JPH0697060B2 - Torque transmission device - Google Patents

Description

Description: BACKGROUND OF THE INVENTION 1. Field of the Invention 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, in particular, a torque fluctuation, which is coaxial with each other via a rolling bearing portion. And at least two inertia bodies which are arranged relative to each other and which are rotatable relative to the action of the damper device, one of the two inertia bodies being connected to the internal combustion engine and the other Second inertial body is coupled to the input portion of the transmission through a friction clutch, and the second inertial body has a friction surface for cooperating with a clutch disc.

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, and if a rolling bearing is used for the bearing portion, both inner and outer raceways are provided. One of the wheels is non-rotatably connected to one inertial body,
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.

The problem to be solved by the invention is that the torque transmission device of the type mentioned at the outset has an improved function and a long service life, and is particularly simple and economical. It is to provide a torque transmission device that can be manufactured.

Means for Solving the Problems According to the present invention, this problem 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 fluctuation, which is coaxial with each other via a rolling bearing portion. And at least two inertia bodies which are arranged relative to each other and are rotatable relative to the action of the damper device, one of the two inertia bodies being coupled to the internal combustion engine,
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 for cooperating with a clutch disc. The second inertial body is formed between the two inertial bodies on the internal combustion engine side of the second inertial body by flowing in from the clutch chamber into a radial range between the friction surface and the rolling bearing portion. By providing a circumferentially elongated through-hole inlet opening for the cooling air flow flowing through the outwardly open intermediate chamber (claim 1) or the second inertia An axial through hole extending toward the first inertial body side flows into the radial range between the friction surface and the rolling bearing portion in the body from the clutch chamber, and the second inertial hole is introduced. It is formed between the above inertial bodies on the internal combustion engine side of the body. , For cooling air flow flowing along the wall surface of the damper device through the intermediate chamber that is open towards the outside, by provided (claim 2
1) Or, a means for reducing at least the amount of heat flowing from the friction surface to the rolling bearing portion is provided as a heat insulating portion arranged between the friction surface and the rolling bearing portion, and the heat insulating portion is at least one, It is formed by a ring with an L-shaped cross section, which axially covers one of the bearing inner and outer rings on one of its legs and the other leg is radially directed towards the other of the bearing inner and outer rings. A second spring which extends in the direction of the bearing ring and seals against the bearing ring and is axially loaded by a disc spring in the direction of the bearing ring and which is connected to the input part of the transmission. Between the inertial body and the ends of the radial legs of the L-shaped ring, radially outward and inward, respectively, and second
Is solved by the provision of axial through-holes for the cooling air flow in the radial extent in the inertial body between the friction surface and the rolling bearing (claim 28). .

Functions / Effects These 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 of 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. Furthermore, the measures of the invention avoid excessive heating of the bearing lubricants, such as oil, grease, etc., which guarantees always satisfactory bearing lubrication and thus also a long service life of the bearing parts.

According to the first aspect of the present invention, the through hole elongated in the circumferential direction can be easily manufactured by a casting technique, and in addition to guiding the cooling air flow, the friction surface can be transferred to the rolling bearing portion. It also helps to block heat flow. This amount of heat flowing from the friction surface to the rolling bearing is further reduced by the fact that the portion (web) left between the through holes is abruptly contracted and acts on the heat flow like a throttle. Decrease.

According to the through hole extending toward the first inertial body side in the second invention described in claim 21, it is possible to smoothly change the direction of the cooling air flow. Due to such a gentle turning of the cooling air flow from at least approximately axially to at least approximately radial, the generation of swirls, and thus also the flow losses, is reduced, which increases the cooling capacity of the cooling air flow and the rolling bearing parts. The temperature can be further reduced.
Furthermore, this cooling air stream also effectively cools the damper device. Further, the through-hole having the expanding shape can be easily manufactured at least by a casting technique.

The third aspect of the present invention according to claim 28 includes a heat insulating portion as yet another means for reducing the temperature of the rolling bearing portion. Such an adiabatic part virtually completely blocks the flow of heat from the friction surface to the rolling bearing part, i.e. over the entire circumference.

