JPH0718471B2 - Torque transmission device - Google Patents

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 at least two inertias being arranged coaxially to one another via a rolling bearing part and being rotatable with respect to the action of a damper device. A first inertial body of one of the two inertial bodies is coupled to the internal combustion engine, and the other second inertial body is coupled to the input portion of the transmission via a friction clutch, and The second inertial body has a friction surface that cooperates with the clutch disc.

[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]

SUMMARY OF THE INVENTION According to the invention, the object is a torque transmission device having a device for absorbing or compensating for the rotational shock of an internal combustion engine, in particular the torque fluctuations, which are mutually connected via rolling bearing parts. It has at least two inertial bodies which are arranged coaxially and which are rotatable relative to each other against the action of the damper device, the first inertial body of one of the two inertial bodies being connected to the internal combustion engine. , The other second inertial body is coupled to the input part of the transmission via a friction clutch, and said second inertial body has a friction surface cooperating with a clutch disc, and in the radial direction said The outer side formed between the inertial bodies on the internal combustion engine side of the second inertial body by flowing from the clutch chamber into the second inertial body in the range between the friction surface and the rolling bearing portion. Open the middle room towards Heat insulating portion is resolved by being provided between the inlet opening is provided in the eyeholes for cooling air flow through I, and a rolling bearing unit and the second inertial body.

[0005]

The through holes allow 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. This is because the bearing voids disappear due to the large temperature differences that occur between the individual bearing components.

In particular, according to the present invention, the through hole or the passage can be formed arbitrarily. In short, the through hole or the passage does not necessarily have to be elongated in the circumferential direction. Further, according to the present invention, the heat insulating portion is provided between the rolling bearing portion and the second inertial body for cooling. Due to such a combination of the cooling means and the adiabatic part, the rolling bearing arranged between the two inertial bodies can be well protected from overheating and furthermore the second inertial body can be cooled.

It was possible to significantly reduce the temperature of the ball bearing by providing an insulating cap made of plastic between the ball bearing and the second inertial body, but the resulting reduction in temperature is To achieve a sufficient service life of the lubricating oil in the bearing and at the same time keep the temperature of both the inner and outer rings of the bearing below the critical value, in other words keep it low to prevent negative effects on the strength of the rolling element raceways. And it wasn't enough in all cases. Therefore, in the present invention, the passage or the through hole for the cooling air flow is arranged immediately outside the outer circumference of the bearing.

The through hole or passage starts from the friction surface of the second inertial body and first extends axially toward the side plate of the torsion damper and then curves radially outward in an arc. The air flowing from the relatively cool clutch chamber through the through hole or passage thus scrapes against the back side of the second inertia body, thereby cooling the second inertia body itself and, on the other hand, on the other hand. At the same time, the damper part and the torsion spring in the damper are cooled.

Even in such a structure, it is possible to form the through hole or the passage in the circumferential direction so that the flow of heat from the friction surface to the ball bearing can be prevented or restricted. is there.

In the starting test in Yamano, the peak of the temperature rise from the outer circumference in the radial direction of the through hole or passage to the inner circumference in the radial direction or the range of the ball bearing remained at 80 ° C. With no flywheel inertia, the temperature in the bearing range reached a high temperature almost equal to the lining friction surface of the second inertia.

It is advantageous to form the through hole in the shape of a slit that is long in the circumferential direction.

According to a particularly advantageous construction of the through-hole, the through-hole has a slit-like design on its friction surface side, and
The through hole cross section is expanded towards the opposite side of the inertial body. With such a configuration of the through-holes, the through-holes are configured like fan blades, so that these through-holes can force an 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 produce 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.

The reduction of the amount of heat transferred from the friction surface to the bearing is not only obtained 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 comprises 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 inertial 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 configuration, that is, the first inertial body has an axial direction addition portion, and the axial direction addition portion axially moves into 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.

[0021]

DESCRIPTION OF THE PREFERRED EMBODIMENTS As can be seen from the drawings, the rotational impact of an internal combustion engine,
In particular, the device 1 for absorbing or compensating for torque fluctuations of an internal combustion engine has a flywheel 2, which is divided into two inertia bodies 3 and 4. The inertial body 3 is fixed to a crankshaft 5 of an internal combustion engine (not shown) via fixing bolts 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. The first damper device 1 is provided between the inertial body 3 and the inertial body 4.
3 and a second damper device 14 connected in series to this
A damper mechanism of the form is provided, which allows the inertial bodies 3 and 4 to rotate relative to each other.

