially spring loaded on the end face of the. The disc spring 27 is
It is supported radially outside on the shoulder of a disk 30 which is rigidly connected to the second inertial body 4 via a rivet pin 29 and on the inside radially in the end of the radial leg 25b of the ring 25. The range is spring loaded. Similarly, the disc spring 28 is supported radially outwardly on the shoulder of the inertial body 4 and radially inwardly on the radial leg 2 of the ring 26.
A spring load is applied to the end area of 6b.

The bore 18 of the inertial body 4 has a diameter larger than the outer diameter of the outer ring 17 for receiving the rings 25 and 26, which forms a radial intermediate space.

By proper selection of the material of the rings 25, 26, they can also serve as thermal insulation, at least reducing the heat transfer from the friction surface 4a cooperating with the clutch disc 9 to the bearing 16.

Since the bearing 16 is axially tightened between the shoulder 31 of the inertial body 4 and the disk 30 by inserting the rings 25 and 26, the bearing 16 is fixed to the inertial body 4 in the axial direction. Has been done.

The damper device 13 has two disks 30, 33 arranged on both sides of a flange 32, which are non-rotatably connected to each other via a retaining rivet pin 29 at an axial distance. There is. Preliminary rivet pin 29
Also serves to fix both disks 30, 33 to the inertial body 4. Disks 30, 33 and flange 32
A notch 34 is provided in the recess, in which a force-storing member in the form of a coil spring is received. These force accumulating members 34 act in the opposite direction against the relative rotation between the flange 32 and the disks 30 and 33.

The damper device 13 further comprises a friction device 13a which acts over a possible pivoting angle between the inertia bodies 3,4. The friction device 13a is arranged axially between the disc 30 and the inertial body 3 and is stored by a disc spring which is held tightly between the disc 30 and the pressure ring 36. Member 3
5 by means of which the friction ring 37 arranged between the pressure ring 36 and the inertial body 3 is tightened.
The force acting on the disk 30 by the disc spring 35 is the bearing 16
Be absorbed through.

The flange 32 forms the output part of the damper device 14 on the one hand and the damper device 1 on the other hand.
4 forming the output part. The input portion of the damper device 14 is composed of two discs 3 which are axially spaced from each other.
8 and 39, which are not rotatable with respect to the inertial body 3. The ring-shaped disc 39 is attached to the inertial body 3 by rivets 40. Disk 3
8 has axially formed tabs 38a integrally formed on the outer periphery, which are engaged in the notches 41 of the disc 39 to prevent the disc 38 from rotating with respect to the disc 39. A radial arm 42 of the flange 32 is fastened between the disks 38, 39 when viewed axially.
For this purpose, the disks 38, 39 are clamped together by means of a disc spring 43. For this purpose, the disc spring 43 is supported on the one hand by the inertial body 3, and on the other hand by the disc 3
8 is given a spring load toward the disk 39.

The inertial member 4 is the rolling bearing 1 when viewed in the radial direction.
An axial through hole 45 is provided between the hole 18 for receiving 6 and the friction surface 4a of the inertial body 4, and the through hole is
Friction surface 4a of inertial body 4 cooperating with clutch disc 9
To reduce the amount of heat transfer from the bearing 16 to the bearing 16. As can be seen from FIG. 2, the through holes 45 are elongated or slit-shaped when viewed in the circumferential direction, and are arranged on a virtual circle having the same diameter. Furthermore, the through hole 45 is arranged adjacent to the bearing 16, i.e. in the radial direction, very close to the bearing 15. The through hole 45 is the friction surface 4a of the inertial body 4.
From the side, as seen in cross section, it is axially expanded towards the surface 47 on the damper device 13, 14 side (FIG. 1).
In this case, the through hole 45 is configured as follows. That is, as viewed in the radial cross-sectional view, the radially inner wall surface 48 extends at least substantially in the axial direction, and the radially outer wall surface 49 extends radially outward in an arc shape in the direction toward the surface 47 of the inertial body 4. As a result, the through hole 45 is radially outward on the surface 47 of the inertial body 4 on the side opposite to the friction surface 4a via a part of the range X extending in the radial direction of the friction surface 4a. Has fallen to (Fig. 1). With such a configuration of the through hole 45, the through hole 45 acts like a fan blade, and as a result, the air flowing into the through hole 45 from the friction surface 4a side passes through the through hole 45 and the inertial body is passed through. 4 along the back surface 47, thereby cooling this inertial body. Furthermore, this forced air circulation also cools the components of the damper device. This is because the air also flows along the discs 33 and 39, and some of the air flow can escape, for example, through the flange 32 for the energy storage member and the notches in the discs 33, 30. .

