JP3009588B2 - Torque transmission device - Google Patents

Description

Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to at least two bearings which are arranged coaxially with each other via a bearing and which can rotate with a restriction to one another against the action of a shock absorber. A flywheel mass, one of the flywheel masses being connectable to the internal combustion engine and the other flywheel mass, the second flywheel mass being connectable to the input of the transmission; The invention relates to a torque transmission device having means for absorbing or compensating for rotational shocks, in particular torque fluctuations, of an internal combustion engine having a friction surface cooperating with a clutch disc. In such a torque transmitting device, it has already been proposed to provide a bearing directly between both flywheel masses (FRPS 2166604). When a rolling bearing is used, one bearing ring is non-rotatably connected to one fly mass and the other bearing ring is non-rotatably connected to the other fly mass. Such a torque transmission achieves very good damping of the vibrations occurring between the internal combustion engine and the drive train of the motor vehicle,
This torque transmitting device has not been widely used in the automotive industry until now because the service life of bearings located between flywheel masses is too short. Such a bearing is one of the problems with such a torque transmitting device, since this bearing is already unusable after a short operating time due to adverse operating conditions. [0003] The object of the invention is to provide an improved function and an extended service life in comparison with the previously proposed torque transmissions of the type mentioned at the outset, and in a particularly simple manner. It is to propose a torque transmission device which can be manufactured economically. SUMMARY OF THE INVENTION An object of the present invention is to provide a means for reducing the flow of heat from a friction surface to a bearing, the means being provided with an L-shaped cross section disposed between the friction surface and the bearing. And is arranged between the bearing area of the second flywheel mass and the bearing, the seal for the bearing being provided in the radial direction of the L-shaped insulation. The problem was solved by being provided on the legs. According to the present invention, the thermal load on the bearing is reduced. Extensive experimentation has shown that the thermal energy released during operation of the friction clutch causes a thermal load on the bearing which is undesirable for continuation. In particular, when a bearing having a small bearing space is used, a biting phenomenon occurs in the bearing due to an expansion or contraction phenomenon between individual components due to a very early heating and cooling. This is because the bearing space disappears due to the large temperature differences occurring between the individual bearing parts. Furthermore, the measures according to the invention avoid the occurrence of overheating of the bearing lubricant, for example oil, grease or the like, which guarantees always satisfactory bearing lubrication and thus a long service life of the bearing. [0006] Such an arrangement of thermal insulation is particularly advantageous in devices in which the bearings have rolling bearings. because,
Forming a bearing ring with a second flywheel mass non-rotatably coupled thereto and a seat for receiving the bearing;
This is because a heat insulator can be provided between the holding portion of the bounce mass body. Various materials are provided for the production of thermal insulators for preventing overheating of bearings. Particularly advantageously, the insulation can be made of plastic, optionally fiber-reinforced plastic or ceramic material. Plastics used are duroplastics, especially phenoplastics, for example hard paper or thermoplastics, for example polytetrafluoroethylene, polyamide or polyamideimide. Further, the insulation can be made of fiber reinforced polycarbonate. In particular, one of the fly masses is provided with an axial extension, which extends axially into the central cutout of the other fly mass, When the bearing is arranged between the bearing and the bearing, it is advantageous if the heat insulator is arranged between the central notch and the bearing. One of the fly masses has a central pin-shaped additional portion, which extends axially into the central notch of the other fly mass, and which is not in contact with the additional portion. If a bearing is arranged between them, it is advantageous if the heat insulator is arranged between this additional part and the bearing. A second motor coupled to the input of the torque transmitting device.
