JPS6110120A - Transmission gear for torque - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a torque transmission device, in particular for an internal combustion engine, with means for dampening rotational shocks, which are arranged coaxially with respect to each other via a bearing mechanism. at least two masses rotatable with respect to each other within certain limits and opposite to the action of the damping device, the first mass being connected to the engine and the second mass being connected to the friction device. The present invention is of the type that can be connected to an input of a power transmission via a friction surface and that is provided with a friction surface that cooperates with a clutch disc.

2. Description of the Prior Art Conventionally, in torque transmission devices of this type, a bearing mechanism is provided directly between the two masses, so that when rolling bearings are used, one of the masses is attached to the other mass, and the other race is non-rotatably coupled to the other mass. When using this torque transmission device, be sure to
)/ and the drive system, but this torque transmission device has become generally widely used in automobiles due to the short life of the bearing mechanism arranged between the two mass bodies. In other words, this bearing TPM has a short service life because it is used harshly, and is a cancer in this type of equipment.

SUMMARY OF THE INVENTION It is therefore an object of the present invention to provide a torque transmitting device of the type mentioned at the outset with improved functionality and a longer service life, while also being particularly simple and economical to manufacture. An object of the present invention is to provide a torque transmission device that is as follows.

Means of the Invention for Solving the Problems The gist of the invention for solving the above problems is that means are provided for at least reducing the flow of heat from the friction surface to the support mechanism.

Extensive experiments have shown that the thermal energy released during operation of the friction clutch is responsible for the unacceptable thermal loading of the bearing.

Particularly when a bearing with little storage play is used, a jamming phenomenon occurs within the bearing due to the difference in expansion and contraction that occurs between each component due to rapid heating and cooling. The reason for this is that if a large temperature difference occurs between the parts of the bearing, the bearing will lose play. The measure of the invention furthermore avoids overheating of the delivery lubricant, for example oil, grease, etc., which results in always sufficient bearing lubrication and thus increases the service life of the bearing.

As a means of preventing unacceptable heating of the bearing, a heat insulating material is particularly preferably arranged between the friction surface and the bearing.

It is particularly advantageous if the insulation is arranged between the support area of the second mass and the bearing.

Such an arrangement of the insulation is particularly advantageous in devices in which the support mechanism has rolling bearings. This is because a thermal insulation can be provided between the race comprising the second mass and non-rotatably connected thereto, and the supporting part of this mass forming a seat for accommodating the bearing. It is from.

Various materials are available for fabricating insulation to prevent overheating of the bearing mechanism. Particularly advantageously, the insulation material is plastic,
It can be made of plastic or ceramic material, optionally reinforced with fibers. As plastics used are duroplastics, in particular phenoplastics, such as hard paper, or thermoplastics, such as polytetrafluoroethylene/, polyamide or biryamidemide.

Furthermore, the insulation material can also consist of fiber-reinforced polycarbonate, in particular if one of the masses is provided with an axial projection which axially extends into the central recess of the other mass. If the bearing mechanism is arranged between the projection and the recess, it is advantageous if the heat insulating material is arranged between the central recess and the bearing. One of the masses has a central projection which projects axially into a central notch of the other mass, and a bearing mechanism is provided between the projection and the notch. If so, a heat insulating material is advantageously arranged between this projection and the bearing.

the second mass coupled to the input of the power transmission device has a central notch, and a heat insulating material is disposed between the notch and the bearing race non-rotatably coupled thereto; is particularly advantageous.

an inner race of the bearing is disposed on the protrusion, and
Advantageously, the outer ring is accommodated in the central recess and supports the second mass via a heat insulating material.

There are various ways to secure the lace insulation, depending on the material selection. In the arrangement, the insulation material is fixed to the bearing or the corresponding race by an injection method, a sintering method or, if it consists of an insulation ring with a sleeve-like region, to the bearing by pressing.