EXAMPLE According to a particularly advantageous embodiment of the through-hole, the through-hole is designed in the form of a slit on its friction surface side, and the through-hole cross section expands towards the opposite side of the inertial body. Has been done.
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 achieved by arranging the through hole adjacent to the bearing part, i.e. by arranging the through hole in radial view near the outer circumference of the rolling bearing. It

In order to produce a forced air flow, according to an advantageous embodiment 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 embodiment of the invention for this purpose, the through-holes, 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 a further preferred embodiment, 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 embodiment of the invention, the web left between two adjacent through-holes has a circumferential direction of 0.5 to 2.5 times the circumferential length of one through-hole. Have a length.

Reducing the amount of heat transferred from the friction surface to the bearing is
Not only is it obtained by the air flow created by the through holes, but also the web between the through holes has a small cross-section, so that the blocking or throttling part of the heat transfer path is blocked. It can also be obtained by forming. 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 outward of 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 a force-applying member acting in the circumferential direction and / or a friction device or a sliding device and has an output part which is non-rotatably connected to the second inertia body by means of a rivet pin. In the transmission device, it is advantageous if the through holes are arranged between the rivet pins when viewed in the circumferential direction. In this case, according to an advantageous embodiment, the through-holes are provided at least approximately on an imaginary circle of the same diameter as the rivet pin, and the rivet pin is between the two through-holes. The range of the web has been fixed. 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. Also,
It is also possible for the web with rivet pins to have a circumferential length that is at least approximately twice that of the web without rivet pins.

According to the arrangement and configuration of the through hole according to the invention, the second
The air flowing in through the through hole on the friction surface side of the inertial body of the second inertial body flows along the back side of the second inertial body where the damper device is provided, thereby cooling the inertial body and the damper device. It

The present invention provides a torque transmission device having the following configuration, that is, the first inertial body has an axial addition portion, and the axial addition portion penetrates into the central hole of the second inertial body in the axial direction. In particular, it can be particularly advantageously implemented in a torque transmission device having a structure in which a bearing part having a rolling bearing is arranged between the axial addition part and the central hole.

The invention will now be described with reference to the illustrated embodiment.

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 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 is supported by an input shaft 10 of a transmission (not shown). The pressure plate 8 of the friction clutch 7 has a clutch cover 11
Further, a disc spring 12 rotatably supported (switchable between a position when the clutch is engaged and a position when the clutch is disengaged) is added to the inertia body 4 by a spring. By operating the friction clutch, the inertia body 4 and thus the flywheel 2 of the transmission input shaft 10 are connected and disconnected. Inertial body 3 and inertial body 4
A damper mechanism in the form of a first damper device 13 and a second damper device 14 connected in series therewith is provided between and, which damper mechanism causes relative rotation of the inertial bodies 3 and 4. To enable.

Both inertial bodies 3 and 4 are rotatably supported by bearings 15 relative to each other. The bearing portion 15 includes a rolling bearing 16 in the form of a single row ball bearing. The outer ring (outer race ring) 17 of the rolling bearing 16 is in the hole 18 of the inertial body 4, and the inner ring (inner race ring) 19 of the rolling bearing 16 is in the axial direction to the side opposite to the inertial body 3 and the crankshaft 5 side. Located on a central cylindrical pin 20 that extends and extends into bore 18.

The inner ring 19 is press-fitted onto the pin-shaped portion 20 and is axially fitted 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 20a of the pin-shaped portion 20.