It is particularly advantageous if the flywheel mass has a central cutout and a thermal insulator is arranged between this cutout and a bearing ring which is non-rotatably connected thereto. An inner bearing ring is arranged in the additional part, an outer bearing ring is accommodated in the central notch, and supports the second flywheel mass via a heat insulator. It is effective to have. In order to fix the heat insulator to the bearing ring,
There are various methods depending on the material selection. For example, the heat insulator is fixed to the bearing by injection or sintering, or to the bearing by means of a press-fit if it consists of a heat-insulating ring with a sleeve-like area. Another advantageous possibility of providing an insulation between the bearing and the corresponding flywheel mass is that the outer bearing ring is housed in a notch having a diameter larger than its outer diameter, and the notch and the outer The bearing is pre-mounted on one of the fly masses in such a way that the space between it and the bearing ring is filled by injection or injection with plastic. [0012] It is particularly advantageous if the thermal insulation is also formed as a seal for the bearing. To this end, the heat insulator integrally comprises a seal for the bearing. In this case, the thermal insulation is formed by at least one ring having an L-shaped cross section, one leg of which axially covers and grips one of the bearing rings and the other of the rings. Advantageously, the legs extend radially toward the other bearing ring. In that case, the radially extending legs of the heat insulator having an L-shaped cross section extend at least partially along the radial direction of the bearing ring which is not axially covered by the heat insulator, and It is effective if supported by this ring. [0013] In many applications it is advantageous if the insulation is formed from a single L-shaped ring and its axially extending legs extend at least approximately over the entire width of the bearing ring. It is particularly advantageous if it consists of two L-shaped rings, which are each mounted on one bearing ring from one side. In a torque transmitting device in which the rolling bearing is accommodated in a central notch of a flywheel mass with a friction surface, a ring of L-shaped insulation is provided with a radially inwardly facing cross section. It is particularly advantageous if the legs are provided and are accommodated in an outer bearing ring. In order to ensure a sufficient sealing of the bearing, the radially extending legs of the ring of thermal insulation are pivoted by the energy storage element towards the bearing ring which is half-covered by the legs. It is particularly advantageous if the load is applied in one direction, whereby the leg is pressed against the end face of the ring. Such a storage element is advantageously formed by a disc spring. The ring of L-shaped insulation is elastically pre-shrunk on the radial legs when it is mounted on the bearing, so that the ring radially covered by the legs is elastic. It is good to be formed so that it may be supported. If a disc spring is used for loading the radially extending sealing legs of the insulation, the disc spring is mounted on a second flywheel mass which can be connected to the input of the transmission radially outward. It is particularly advantageous if the bearing element is supported radially and is axially loaded radially inward in the region of the end of the radial leg of the seal ring. For the assembly, it is particularly advantageous if the insulation has a sleeve-shaped area, which is pressed into a cutout in one of the flywheel masses, which houses the bearing. . Depending on the intended use, the insulation is first pressed into the notch, or the insulation is first mounted on the bearing and then pressed together with it into the notch of one of the fly masses. It is effective to become. In yet another aspect, the sleeve-like region of the insulation, which holds the bearing, has different thicknesses or diameters in the axial direction, so that only the region with the larger diameter or thickness is pressed. It is accommodated in the bearing accommodation notch by a fit. When using a bearing filled with a lubricating medium, one bearing ring is axially covered and gripped,
It is particularly advantageous if a seal is provided between the legs of the ring with an L-shaped cross section and the bearing ring, so that the lubricating medium can be removed, for example by centrifugal force, by means of the insulation and the bearing ring Is prevented from invading. Such seals are preferably formed as O-rings. In this case, the seal is supported on the inner peripheral surface of the axially extending leg of the insulation and is accommodated in a cutout of the outer bearing ring, for example a bevel or a groove. It is advantageous if the seal is tightened between the end face of the axially extending leg of the insulation and the shoulder of the outer bearing ring. In order to be able to position without difficulty between the two fly masses in connection with simple assembly and manufacturing errors, the conical or cross section between the bearing area of the second fly mass and the bearing. Advantageously, a ring of tapered insulation is arranged. In that case, at least one of the bearing and the support area may have a conical or tapered peripheral surface adapted to the insulating ring. In order to automatically compensate for accidental wear and to fully fix and hold the bearing in its receiving bore, a conical or tapered insulating ring with axial rebound in its narrowing direction Advantageously, a force is applied, whereby the insulating ring is clamped between the receiving bore and the corresponding bearing ring. In order to ensure a sufficient tightening of the insulation ring, the insulation ring can be slit open. The conical or tapered insulating ring may also have a seal for the bearing. This seal is formed as described above and is axially loaded by the energy storage element towards the end face of the bearing ring supporting the seal. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS As can be seen from FIG. 1, the device 1 for damping a rotational shock comprises a flywheel 2, which is divided into two flywheel masses 3,4. The flywheel mass 3 is fixed to a crankshaft 5 of an internal combustion engine (not shown) via a fixing screw 6. A friction clutch 7 is fixed to the fly mass 4 by means not shown. A clutch disk 9 is provided between the pressure plate 8 of the friction clutch 7 and the flywheel mass 4, and the clutch disk 9 is attached to an input shaft 10 of a transmission (not shown).