In another advantageous possibility of providing a heat-insulating gold film between the bearing and the corresponding mass, the outer ring is accommodated in a cutout with a large diameter compared to its outer diameter, and the outer ring A bearing is premounted on one of the masses in such a way that the space between them is filled by injection or injection with plastic.

Particularly preferably, the insulation material is also designed as a packing for the bearing. For this purpose, the insulation material is provided with an integral packing for the bearing.

In that case, the insulation is formed by at least one ring of cross-sectional shape, one leg of which covers and grips one of the bearing races in the +h direction, and the other leg of this ring covers and grips one of the bearing races in the It is advantageous if the legs extend radially towards the other bearing race. In that case, the radially extending leg of the cross-sectional insulation extends at least partially along the radial direction of the bearing race that is not axially covered by the insulation, and It is effective to have support from this race.

Although it is effective in many applications for the insulation to be formed from a cross-section ring whose axially extending legs extend at least approximately the full width of the race, it is advantageous in many applications, but it is effective in many applications when the insulation is Torque transmission in which the rolling bearing is accommodated in a central recess in a mass with friction surfaces, which is particularly effective if the rings are mounted on one bearing race from one side in each case. It is particularly advantageous for the device if the ring of insulating material, which is cross-sectionally shaped, is provided with legs pointing radially inward in cross-section and is accommodated in the outer ring.

In order to ensure an adequate sealing of the bearing, the radially extending legs of the ring made of insulation material must be loaded axially by the force storage element towards the bearing race, which is half-covered by the legs. It is particularly advantageous if the legs are crimped onto the end faces of the laces. A force storage element of this kind is advantageously formed by a disc spring.

When a ring of insulating material with an angular cross-section is installed in a bearing, its radial legs are elastically attached, so that it is elastically supported on the race that is radially covered by these legs. It is best to form the

When using a disc spring for loading the packing leg, which extends in the radial direction of the insulation, the disc spring extends radially outwardly into a second mass connectable to the input of the power transmission. It is particularly advantageous if it is supported and axially loaded radially inwardly in the end region of the radial leg of the sealing ring.

For assembly, it is particularly advantageous if the insulation has a sleeve-like area that is pressed into the recess of one of the masses, which accommodates the bearing. Depending on the intended use, the insulation material is first press-fitted into the recess, or the insulation material is first attached to the bearing and then press-fitted together with it into the recess of one of the masses. is effective. In a further embodiment, the sleeve-like regions of the insulation material gripping the bearings have different thicknesses or diameters in the axial direction, so that only the regions with the larger diameters or thicknesses are pressed. It is accommodated in the bearing receiving recess by a fit.

When using bearings based on a lubricating medium, a packing is provided between the leg of the ring, which has a cross-section that covers and grips the force bearing race in the axial direction, and this bearing race. It is particularly advantageous if the additional packing prevents lubricating medium from penetrating between the insulation and the raceway due to centrifugal forces, for example. A packing of this kind is preferably designed as an OIJ ring. In that case, the packing is supported on the inner peripheral surface of the axially extending leg of the insulation and is accommodated in a cutout in the outer race, for example a chamfer or a groove.

Advantageously, the packing is tightened between the end of the axially extending leg of the insulation and the shoulder of the outer race.

(Image quality in relation to simple assembly and manufacturing tolerances) i3: In order to be able to position the body between the bodies without any problems, the second
Advantageously, a ring of heat-insulating material with a conical or tapered cross section is arranged between the support area of the mass and the bearing.

In that case, the bearing and/or the support area can have a conical or tapered circumferential surface adapted to the insulation ring. automatically compensates for accidental wear,
In addition, in order to sufficiently fix and hold the bearing in its receiving hole, it is effective that the heat insulating ring, which has a conical or tapered cross section, is subjected to an elastic force in the axial direction in its narrowing direction. , whereby the insulation ring is clamped between the receiving hole and the corresponding race.

To ensure sufficient tightening of the insulation ring, the insulation ring can be provided with a slit and left open.

The conical or tapered insulation ring can also have a seal for the bearing.