A ring having an L-shaped cross section between the outer ring 17 and the inertial body 4.
25, 26 are provided, each of which is mounted on one side on the outer ring 17. Ring 2 with L-shaped cross section
5,26 legs 25a, 26a axially facing each other
Surrounds and engages the outer ring 17. A part of the legs 25b, 26b facing inward in the radial direction is the inner ring 1 in the radial direction.
It has reached the top 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 the perfect sealing of the bearing 16, the radially extending legs 25b, 26b are axially spring-loaded on the end face of the inner ring 19 by means of force-storing members in the form of disc springs 27, 28, respectively. Has been done. The disc spring 27 is supported radially outside on a shoulder of a disk 30 that is fixedly connected to the second inertia body 4 via a rivet pin 29, and
A spring load is applied radially inwardly to the end area of the leg 25b of the ring 25 in the radial direction. Similarly, the disc spring 28 is supported radially outwardly on the shoulder of the inertial body 4 and radially radially inwardly loads the end region of the radial leg 26b of the ring 26.

The hole 18 of the inertial body 4 receives the rings 25 and 26 to receive the outer ring 1
It has a larger diameter than the outer diameter of 7, which forms a radial intermediate space.

By appropriate selection of the material of the rings 25, 26, the rings are brought from the friction surface 4a cooperating with the clutch disc 9 into the bearing.
It can also serve as an insulation that at least reduces heat transfer to 16.

The bearing 16 is fixed to the inertial body 4 in the axial direction by interposing the rings 25 and 26 and tightened in the axial direction between the shoulder 31 of the inertial body 4 and the disk 30. .

The damper device 13 has two discs 30, 33 arranged on both sides of the flange 32, these being the retaining rivet pin 2
They are non-rotatably connected to each other with an axial gap therebetween. Preliminary rivet pin 29 has both discs 30,33
Also serves to fix the to the inertial body 4. Disc 30,33
Also, the flange 32 is provided with a notch 34 in which a force-storing member in the form of a coil spring is received. These accumulators 34 consist of a flange 32 and both disks 30,3.
It acts in the opposite direction against the relative rotation with 3.

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 includes the disk 30 and the inertial member 3 in the axial direction.
Is located between and and has a disc 30 and a pressure ring
A friction ring arranged between the pressure ring 36 and the inertial body 3 by means of a force-storing member 35 formed by a disc spring, which is held tightly between it and 36;
37 is tightened. The force acting on the disk 30 by the disc spring 35 is absorbed by the bearing 16.

The flange 32 forms the output part of the damper device 14 on the one hand and the output part of the damper device 14 on the other hand. The input part of this damper device 14 is formed by two disks 38, 39 which are axially spaced apart and which are not rotatable relative to the inertial body 3. The ring-shaped disc 39 is attached to the inertial body 3 by rivets 40. The disc 38 has axially formed tabs 38a integrally formed on the outer periphery thereof, 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 two disks 38, 39 are clamped together by means of a disc spring 43. To this end, the disc spring 43 is supported on the one hand by the inertial body 3 and, on the other hand, exerts a spring load on the disc 38 towards the disc 39.

The inertial body 4 has an axial through hole 45 between the hole 18 for receiving the rolling bearing 16 and the space 4a between the inertial bodies 4 when viewed in the radial direction.
The through hole reduces the amount of heat transfer from the friction surface 4a of the inertial body 4 cooperating with the clutch disc 9 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 the circumference of a virtual circle having the same diameter. Furthermore, the through hole 45 is arranged adjacent to the bearing 16, that is to say in the radial direction, very close to the bearing 15. The through hole 45 is the inertial body 4.
Starting from the friction surface 4a side of the damper device 1
It is expanded axially toward the surface 47 on the 3,14 side (first
Figure). 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 48.
49 extends radially outward in a circular arc shape in the direction toward the surface 47 of the inertial body 4, whereby the through hole 45 is formed in the inertial body 4.
In the surface 47 on the side opposite to the friction surface 4a, it falls to the outside in the radial direction through a part of the range X of the range extending in the radial direction of the friction surface 4a (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 is the through hole.
Flows through 45 along the backside 47 of the inertial body 4, thereby cooling it. 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, as seen in the circumferential direction, there are two through holes 45 between each of the two rivet pins 29, in which case the through holes 45 and the rivet pins 29 are of at least approximately equal diameter 50. It is located on the circumference of a virtual circle. Webs 51 and 52 are formed between the through holes 45, so that the heat generated from the friction surface 4a reaches the inner region 53 of the inertial body 4 which is closed around the rolling bearing 16. , The above web
You have to go through 51,52. In the illustrated embodiment, the web 52 through which the rivet pin 29 passes is longer than the web 51 through which the rivet pin 29 does not pass when viewed in the circumferential direction (second
Figure). In the illustrated embodiment, the circumferential length of the web 52 is web.
It is at least approximately twice the circumferential length of 51. Through hole 45
Is slightly longer than the shortest extent of web 51 in the circumferential direction, but shorter than the shortest extent of web 52. Further, as can be seen in FIG. 2, the through hole 45 extends over at least approximately 50% of the imaginary circle of the diameter 50 of the inertial body 4.