The pressure plate 8 of the friction clutch 7 is loaded toward the flywheel mass 4 by a disc spring 12 pivotally mounted on a clutch cover 11. By operating the friction clutch 7, the flywheel 2 of the input shaft 10 is interrupted by the flywheel mass body 4 and the input shaft 10. A shock absorber 13 and a sliding clutch 14 are provided between the two fly masses 3 and 4 in parallel thereto, and both allow relative movement between the two fly masses 3 and 4 to a certain extent. The two fly masses 3, 4 are supported via bearings 15 so as to be rotatable relative to each other. The bearing 15 includes a single-row ball bearing 16. The outer bearing ring 17 of the ball bearing 16 extends into the notch 18 or hole of the flywheel 4 and the inner bearing ring 19 extends axially away from the crankshaft 5 and projects into the notch 18. , Mounted on the cylindrical central addition 20 of the flywheel mass 3. The inner bearing ring 19 is mounted on the additional part 20 by a press fit and is axially clamped between the additional part 20 or the shoulder 21 of the flywheel 3 and the safety disk 22. The safety disk 22 is fixed to the end face 20 a of the additional portion 20 by screws 23. A thermal insulator 24 is provided between the outer bearing ring 17 and the flywheel mass 4, whereby the friction surface 4 of the flywheel mass 4 cooperating with the clutch disc 9 is provided.
The flow of heat from a to the ball bearings 16 is interrupted or at least reduced. This prevents overheating of the grease filling of the bearing as well as excessive thermal strain or unacceptable elongation of the bearing. Otherwise, excessive thermal strain as well as unacceptable elongation could lock the ball 16a between the inner and outer bearing rings. For receiving the insulation 24, the notch 18 of the flywheel 4 has a diameter which is greater than the diameter of the outer bearing ring 17, thereby creating a radial gap. The heat insulator 24 comprises two rings 2 having an L-shaped cross section.
5 and 26, each of which is attached to the outer bearing ring 17 from one side. The legs 25a, 26a of the rings 25, 26 having an L-shaped cross section cover the outer bearing ring 17. The radially inward legs 25b, 26b partially extend radially along the inner bearing ring 19 and are supported by the axially inner bearing ring 19, whereby the ball bearing 16 It is also useful as a seal. In order to ensure a sufficient seal of the ball bearing 16, the radially extending legs 25
b, 26b are loaded axially toward the end face of the inner bearing ring 19 by a power storage member comprising a disc spring 27, 28, respectively. The disc spring 27 is supported radially outward on the shoulder of a plate 30 which is connected to the second flywheel mass 4 via a bolt 29 and radially inward on the radial leg 25b of the ring 25. Loading end area. Similarly, a disc spring 28 is supported radially outward on the shoulder of the flywheel 4 and radially inward on the ring 2.
6 at the end region of the radial leg 26b. For mounting the rings 25, 26 and the ball bearings 16, in the embodiment shown in FIG. 1, the sleeve-like region of the ring is first pressed into the outer bearing ring 17 and then provided with the rings 25, 26. The ball bearing 16 may be press-fit into a hole or notch 18 in the flywheel mass 4.