This seal is formed as described above and is loaded in the axial direction by means of a force accumulator towards the end face of the race supporting the seal.

DESCRIPTION OF THE PREFERRED EMBODIMENTS As can be seen from FIG. 1, the rotary shock absorber 1 is equipped with a flywheel 2, which is divided into two mass bodies 3, 4. The mass body 3 is fixed to a crankshaft 5 of an engine (not shown) via a fixing screw 6. mass body 4
A friction clutch 7 is fixed by means not shown. A clutch disc 9 is provided between the pressure plate 8 of the friction clutch 7 and the mass body 4, and this clutch disc 9 is attached to an input shaft 10 of a power transmission device (not shown). The pressure plate 8 of the friction clutch 7 is biased towards the mass 1 by a disk spring 12 which is pivotably mounted on the clutch clutch 11. By operating the friction clutch 7, the mass body 4 and thus the flywheel 2 of the input arm 110 are disconnected and disconnected. Image mass 3.4. A shock absorber 13 and a parallel 1/slip clutch 14 are provided therebetween, both of which permit relative movement between the image masses 3, 4 within certain limits.

The image bodies 3 and 4 are rotatably supported relative to each other via a bearing m1xs. The support mechanism 15 includes a single row ball bearing 16. The outer race 17 of the ball bearing 16 is inserted into the notch 18 or hole of the mass body 4, and the inner race 19 of the mass body 3 extends axially away from the crankshaft 5 and projects into the notch 18. It is attached to a cylindrical central protrusion 20.

The inner race 19 is attached to the projection 20 by a press fit and is axially clamped between the shoulder 21 of the projection 20 or of the mass 3 and the safety disc 22. The safety disc 22 is fixed to the end surface 20a of the protrusion 20 by screws 23.

A heat insulating material 24 is provided between the outer race 17 and the mass 4, by which the flow of heat from the friction surface 4a of the mass 4 cooperating with the clutch disc 9 to the ball bearing 16 is interrupted or At least it's alleviated. by this,
Overheating of the bearing grease filling as well as excessive thermal strain or unacceptable elongation of the bearing are prevented.

Otherwise, excessive thermal strain as well as unacceptable elongation could cause ball 16a to jam between the inner and outer races.

For receiving the insulation 24, the recess 18 in the mass 4 has a large diameter compared to the diameter of the outer ring 17, thereby creating a radial gap.

The insulation 24 is formed by two rings 25 and 26 of cross-section, which are each attached to the outer ring 17 from one side.

The legs 25a of this ring 25, 26 have an angular cross-section.

26a covers the outer race 17. The radially inwardly directed leg zsb, 26b partially radially connects the inner race 1
9 and is supported in the axial direction on the inner ring 19, thereby also serving as a packing for the ball bearing 6. In order to ensure a sufficient sealing of the ball bearing 16, the radially extending legs 25b, 26b are each loaded axially towards the end face of the inner ring 19 by a force accumulator consisting of a disk spring 27,28. ing. Belleville spring 27r1. radially outwardly on the shoulders of the plate 30 connected to the second mass 4 via standoff bolts 29 and radially inwardly on the ends of the radial legs 25b of the ring 25 Loading space. Similarly, disc spring 2
8 is supported radially outwardly on the shoulder of the mass 4;
and radially inwardly the radial legs 26 of the ring 26
Loading the end region of b.

For mounting the ring 25.26 and the ball bearing 16, in the embodiment shown in FIG.
A ball bearing 16 with 6 is preferably press-fitted into the bore or recess 18 of the mass 4 . The ball bearing 16 is a ring 25
The shoulder 31 of the mass body 4 and the plate 3 in the axial direction are
0, and is immovably fixed to the mass body 4 in the axial direction.

The shock absorbers 13 are arranged on both sides of the flange 32! It has two plates 30.33 which are separated by W and are non-rotatably connected to each other at an axial distance via spacer bolts 29.