As can be seen from FIG. 2, two through holes 45 are provided between the two rivet pins 29 as seen in the circumferential direction.
In this case, the through hole 45 and the rivet pin 29 are located at least approximately on an imaginary circle having the same diameter 50. Through hole 45, web 51,
52 is formed and the heat generated by the friction surface 4 a must pass through the webs 51, 52 in order to reach the inner region 53 of the inertial body 4 which surrounds the rolling bearing 16 and is closed. In the illustrated embodiment, the web 52 through which the rivet pin 29 passes has the rivet pin 2 as seen in the circumferential direction.
It is longer than the web 51, which 9 is not threaded (Fig. 2). In the illustrated embodiment, the circumferential length of the web 52 is at least approximately twice the circumferential length of the web 51. The through hole 45 is
In the circumferential direction, it is constructed to be somewhat longer than the shortest range of the web 51, but shorter than the shortest range of the web 52. As can be further seen in FIG. 2, the through holes 45 extend over at least approximately 50% of the imaginary circle of the diameter 50 of the inertial body 4.

When the generated load is small, a through hole between the two rivet pins 29 is shown in FIG.
As shown at 4, by removing one web 51 between the two through holes 45 and connecting both through holes,
It can be made longer in the circumferential direction.

The reduction of the amount of heat transferred from the friction surface 4a to the bearing 16 is not only caused by the air flow generated by the through holes 45, but also the remaining webs 51, 52 are cross-sectioned in their cross section. It can also be obtained by forming a blocking portion or a throttle portion for the heat transfer flow due to the small value. Through holes 45 or webs 51, 5
On the basis of the radial mass distribution of the inertial body 4 with respect to the diameter range in which the two are provided, the amount of heat generated in the clutch is essentially the inner range 53 of the inertial body 4 surrounding the bearing 16.
Slightly raises the temperature of the inertial body 4 in the radially outer region of the above, but the above-mentioned inner region 53 and thus also the bearing 16 are exposed to significantly lesser temperature. By providing the through holes 45, the effect that the inertial body 4 only causes a slightly higher temperature only in the range radially outside the through holes 45 is obtained.
This is due to the fact that the bulk of the material of the inertial body 4 or the mass of this inertial body lies radially outside these through-holes 45.

Still another effect of the illustrated construction is that the rivet pin fixed to the web 52 acting as a blocking portion or a narrowing portion of the heat conduction path transfers a part of heat to the disks 30, 33.
The result is that the heat exchange surface with the air flow produced by the through holes is increased.

Provided by, for example, the bearing manufacturer,
When a bearing with a seal ring is used, in many applications, the rings 16 and 25 are omitted, and the bearing outer ring 17 is directly fitted into the hole 18 adapted to the outer ring outer periphery, so that the bearing 16 is fitted. It is possible to attach it to the inertial body 4 in advance.

[Brief description of drawings]

FIG. 1 is a sectional view of an embodiment of a torque transmission device of the present invention.