The ball bearing 16 is fixed axially immovably to the mass body 4 by being inserted between the shoulder 31 and the plate 30 of the mass body 4 in the axial direction by inserting the rings 25 and 26 therebetween. The shock absorber 13 has two plates 30, 33 arranged on both sides of the flange 32.
Reference numerals 33 are non-rotatably connected to each other via bolts 29 at axial intervals. Separating bolts 29 also serve to fix both plates 30, 33 to mass 4. Board 3
A notch is provided in each of the flanges 0 and 33 and the flange 32, and a power storage member including a coil spring 34 is accommodated in the notch. This coil spring 34 acts against the relative rotation between the flange 32 and the two plates 30,33. The damping device 13 furthermore has a friction device 13a, which is effective over the possible relative rotation angles between the two flywheel masses 3,4. The friction device 13a is arranged in the axial direction between the plate 30 and the flywheel mass 3 and has a power storage element formed by a disc spring 35, which is composed of a plate 30 and a pressure ring 36. , Whereby a friction ring 37 arranged between the pressure ring 36 and the flywheel mass 3 is tightened. The force acting on the plate 30 by the disc spring 35 is supported by the ball bearing 16. The flange 32 forms an input for the shock absorber 13 and also forms an output for the slip clutch 14. The input part of the slip clutch 14 is formed by two plates 38, 39 provided at an axial interval, and the plates 38, 39 cannot rotate with respect to the flywheel mass. The annular plate 39 is fixed to the fly mass via rivets 40. An axial tongue 38a is integrally formed on the outer periphery of the plate 38.
8a is engaged in a notch 41 of the plate 39 to prevent the rotation of the plate 38 with respect to the plate 39. Both plates 3 in the axial direction
8, 39, an additional portion 42 in the radial direction of the flange 32
Has been tightened. Because of this, both plates 38,
39 are mutually compressed by a disc spring 43. For this purpose, the disc spring 43 bears on the flywheel mass 3 and loads the plate 38 towards the plate 39. In the area between the additional portions 42 of the flange 32, plates 38, 39 are provided.
Is provided with a notch which is axially aligned and accommodates a power storage member 44,
Reference numeral 4 serves as a terminal stopper of the additional portion 42 of the flange 32, thereby limiting the rotation angle of the slip clutch 14. In the embodiment shown in FIG. 2, the ball bearing 1 is likewise used for supporting the flywheel mass 4 on the flywheel mass 3.
16 are used, and this ball bearing is arranged similarly to the ball bearing 16 shown in FIG. The outer bearing ring 117 of the ball bearing 116 is provided with chamfers 117a, 117b, whereby the outer bearing ring 117 and the rings 125, 12 of insulating material axially covering it.
6 is formed. In this space, a seal composed of O-rings 145 and 146 is arranged. The O-rings 145 and 146 protect the bearing grease between the L-shaped rings 125 and 126 and the outer bearing ring 117 from being pushed out or exuding. Chamfers 117a, 117b and O-ring 14
5, 146 are mutually defined so that the O-rings are elastically deformed between the rings 125, 126 having an L-shaped cross section and the chamfered portions 117a, 117b of the ball bearing 116. As can be seen from FIG. 2, the thickness of the radial legs 125b, 126b of the rings 125, 126 having an L-shaped cross section is smaller than the thickness of the legs 125a, 126a extending in the axial direction. are doing. Seal nose 125c, 126c is integrally formed at the radial inner end of the leg 125b, 126b. In the embodiment shown in FIG. 3, a ring 225 made of a heat insulator having a conical or tapered cross section is disposed between the notch 218 of the flywheel mass body 4 containing the ball bearing 216 and the outer bearing ring 217. Have been. In this embodiment, both the outer peripheral surface and the inner peripheral surface of the ring 225 extend conically in the axial direction. It is also possible for only one of the peripheral surfaces to be formed so as to extend conically. The notch 218 is formed on the conical outer surface of the ring 225 and the outer surface of the outer bearing ring 217 is formed on the ring 2.