The separating plate 29 also serves to secure the two plates 30,33 to the mass 4. A notch is provided in the plate 30.33 as well as in the flange 32, and a coil spring 34 is inserted into this notch.
A force storage member consisting of is housed. This coil splash 3
44 acts against the relative rotation between the flange 32 and both plates 30.33.

Furthermore, the damping device 13 has a friction device 13a, which is effective over a variable relative rotation angle between the two masses 3.4. The friction device 13a is arranged axially between the plate 30 and the mass body 3 and is provided with a force accumulating member formed by a disc spring 35, which is in contact with the plate 30 under pressure. A friction ring 37 arranged between the pressure ring 36 and the mass body 3 is thereby tightened. The force acting on plate 30 by countersunk spring 35 is supported by ball bearing I6.

It forms the input part of the 32-piece shock absorber 13 and also forms the output part of the slip clutch 14. The input of the slip clutch 14 is formed by two axially spaced plates 38.39, which are non-rotatable relative to the mass.

An annular plate 39 is fixed to the mass body via four beams 40. A tongue piece 38a extending in the bow direction is integrally formed on the outer periphery of the plate 38, and this tongue piece 38a engages in the notch 41 of the plate 39 to prevent rotation of the plate 38 with respect to the plate 39. There is.

A radial projection lI2 of the flange 32 is clamped 1 between the two plates 38, 39 in the axial direction.

For this purpose, the two plates 38, 39 are compressed together by disc springs 43. For this purpose, the countersunk gear 43 is supported on the mass 3 and loads the plate 38 towards the plate 39. In the region between the projections 42 of the flange 32, a cutout is provided in the plate 38,39,
This recess coincides in the middle direction and accommodates a force accumulator 14, which serves as an end stop for the arrow 712 of the flange 32 and thereby controls the slip clutch 14. Rotation angle is limited.

In the embodiment shown in FIG. 2, mass body 1 for mass body 3
A ball bearing 116 is likewise used for the support of the ball bearing 116, which is arranged similarly to the ball bearing 6 shown in FIG. The outer L'-seat 1.17 of the ball bearing 116 is provided with chamfered portions 117a and J17b, which allow the outer race 117 and the rings 125 and 126 made of heat insulating material that cover it in the axial direction to be connected to each other. A space is formed in between. A packing consisting of ○ rings 145° 1 and 16 is arranged within this space.

These OIJ rings 145 and 146 protect the grease between the rings 125 and 126, each having an angular cross section, and the outer race 117 from being extruded or oozing out. Chamfered portions 117a, 117b and O-ring l 115
, 1 = 16 is a cross-sectional ring 125, 12C)
and the chamfered portion 1 of the ball bearing 116 ] 7 a , 1 ],
7b and 0-ring are mutually defined so as to be elastically deformed.

As shown in Fig. 2, the ring 125 has a cross-sectional shape.
．． The thickness of the radial legs 125b, 126b of 126 is reduced compared to the thickness of the axially extending legs 125a, 126a. Leg portion 125b.

Seal nose 125C at the radially inner end of 126b.

126C is integrally molded.

In the embodiment shown in FIG. 3, a ring 225 made of a heat insulating material and having a conical or tapered cross section is arranged between the notch 218 of the mass body 4 containing the ball bearing 216 and the outer race 217. In this embodiment, both the outer circumferential surface and the inner circumferential surface of the ring 225 extend conically in the axial direction. - It is also possible to design it in such a way that only the 10,000 circumferential surface extends conically.

The notch 218 is adapted to the conical outer circumferential surface of the ring 225, and the outer circumferential surface of the outer race 217 is adapted to the conical inner circumferential surface of the ring 225. A ring 225 made of a heat insulating material is loaded in a direction in which it becomes thinner in the axial direction by a disc spring 227, and the disc spring 227 is supported by a plate 230 fixed in the axial direction with respect to the mass l. The ring 225 has a radially inwardly extending region 225b which axially bears against the inner race 219 of the ball bearing 216 thereby sealing the ball bearing 216. ball bearing 2
A ring 226 of thermal insulation material is provided to seal the other side of the disc spring 22.
70 action causes the outer race 217 and the crosspiece 4 in the axial direction.
It is tightened between the shoulder 231 of the

The ring 226id'/- includes a ring 226b, which is axially supported on the inner race 219.