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 the 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 region 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 the proper selection of the material of the rings 25, 26, they can also serve as an 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 discs 30, 33 arranged on both sides of a flange 32, which are connected to each other via a retaining rivet pin 29 at an axial distance so that they cannot rotate. 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 inertia body 4 is a 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 approximately in the axial direction, and the radially outer wall surface 49 extends radially outward in a circular 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 blower 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 becomes an inertial body. 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 disks 33 and 39, and part of the air flow can escape, for example, through the flange 32 for the energy storage member and the notches in the disks 33, 30. .

As can be seen from FIG. 2, two through holes 45 are provided between the two rivet pins 29 as viewed 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, the 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 in 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 advantage 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 conducting path transfers a part of the 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 a device for absorbing or compensating the rotational impact of an internal combustion engine, especially torque fluctuation, 2 flywheel, 3, 4 inertial body, 4a friction surface, 5 crankshaft, 6 fixing bolts, 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 arms, 43 disc springs, 45 through holes, 4
7 surfaces (rear surface), 48 wall surfaces, 49 wall surfaces, 50
Diameter, 51 web, 52 web, 53 inner range

─────────────────────────────────────────────────── ─── Continuation of the front page (51) Int.Cl. ⁶ Identification code Internal reference number FI Technical display location F16F 15/30 9030-3J F16F 15/12 N 9030-3J B 9030-3J 15/30 S (56 ) References: Actual development Sho 59-113548 (JP, U) Actual development Sho 60-191746 (JP, U) Actual public Sho 59-10420 (JP, Y2)

Claims (26)