Fits 25 conical inner peripheral surfaces. The ring 225 of heat insulation is loaded by a disc spring 227 in the direction of narrowing in the axial direction, the disc spring 227 being supported by a plate 230 fixed axially to the flywheel mass 4. Ring 225 has a radially inwardly extending region 225
b, which seals the ball bearing 216 by being axially supported by a bearing ring 219 inside the ball bearing 216. In order to seal the other side of the ball bearing 216, a ring 226 of thermal insulation is provided, which is axially outer by the action of a coned disc spring 227 and the shoulder 2 of the flywheel 4 in the axial direction.
31. The ring 226 has a seal nose 226b, which is the inner bearing ring 2
19 is supported in the axial direction. In the embodiment shown in FIGS. 1 and 2, the disc springs 27, 28 are provided with radially extending sealing regions 25, 26.
b, 125b, 126b in the axially inner bearing ring 1
It is loading toward 9,119. Depending on the proper material selection, the radial legs 25b, 26b; 125 of the rings 25, 26;
b, 126b so that the rings 25, 26 are elastically deformed;
125 and 126 may be formed. The ring is thereby axially supported under preload on the bearing rings 19, 119 inside the ball bearings 16, 116. According to this means, the disc springs 27 and 28 can be omitted. In the above-described embodiment, the heat insulator was formed by an additional ring arranged between the second flywheel mass 4 and the ball bearings 16, 116, 216. However, in another embodiment (not shown), the heat insulator is connected to the ball bearing 1.
6,116,216 or outer bearing ring 17,1
17, 217 can also be mounted by injection or sintering, so that the heat insulator is effectively integral with the ball bearing. Similarly, a heat insulator can be attached to the peripheral surface of the notch 18, 118, 218. When using a bearing with a seal ring, as provided by the bearing manufacturer, the outer bearing ring 17 is provided with a notch 1 having a diameter larger than its outer diameter.
The ball bearing 16 can be pre-mounted on the flywheel mass body 4 by centering and holding it in the space 8 and filling the space between the notch 18 and the outer bearing ring 17 with plastic or artificial resin. is there.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a longitudinal 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. FIG. 3 is a partial sectional view of a third embodiment of the present invention. [Explanation of Signs] 1 Device for damping rotational shock, 2 Flywheel, 3,
4 Bounce mass, 4a friction surface, 5 crankshaft,
6 fixing screw, 7 friction clutch, 8 pressure plate,
9 clutch disc, 10 input shaft, 11 clutch cover, 12 disc spring, 13 shock absorber, 1
4 sliding clutch, 15 bearings, 16 ball bearings,
17 bearing ring, 18 holes, 19 bearing ring, 20 additional parts, 20a end face, 21 shoulder, 2
2 safety disk, 23 screws, 24 heat insulator, 2
5,26 ring, 25a, 26a, 25b, 26b
Legs, 27,28 disc springs, 29 bolts,
30 boards, 31 shoulders, 32 flanges, 33
Plate, 34 coil spring, 35 disc spring, 36 pressure ring, 37 friction ring, 38, 39 plate,
40 rivets, 41 notches, 42 additional parts, 43
Disc spring, 44 energy storage member, 117a, 117b
Chamfer, 145 O-ring

────────────────────────────────────────────────── ─── Continued on the front page (72) Inventor Wolfgang Like Baden-Buhl Amalie-Müller-Strasse 20 Germany (56) References JP-A-57-47019 (JP, A) JP-A-54-59549 (JP, A) Fully open sho 59-52254 (JP, U) Fully open sho 56-35922 (JP, U) Fully open sho 55-170524 (JP, U) (58) Fields investigated (Int. Cl. ⁷ , DB name) ) F16F 15/12-15/31

Claims (1)

(57) [Claims] At least two coaxially arranged via bearings and rotatable with each other restricted against the action of the shock absorber
One of the bounce masses, one of the bounce masses
A flywheel mass is connectable to the internal combustion engine and the other flywheel mass, a second flywheel mass is connectable to the input of the transmission and has a friction surface cooperating with the clutch disc. A torque transmission device having a means for absorbing or compensating for rotational shocks of the internal combustion engine, particularly torque fluctuations.