In the embodiment shown in FIGS. 1 and 2, disc spring 27.
28 is a radially extending sealing area 25.26i:);
125b and 126b are loaded toward the inner races 19 and 119 in the axial direction.

Depending on appropriate material selection, rings 25, 217)
; 125, 126 may be assembled to form the rings 25, 26; 125° 126 such that their radial legs 25b, 26b; Thereby, the ring is axially supported under preload on the inner races 19, 119 of the ball bearings 16, 116. According to this means, 8f of the disc springs 27, 217)
f: Can be omitted.

In the embodiment described above, the insulation was formed by an additional ring distributed between the second mass 1 and the ball bearing 16 (16, 116, 217). However, in another embodiment, not shown, the insulation material may be
, 217) 16 or outer race 17 , 1.17
, 217, the injection molding can also be attached by the stem-joining method, in which case the heat insulating material becomes virtually integral with the ball bearing. Similarly, cut out the insulation material 1B, 118, 2
It can also be attached to the circumferential surface of 1.8.

When using a bearing with a packing ring, such as that provided by a bearing loader, the outer race 1'7 is inserted and held centered in a notch 18 having a diameter larger than its outer diameter; It is also possible to pre-mount the ball bearing 16 on the mass body 4 in such a way that the space between the notch 18 and the outer ring 17 is filled with plastic or artificial resin.

Effects of the Present Invention According to the present invention, the thermal load on the bearing is reduced by the heat insulating material, thereby increasing the useful life of the bearing.

[Brief explanation of the drawing]

FIG. 1 is a vertical sectional view of a first embodiment of the present invention, FIG. 2 is a partial sectional view of a second embodiment of the present invention, and FIG. 3 is a partial sectional view of a third embodiment of the present invention.
FIG. 3 is a partial cross-sectional view of the embodiment. 1... Rotating shock absorber, 2... Flywheel, 3, 4
...Mass body, 1a.Friction surface, 5.Crankshaft, 6.Fixing screw, 7.Friction clutch, 8.Pressure plate, 9.Clutch disk, 10.Input shaft. 11 ・
Clutch cover, 12... disc spring, 13... shock absorber, 1 tl... slip clutch, 15... support mechanism, 1
6 Ball bearing,] 7... Outer race, 18... Hole, 19
・Inner race, 20... Protrusion, 20a... End surface, 21
・・Shoulder, 22・・Safety disc, 23・・Screw, 24・・
Insulation, 25, 2 Rolling, 25a, 26a. 25b, 26b... Legs, 27. 28... Belleville springs, 29
... Separation bolt, 30... Plate, 31... Shoulder, 32...
・Flange, 33...Plate, 311...Coil spring, 35
... Belleville spring, 3G... Pressure ring, 37... Friction ring, 38. :', 9... board, 40... rivet, 4
1...notch, 42...protrusion, 43...disc spring, l14
...power storage member, 117 a , 117 b , -
Chamfer s, 145...0 ring.

Claims (1)