Two rivet pins 29 if the load generated is small
By connecting the two through holes by removing one web 51 between the two through holes 45, as shown by a chain line 54 in FIG. 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 have a small cross section. Can also be obtained by forming a blocking portion or a throttle portion for the heat conduction flow by. Based on the radial mass distribution of the inertial body 4 with respect to the diameter range in which the through holes 45 or the webs 51, 52 are provided, the amount of heat generated in the clutch is substantially equal to that of the inertial body 4 surrounding the bearing 16. The temperature of the inertial body 4 in the radially outer region of the inner region 53 present is slightly increased, but the inner region 53 and thus also the bearing 16 are exposed to a significantly lower temperature. By providing the through holes 45, the effect that the inertial body 4 only produces a slightly higher temperature only in the area radially outside these through holes 45 has the effect that most of the material of the inertial body 4 is produced. Alternatively, most of the mass of the inertial body is located outside of the through holes 45 in the radial direction.

Yet another advantage of the illustrated arrangement is that a rivet pin fixed to the web 52, which acts as a blocking or throttling portion of the heat transfer path, directs a portion of the heat to the disks 30, 33, thereby allowing the through holes to pass. The fact is that the heat exchange surface with the air flow produced is increased.

For example, when using a bearing with a seal ring, provided by the bearing manufacturer, in many applications the rings 25, 26 are omitted and the bearing outer ring 17 is fitted into a hole 18 adapted to the outer ring periphery. By directly pressing the bearing 16
It is possible to attach the 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 sectional view taken along the line II-II in FIG. 1 ... Device for absorbing or compensating for rotational impact of internal combustion engine, especially torque fluctuation, 2 ... Flywheel, 3,4 ... Inertia, 4a ... Friction surface, 5 ... Crankshaft, 6 ... Fixed Bolt, 7 ... Friction clutch, 8 ... Pressure plate, 9 ... Clutch disc, 10 ... Transmission input shaft, 11
...... Clutch cover, 12 ...... Disc spring, 13 ...... First damper device, 13a ...... Friction device, 14 ...... Second damper device, 1
5 …… Bearing part, 16 …… Rolling bearing, 17 …… Outer ring, 18 ……
Hole, 19 ... Inner ring, 20 ... Pin-shaped part, 20a ... End surface, 21 ...
… Shoulders, 22 …… fixed discs, 25 …… rings, 25a, 25b…
… Legs, 26 …… rings, 26a, 26b …… legs, 27 …… disc springs, 28 …… disc springs, 29 …… rivet pins, 30 …… discs, 31 …… shoulders, 32 …… flange, 33 …… Disc, 34…
… Notches, 35 …… Accumulators, 36 …… Pressure rings, 37 ……
Friction ring, 38 …… disc, 39 …… disc, 40 ……
Rivet, 41 ...... Notch, 42 ...... Arm, 43 ...... Disc spring, 45 ...... Through hole, 47 ...... Face, 48 ...... Wall, 49 ...... Wall, 50 ...... Diameter, 51 ...... Web , 52 …… Web, 53 ……
Inner range

 ─────────────────────────────────────────────────── ─── Continuation of the front page (56) Reference JP-A-59-151624 (JP, A) Actual development S59-113548 (JP, U) Actual public S59-420 (JP, Y2)