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

[Explanation of symbols]

1 device for absorbing or compensating for rotational impact of internal combustion engine, especially torque fluctuation, 2 flywheel, 3, 4 inertial body, 4a friction surface, 5 crankshaft, 6 fixing screw, 7 friction clutch, 8 pressure plate,
9 clutch disc, 10 transmission input shaft, 1
DESCRIPTION OF SYMBOLS 1 clutch cover, 12 disc spring, 13 1st damper device, 13a friction device, 14 2nd damper device, 15 bearing part, 16 rolling bearing, 17
Outer ring, 18 holes, 19 inner ring, 20 pin-shaped parts,
20a end face, 21 shoulder, 22 fixed disc,
25 ring, 25a, 25b leg portion, 26 ring, 26a, 26b leg portion, 27 disc spring, 2
8 Belleville springs, 29 rivet pins, 30 discs,
31 shoulders, 32 flanges, 33 discs,
34 notches, 35 accumulating member (disc spring), 36
Pressure ring, 37 friction ring, 38 disc,
39 discs, 40 rivets, 41 notches,
42 arm, 43 disc spring, 45 through hole,
47 surfaces (rear surface), 48 wall surfaces, 49 wall surfaces, 50
Diameter, 51 web, 52 web, 53 inner range

Claims (35)