[Claims] 1. A torque transmission device equipped with means for damping rotational impact, especially engine torque fluctuations, which are arranged coaxially with each other via a support mechanism to counteract the action of the damping device. comprising at least two masses rotatable with respect to each other within certain limits, the first mass being connected to the engine and the second mass being connected via a friction device to the input of the power transmission device; In a version that is possible and is provided with a friction surface cooperating with the clutch disc, said friction surface (4a
) to the bearing mechanism (15). 2. Torque transmission device according to claim 1, wherein said means consists of a heat insulating material arranged between the friction surface (4a) and the bearing mechanism (15). 3. The heat insulating material covers the support area (18, 1) of the second mass (4)
18, 218) and the bearing (16, 116, 216). 4. The support mechanism is a rolling bearing (16, 116, 21
6), and the heat insulating material (24, 125, 126, 2
25, 226) support the second mass body (4) and are non-rotatably coupled to the bearing race (17, 117, 21).
7) and a seat provided on the mass body (4) for housing the bearing (
18, 118, 218), the torque transmission device according to any one of claims 1 to 3. 5. Insulation material (24; 125, 126; 225, 226)
Claims 1 to 4 consist of plastic.
The torque transmission device according to any one of the preceding paragraphs. 6. Insulation material (24; 125, 126; 225, 226)
Claims 1 to 4 consist of a ceramic material.
The torque transmission device according to any one of the preceding paragraphs. 7. Insulation material (24; 125, 126; 225, 226)
5. The torque transmission device according to claim 1, wherein the torque transmitting device is made of a duroplastic material. 8. Insulation material (24; 125, 126; 225, 226)
Claims 1 to 5 consist of a thermoplastic material.
The torque transmission device according to any one of the preceding paragraphs. 9. Insulation material (24; 125, 126; 225, 226)
A torque transmission device according to any one of claims 1 to 5, wherein the torque transmission device is made of fiber-reinforced polycarbonate. 10. One mass body is provided with an axial protrusion, this protrusion protrudes into the central notch of the other mass body in the axial direction, and there is a gap between the protrusion and the notch. The support mechanism is arranged, and the heat insulating material (24; 125, 1
26; 225, 226) are central notches (18, 118,
218) and the bearing (16, 116, 216). 11. One of the masses has a central protrusion, which protrudes axially into the central notch of the other mass, and a bearing is provided between the protrusion and the notch. 10. The torque transmission device according to claim 1, wherein the mechanism is arranged and a heat insulating material is arranged between the protrusion and the bearing. 12, a second coupled to the input section (10) of the power transmission device;
The mass body (4) of the central notch (18, 118, 218)
and a heat insulating material (24; 125, 126; 225, 226) is arranged between this notch and the bearing race (17, 117, 217) non-rotatably coupled thereto. A torque transmission device according to any one of claims 1 to 11. 13. Inner race (19) of bearing (16, 116, 216)
, 119, 219) are arranged on the protrusion (20), and the outer race (17, 117, 217) is housed in the central notch (18, 118, 218),
and insulation material (24; 125, 126; 225, 226)
13. Torque transmission device according to claim 1, wherein the second mass body (4) is supported via the second mass body (4). 14. The torque transmission device according to any one of claims 1 to 13, wherein the heat insulating material is attached to the bearing by an injection method. 15. The torque transmission device according to any one of claims 1 to 13, wherein the heat insulating material is attached to the bearing by a sintering method. 16, The insulation material (24; 125, 126) is the bearing (16,
116) The torque transmission device according to any one of claims 1 to 13, which is press-fitted to the torque transmission device. 17. The outer race (17) is accommodated in a cutout (18) having a larger diameter than its outer diameter, and the space between the cutout (18) and the outer race (17) is filled with plastic by injection method or Torque transmission device according to any one of the claims 1 to 16, characterized in that the bearing (16) is previously mounted on one mass (4) in such a way that it is filled by injection method. . 18, insulation material (24; 125, 126; 225, 226
18. Torque transmission device according to one of the claims 1 to 17, wherein the bearing (16, 116, 216) also serves as a packing. 19, insulation material (24 125, 126; 225, 226
) is the packing (
25b, 26b, 125b, 126b, 225b, 22
6b), the torque transmission device according to any one of claims 1 to 18. 20, the insulation (24; 125, 126; 225) is formed by at least one ring (25, 26) of L-shaped cross section, one leg (25a,