Claims (29)

[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, which is arranged coaxially to each other via a rolling bearing portion and which opposes 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. In the second inertial body (4) of the type in which the second inertial body has a friction surface cooperating with the clutch disc. In the radial range between the surface (4a) and the rolling bearing portion (15), the gas flows from the clutch chamber to the outside formed between the inertial bodies on the internal combustion engine side of the second inertial body. Cooling air flowing through the open intermediate chamber A torque transmission device, characterized in that an inlet opening of an elongated through hole (45) for the air flow is provided in the circumferential direction. 2. The torque transmission device according to claim 1, wherein the through hole penetrates the inertial body in the axial direction. 3. The cooling air flow flows along the wall surface of the damper device, as claimed in claim 1 or 2.
The torque transmission device according to the item. 4. A through hole (45) is formed in a slit shape on the friction surface side of the second inertial body, and the cross section of the through hole is the same as the friction surface side of the second inertial body. Towards the other side,
The torque transmission device according to claim 1, which is expanded. 5. The torque transmission device according to any one of claims 1 to 4, wherein the through hole (45) is formed in a fan blade shape. 6. The torque transmission device according to claim 1, wherein the through hole (45) is adjacent to the rolling bearing portion (15). 7. A through hole (45) is provided in the second inertial body (4),
On the side (47) opposite to the friction surface (4a), the friction surface (4
The friction surface (4a) of the inertial body (4) over the range (X) of at least a part of the portion extending in the radial direction of (a).
The torque transmission device according to any one of claims 1 to 6, wherein the torque transmission device extends radially outward at a position axially lower than a plane of a surface opposite to the surface. 8. The through hole (45) has a radial cross section,
The second inertial body (4) is configured as follows.
Of the through hole (45) extending from at least the friction surface side surface (46) of the through hole (45) in the radial direction, and the radially outer wall surface (49) of the The torque transmission device according to any one of claims 1 to 5, which descends radially outward in a direction toward the surface (47) on the opposite side of the second inertial body (4). . 9. The torque transmission device according to any one of claims 1 to 7, wherein the through holes (45) are evenly distributed in the circumferential direction. 10. The torque transmission according to any one of claims 1 to 9, wherein the through holes (45) are arranged on an imaginary circle having the same diameter (50). apparatus. 11. The through hole (45) is within the entire central angle range of the inertial body.
Claims 1 to 10 which cover 20 to 70%
The torque transmission device according to claim 1. 12. A web (51, 52) provided between two adjacent through holes (45) has a circumferential direction 0.5 to 2.5 times the circumferential length of one through hole (45). The torque transmission device according to any one of claims 1 to 11, which has a length. 13. 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.
Non-rotatable with respect to the inertial body of and through hole (45)
Is arranged between the rivet pins (29) when viewed in the circumferential direction, the torque transmission device according to any one of claims 1 to 12. 14. The torque transmission device according to claim 13, wherein the through hole (45) and the rivet pin (29) are provided on an imaginary circle having at least approximately the same diameter (50). 15. Two rivet pins (2
The torque transmission device according to claim 13 or 14, wherein two through-holes (45) are provided between the two. 16. Exists between two through holes (45),
14. The web according to claim 13, wherein the web (52) having the rivet pin (29) has a larger circumferential length than the web (51) having no rivet pin (29). The torque transmission device according to any one of items 1 to 15. 17. The circumferential length of the web (52) having the rivet pin (29) is at least approximately twice the circumferential length of the web (51) without the rivet pin (29). , Any one of claims 13 to 16
The torque transmission device according to the item. 18. A means (25, 26) for reducing at least the amount of heat flowing from the friction surface (4a) to the rolling bearing portion (15),
The heat insulating portion is provided between the friction surface (4a) and the rolling bearing portion (15), and the heat insulating portion is at least 1