[Claims] 1. 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, wherein the torque transmission devices are arranged coaxially with each other via a rolling bearing portion and resist the action of a damper device. 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 via a friction clutch. Is coupled to the input part of the transmission and the second inertial body has a friction surface cooperating with the clutch disc, and in the radial direction the friction surface (4a) and the rolling bearing portion (15). An intermediate portion which flows into the second inertial body in the range between the two and is opened toward the outside formed between the inertial bodies on the internal combustion engine side of the second inertial body. Cooling air flow through the chamber A through hole (45) for the inlet, and a heat insulating part is provided between the rolling bearing part (15) and the second inertia body (4). Torque transmission device. 2. The torque transmission device according to claim 1, wherein the through hole penetrates the inertial body in the axial direction. 3. The torque transmission device according to claim 1, wherein the cooling air flow flows along the wall surface of the damper device. 4. The torque transmission device according to claim 1, wherein the through hole (45) is formed elongated in the circumferential direction. 5. The through hole (45) is formed in a slit shape on the friction surface side, and the cross section of the through hole is on the side of the second inertial body opposite to the friction surface side. The torque transmission device according to claim 1, wherein the torque transmission device is expanded toward the front. 6. Torque transmission device according to claim 1, wherein the through holes (45) are fan-shaped. 7. The through hole (45) has a rolling bearing portion (15).
The torque transmission device according to any one of claims 1 to 6, which is adjacent to. 8. The through hole (45) has a second inertial body (4).
On the side (47) opposite to the friction surface (4a), over the range (X) of at least a part of the portion extending in the radial direction of the friction surface (4a), the inertial body ( The torque transmission device according to any one of claims 1 to 7, which extends radially outward at a position axially lower than a plane of a surface opposite to the friction surface (4a) of 4). 9. The through hole (45), as viewed in a radial cross-section, is constructed as follows: from the surface (46) of the second inertial body (4) on the friction surface side. Through hole (4
The radially inner wall surface (48) of 5) extends at least approximately in the axial direction, and the radially outer wall surface (49).
Is descending radially outward in a direction towards the opposite surface (47) of the second inertial body (4). 10. Torque transmission device according to claim 1, wherein the through holes (45) are evenly distributed in the circumferential direction. 11. Torque transmission device according to claim 1, wherein the through holes (45) are arranged on an imaginary circle having the same diameter (50). 12. Torque transmission device according to claim 1, wherein the through hole (45) covers 20 to 70% of the total central angle range of the inertial body. 13. A web (51, 52) provided between two adjacent through holes (45) has one through hole (4).
13. The torque transmission device according to claim 1, which has a circumferential length 0.5 to 2.5 times the circumferential length 5). 14. 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. Non-rotatable and through hole (4
14. The torque transmission device according to claim 1, wherein 5) is arranged between the rivet pins (29) in the circumferential direction. 15. A through hole (45) and a rivet pin (2).
15. Torque transmission device according to claim 14, characterized in that 9) are provided on a virtual circumference of at least approximately the same diameter (50). 16. Two rivet pins when viewed in the circumferential direction
16. Torque transmission device according to claim 14 or 15, wherein two through holes (45) are provided between each (29). 17. A web (52) having a rivet pin (29) lying between two through holes (45).
Web (5) without rivet pins (29)
15. Having a circumferential length greater than 1).
17. The torque transmission device according to any one of 1 to 16. 18. The circumferential length of the web (52) with rivet pins (29) is at least approximately twice the circumferential length of the web (51) without rivet pins (29). The torque transmission device according to any one of claims 14 to 17. 19. The rolling bearing portion (1) from the friction surface (4a).
Means for reducing at least the amount of heat flowing to (5) (25,
26) is provided as a heat insulating part arranged between the friction surface (4a) and the rolling bearing part (15), the heat insulating part being at least one ring (25, L-shaped in cross section).
26) A torque transmission device according to any one of claims 1 to 18 formed by 26). 20. Rings (25, 26) of L-shaped cross section
One leg (25a, 26a) axially covers one (17) of the bearing races and the other leg (25)
20. Torque transmission device according to claim 19, wherein b, 26b) extends in the radial direction towards the other (19) of the bearing races. 21. A ring leg (25) of L-shaped cross section.
21. Torque transmission device according to claim 20, characterized in that b, 26b) abut and seal one of the bearing races. 22. L-shaped cross-section ring leg (25)
b, 26b) is spring loaded towards the bearing race by means of a disc spring (27, 28), the disc spring being connected to the transmission input shaft (10) by a second inertial body (4). 22. The torque transmission device according to claim 20 or 21, wherein the torque transmission device is tightened between the end region of the radial leg and the radial outer side and the inner side, respectively. 23. An axial addition portion for allowing one inertial body of both inertial bodies to penetrate axially into a central hole of the other inertial body,
A bearing portion is arranged between the additional portion and the hole, and the heat insulating portion (25, 26) is provided in the central hole (18) and the bearing portion (15).
The torque transmission device according to any one of claims 1 to 22, which is disposed between and. 24. The heat insulating part (25, 26) is a bearing part (1).
Torque transmission device according to any one of claims 1 to 23, which serves as the sole packing for 5). 25. A torque transmission device having a flywheel for an internal combustion engine, wherein the flywheel is rotatable via a rolling bearing part and against the action of a damper device, also the internal combustion engine. Is divided into a first inertial body that is fixedly connected to the driven shaft of the second inertial body and a second inertial body that has a friction surface that acts on the clutch disc, and the second inertial body.
In the type in which a friction clutch that connects and disconnects the clutch disc and the transmission is arranged on the transmission side of the inertial body of the above, the rolling bearing portion (15) from the friction surface (4a)
Means for reducing at least the amount of heat flowing to (25, 2
6) is provided as a heat insulating part arranged between the friction surface (4a) and the rolling bearing part (15), the heat insulating part being at least one ring (25, 2) having an L-shaped cross section.
6), the ring axially covers one (17) of the bearing inner and outer rings with one of its legs (25a, 26a) and the other leg (25b, 26b).
Extends radially towards the other (19) of the inner and outer bearing rings, abuts against and seals against this bearing race, and is axially loaded by the disc springs (27, 28) towards this bearing race. And the disc spring between the second inertial body (4) coupled to the input portion (10) of the transmission and the end of the radial leg, radially outside and inside, respectively,
An axial through hole (45) for cooling air flow is provided in the second inertia body, which is tightened and radially between the friction surface (4a) and the rolling bearing part (15). The torque transmission device is characterized in that. 26. A damper device wall surface is formed by passing through a middle chamber open to the outside between the first and second inertial bodies on the internal combustion engine side of the second inertial body flowing in from the clutch chamber. 26. Torque transmission device according to claim 25, wherein a circumferentially elongated through hole (45) is provided for the cooling air flow flowing therethrough.