26a; 125a, 126a; 225a) axially covers and grips one of the bearing races (17, 117, 217), and the other leg of the ring radially grips the other bearing race (19 , 119, 219), the torque transmission device according to any one of claims 1 to 19. 21, L-shaped cross-section insulation material (24; 125, 126; 2
25) extending in the radial direction of the legs (25b, 26b, 12
5b, 126b, 225b) in the bearing race (19, 119, 21
21. Torque transmission device according to claim 20, which extends at least partially along the radial direction of the race (9) and is axially supported on this race (19, 119, 219). 22. The insulation material consists of two rings with an L-shaped cross section (25, 26
; 125, 126), and each ring is attached to one bearing race (17, 117) from one side, respectively.
Torque transmission device as described in section. 23. Ring made of heat insulating material with L-shaped cross section (25, 26
; 125, 126; 225) are radially inwardly directed legs (25b, 26b, 125b, 126b, 2) when viewed in cross section.
25b) and outer races (17, 117, 2
Claims 1 to 2 contained in 17)
The torque transmission device according to any one of items 2 to 2. 24, ring made of heat insulating material (25, 26; 125, 1
26; 225) radially extending legs (25b, 26
b, 125b, 126b, 225b) is the force storage member (27
, 28, 227) in the axial direction towards the bearing race (19, 119, 219), which is half-covered by the leg. The torque transmission device according to item 1. 25. The torque transmission device according to claim 24, wherein the force storage member comprises a disc spring (27, 28, 227). 26, a disk spring (27, 28) is supported radially outwardly on a second mass (4) connectable to the input part (10) of the power transmission device and sealed radially inwardly; The radial legs (25b, 26b) of the rings (25, 26)
26. Torque transmission device according to claim 24 or claim 25, wherein the end region of the torque transmission device is axially loaded. 27. The insulation (25, 26; 125, 126) has a sleeve-like area (25a, 26a; 125a, 126a), which area accommodates the bearing (16, 116) of one mass. 28. Torque transmission device according to any one of claims 1 to 27, which is press-fitted into the notch (18, 118) of (4). 28. The insulation (24) is first attached to the bearings (16, 116) and then together with one of the masses (4)
28. The torque transmitting device according to claim 27, which is press-fitted into the notch (18, 118) of the torque transmitting device. 29. The sleeve-like regions of the insulation material that grip the bearing have different thicknesses or diameters in the axial direction, so that only the region with the larger diameter or thickness can be secured to the bearing by press-fitting. The torque transmission device according to any one of claims 1 to 28, which is accommodated in the accommodation notch. 30. Rings (125, 126) with an L-shaped cross section that cover and grip one bearing race (117) in the axial direction.
legs (125a, 126a) and this bearing race (1
29. The torque transmission device according to any one of claims 1 to 29, wherein a packing (145, 146) is provided between the torque transmitting device and the torque transmitting device. 31. The torque transmission device according to claim 30, wherein the packing comprises O-rings (145, 146). 32, the packing (145, 146) is the insulation material (125
, 126) extending in the axial direction of the legs (125a, 126a).
31. The torque transmission device according to claim 29 or 30, wherein the torque transmission device is supported on the inner circumferential surface of the outer race (117) and accommodated in the gap of the outer race (117). 33. The torque transmission device according to claim 30 or 31, wherein the packing is tightened between the end face of the leg portion extending in the axial direction of the heat insulating material and the shoulder of the outer race. 34. A ring (225) made of a heat insulating material having a conical or tapered cross section is arranged between the support area (218) of the second mass body (4) and the bearing (216). The torque transmission device according to any one of items 1 to 33. 35, a ring (225) in which at least one of the bearing (216) and the support region (218) is made of a heat insulating material;
34. The torque transmitting device according to claim 33, having a conical or tapered peripheral surface adapted to. 36. Claim 33 or 3, wherein the ring (225) made of a heat insulating material having a conical or tapered cross section is subjected to an axial preload in the direction of its narrowing.
4. Torque transmission device according to item 4. 37. The torque transmission device according to any one of claims 33 to 35, wherein the ring made of a heat insulating material has a slit. 38. The torque transmission device according to any one of claims 33 to 36, wherein the heat insulating material (225) is integrally provided with a packing (225b) for the bearing (216).