A torque transmission device according to any one of claims 1 to 17, characterized in that it is formed by a ring (25, 26) having an L-shaped cross section. 19. An inertial member of both inertial members has an axial additional portion that axially penetrates into a central hole of the other inertial member, and a bearing portion is arranged between the additional portion and the hole. The heat insulating part (25, 26) is arranged between the central hole (18) and the bearing part (15), and any one of claims 1 to 18 is defined. Torque transmission device. 20. Torque transmission device according to claim 1, characterized in that the heat insulating part (25, 26) serves as the only packing for the bearing part (15). 21. 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, the torque transmission devices being arranged coaxially with each other via a rolling bearing portion and resisting 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. A second inertial body having a friction surface for cooperating with a clutch disc, the second inertial body being coupled to an input portion of the transmission.
Friction bearing (4a) and rolling bearing (15) in the inertial body of
An axial through hole (45) that expands toward the first inertial body (3) side in a radial range between the first inertial body (3) and the second inertial body internal combustion engine. On the side for the cooling air flow flowing along the wall surface of the damper device through the outwardly-opening intermediate chamber formed between the two inertial bodies. Torque transmission device. 22. A means (25, 26) for reducing at least the amount of heat flowing from the friction surface (4a) to the rolling bearing portion (15),
The heat insulating portion is provided between the friction surface (4a) and the rolling bearing portion (15), and the heat insulating portion is at least 1
22. Torque transmission device according to claim 21, characterized in that it is formed by one ring (25, 26) of L-shaped cross section. 23. One leg (25a, 26a) of a ring (25, 26) of L-shaped cross section axially covers one (17) of a bearing race and the other leg (25b). 23. The torque transmission device according to claim 22, wherein the (26b) extends radially in the direction of the other (19) of the bearing races. 24. A leg portion (25b, 26) of a ring having an L-shaped cross section.
The torque transmission device according to claim 23, wherein b) abuts against one of the bearing races and seals. 25. A leg portion (25b, 26) of a ring having an L-shaped cross section.
b) is spring-loaded by the disc springs (27, 28) toward the bearing ring, and the disc springs are attached to the transmission input shaft (10).
Claim 23 or 24, wherein the second inertial body (4) connected to the housing and the end area of the radial leg are clamped radially outside and inside, respectively. The torque transmission device according to the item. 26. An inertial member of both inertial members has an axial additional portion that axially penetrates into a central hole of the other inertial member, and a bearing portion is arranged between the additional portion and the hole. The heat insulating part (25, 26) is arranged between the central hole (18) and the bearing part (15), and any one of claims 21 to 25 is defined. Torque transmission device. 27. Torque transmission device according to any one of claims 21 to 26, characterized in that the heat insulating part (25, 26) serves as the only packing for the bearing part (15). 28. 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 first inertial body of the two inertial bodies being coupled to the internal combustion engine and the other second inertial body being frictional. In the type in which the second inertial body has a friction surface that cooperates with the clutch disc and is connected to the input portion of the transmission through the clutch, the rolling bearing portion (15) is rotated from the friction surface (4a). (25, 26) for reducing at least the amount of heat flowing to the bearing) is provided as a heat insulating portion arranged between the friction surface (4a) and the rolling bearing portion (15), and the heat insulating portion is at least one. , The cross section is L
It is formed by a letter-shaped ring (25, 26), which axially covers one (17) of the bearing inner and outer rings with one of its legs (25a, 26a) and the other leg (25b). , 26
b) extends in the radial direction toward the other (19) of the bearing inner and outer rings, abuts against and seals against this bearing race, and is axially moved by the disc springs (27, 28) in the direction of this bearing race. The end of the radial leg of the L-shaped ring (25, 26) and the second inertial body (4) that is loaded and is coupled to the input portion (10) of the transmission. Between the friction surface (4a) and the rolling bearing portion (15) in the second inertial body (4), which are tightened on the outer side and the inner side in the radial direction, respectively. A torque transmission device characterized in that an axial through hole (45) for cooling air flow is provided in the. 29. 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. 29. Torque transmission device according to claim 28, characterized in that a circumferentially elongated through hole (45) is provided for the cooling air flow flowing therethrough.