[Claims] 1. A torque transmission device having a device for absorbing or compensating for rotational shock, especially torque fluctuation, of an internal combustion engine, the torque transmission devices being arranged coaxially with each other via a bearing part, in particular a rolling bearing part, and in the circumferential direction. It has at least two inertial bodies which are rotatable relative to one another against the action of a damper device with an acting force-storing member, one first inertial body of the two inertial bodies being connected to the internal combustion engine. And the other second inertial body has a friction surface which is coupled to the input part of the transmission via a friction clutch and cooperates with the clutch disc, and one inertial body of the inertial bodies is a bearing part. Is supported by the other inertial body through the second inertial body in the range between the frictional surface and the bearing portion in the radial direction, and is emitted from the frictional surface side and is opposite to the frictional surface side. There is a through hole for cooling that guides the cooling air flow to the side The through hole produces a cooling flow at least mainly flowing along a surface of the damper device facing the second inertial body.
A torque transmission device having a device for absorbing or compensating for a rotational shock of an internal combustion engine, particularly a torque fluctuation. 2. The torque transmission device according to claim 1, wherein a web that reduces the amount of heat flowing from the friction surface to the bearing is provided between the through holes. 3. The through hole is such that the cooling air flow flows from the clutch chamber and flows through an intermediate chamber on the internal combustion engine side of the second inertial body, which is open toward the outside between the inertial bodies. The torque transmission device according to claim 1, wherein the torque transmission device is formed in 4. The through hole is provided directly in the structural part having the friction surface, and the through hole is provided.
The torque transmission device according to any one of items 1 to 7. 5. The torque transmission device according to claim 1, wherein the through hole is elongated in the circumferential direction. 6. The torque transmission according to claim 1, wherein a cross section of the through hole extends from the friction surface side of the inertial body toward the opposite side. apparatus. 7. The torque transmission device according to claim 1, wherein the through hole is formed in a fan blade shape. 8. The torque transmission device according to claim 1, wherein the through hole is adjacent to the bearing portion. 9. A through hole is provided on the side of the second inertial body opposite to the friction surface over at least a part of a portion extending in a radial direction of the friction surface, and At a position that is lower in the axial direction than the plane of the surface opposite to the friction surface of the inertial body,
The torque transmission device according to claim 1, wherein the torque transmission device extends radially outward. 10. The through hole is configured as follows in a radial sectional view, that is, the wall surface on the radial inner side of the through hole emanating from the surface on the friction surface side of the second inertial body. Any of claims 1 to 9 in which at least approximately extends axially and the radially outer wall surface descends radially outward in a direction towards the opposite surface of the second inertial body. The torque transmission device according to item 1. 11. The torque transmission device according to claim 1, wherein the through holes are evenly distributed in the circumferential direction. 12. The torque transmission device according to claim 1, wherein the through holes are arranged on a virtual circle having the same diameter. 13. The through hole has a total center angle range of 20 for the inertial body.
Torque transmission device according to any one of the preceding claims, wherein the torque transmission device ranges from ~ 70%. 14. The web provided between two adjacent through holes has a circumferential length of one through hole of 0.5 to 2.5.
The torque transmission device according to any one of claims 1 to 13, which has a double circumferential length. 15. A damper device comprising a force-accumulating member and / or a friction or sliding member acting in the circumferential direction and having an output part, said output part being provided by a rivet pin to the second inertial body. The torque transmission device according to any one of claims 1 to 14, wherein the torque transmission device is non-rotatable and the through hole is arranged between the rivet pins when viewed in the circumferential direction. 16. The torque transmission device according to claim 15, wherein the through hole and the rivet pin are provided on a virtual circle having at least substantially the same diameter. 17. The two through holes are respectively provided between the two rivet pins when viewed in the circumferential direction.
The torque transmission device according to 5 or 16. 18. The web, having rivet pins, present between the two through holes has a greater circumferential length than the web without rivet pins. The torque transmission device according to any one of 15 to 17. 19. A web according to claim 15, wherein the web with rivet pins has a circumferential length which is at least approximately twice the length in the circumferential direction of a web without rivet pins. The described torque transmission device. 20. The method according to claim 1, wherein the through hole and the fixing screw for connecting the torque transmission device to the internal combustion engine are arranged in different diameter ranges. The torque transmission device according to the item. 21. The torque transmission device according to claim 1, wherein the second inertial body is located radially outside the fixing screw. 22. The torque transmission device according to claim 1, wherein the bearing portion is arranged radially outside of the notch for receiving the fixing screw. 23. The torque transmission device according to claim 1, wherein the bearing portion formed by the rolling bearing is the only centering / bearing portion for both inertial bodies. 24. The torque transmission device as claimed in claim 1, wherein the bearing inner ring is supported on the first inertial body. 25. The friction surface, the through hole, the bearing portion, and the notch for the fixing screw are sequentially arranged in this order from the outer side to the inner side in the radial direction.
4. The torque transmission device according to any one of 4 to 4. 26. The torque transmission device according to claim 1, further comprising a heat insulating portion provided between the rolling bearing and the second inertial body. 27. A heat insulating portion is provided between the bearing range of the second inertial body and the bearing.
The torque transmission device according to any one of claims 26 to 26. 28. The insulation according to claim 26, characterized in that it is formed by two rings of L-shaped cross section.
Alternatively, the torque transmission device described in 27. 29. One leg of a ring of L-shaped cross section axially covers one of the bearing races and the other leg extends radially in the other direction of the bearing race. ,
The torque transmission device according to claim 19. 30. The torque transmitting device according to claim 20, wherein the leg portion of the ring having the L-shaped cross section abuts against one of the bearing races to seal the same. 31. The leg portion of the ring having an L-shaped cross section is spring-loaded toward the bearing ring by a disc spring,
21. The disc spring is clamped radially outward and inward between a second inertial body coupled to the transmission input shaft and an end region of the radial leg, respectively. 21. The torque transmission device as described in 21. 32. An inertial addition part for allowing one inertial member of both inertial members to penetrate axially into a central hole of the other inertial member,
The torque transmission according to any one of claims 1 to 22, wherein a bearing portion is arranged between the additional portion and the hole, and a heat insulating portion is arranged between the central hole and the bearing portion. apparatus. 33. The torque transmitting device according to claim 1, wherein the heat insulating part serves as the only packing for the bearing part. 34. A torque transmission device having a device for absorbing or compensating for a rotational shock of an internal combustion engine, in particular, a torque fluctuation, which is arranged coaxially with each other via a rolling bearing part and resists the action of a damper device. A first inertial body of the two inertial bodies is coupled to the internal combustion engine and a second inertial body of the other inertial body is rotatable relative to each other.
Of the type in which the inertial body is connected to the input part of the transmission via a friction clutch and has a friction surface cooperating with the clutch disc, in a radial direction between the friction surface and the rolling bearing part. In the second inertial body in the range,
A through hole for cooling air flow that flows in from the clutch chamber and flows out on the internal combustion engine side is provided, and the rolling bearing portion and the second
A torque transmission device having a device for absorbing or compensating for a rotational shock of an internal combustion engine, in particular, a torque fluctuation, characterized in that a heat insulating part is provided between the inertial body and the inertial body. 35. The torque transmission device according to claim 34, wherein the cooling air flow flows along the wall surface of the damper device.