Means (24; 125; 126; 225; 226) for reducing the flow of heat from the friction surface (4a) to the bearing (15) are provided, the means being provided between the friction surface (4a) and the bearing (15). And a holding area (18, 118, 218) for the second flywheel mass (4) and a bearing (16, 11), formed of a compression-resistant insulation having an L-shaped cross section arranged at
6,216), characterized in that a unique seal for the bearing is provided on the radial legs of the L-shaped insulation. 2. The bearing is constituted by a rolling bearing (16, 116, 216) and a heat insulator (24; 125; 126; 22).
5,226) held by the second flywheel mass (4);
Bearing rings that cannot rotate with respect to the flywheel (17, 1
2. The torque transmitting device according to claim 1, wherein the torque transmitting device is provided between the flywheel mass and the seat for receiving a bearing of the flywheel mass. 4. 3. Insulator (24; 125, 126; 225, 226)
The torque transmitting device according to claim 1, wherein the torque transmitting device is made of plastic. 4. Insulator (24; 125, 126; 225, 226)
Is formed of a ceramic material.
The torque transmission device according to any one of the preceding claims. 5. 4. The torque transmitting device according to claim 1, wherein the thermal insulator is made of a duroplastic, in particular a phenoplastic, for example hard paper. 6. Insulator (24; 125, 126; 225, 226)
4. The torque transmitting device according to claim 1, wherein the torque transmitting device is formed of a thermoplastic, for example, polytetrafluoroethylene, polyamide or polyamideimide. 7. Insulator (24; 125, 126; 225, 226)
The torque transmitting device according to any one of claims 1 to 3, wherein is molded from fiber-reinforced polycarbonate. 8. One of the fly masses has an axial extension, which extends axially into the central cutout of the other fly mass, and a bearing is arranged between the extension and the cutout. And
A heat insulator (24; 125, 126; 225, 226) has a central notch (18, 118, 218) and a bearing (16, 1).
The torque transmission device according to any one of claims 1 to 7, wherein the torque transmission device is disposed between the torque transmission device and the torque transmission device. 9. One fly mass has a pin-shaped addition in the center, which pin-like extension protrudes into the notch of the other fly-mass and between the pin-shaped addition and the notch. 8. The torque transmitting device according to claim 1, wherein a bearing is arranged and the heat insulator is arranged between the pin-shaped additional portion and the bearing. 10. A second flywheel mass which can be connected to the input of the transmission has a central notch (18, 118, 218) and a bearing which is non-rotatably connected to this notch (18, 118, 218). 10. The torque transmitting device according to claim 1, wherein a heat insulator (24; 125, 126; 225, 226) is provided between the ring and the ring (17, 117, 217). 11. The inner bearing ring (19, 119, 219) of the bearing (16, 116, 216) is received in the additional part (20) and the outer bearing ring (17, 117, 217) has a central notch (18, 118). , 218) and thermal insulators (24; 125, 126; 225, 22).
11. The torque transmitting device according to claim 1, further comprising a second flywheel mass (6) held via (6). 12. The torque transmission device according to any one of claims 1 to 11, wherein the heat insulator is formed on the bearing by an injection method. 13. The torque transmission device according to claim 1, wherein the heat insulator is formed on the bearing by a sintering method. 14． The heat insulator (24; 125, 126) is used for the bearing (16, 125, 126).
116) 1 to 1 which are press-fitted over the same.
2. The torque transmission device according to claim 1, wherein: 15. A bearing (16) is received in one of the flywheel masses, and an outer bearing ring (17) is received in a notch (18) having a diameter larger than the outer diameter of the bearing ring (17) and the notch (18) 15. The torque transmitting device according to claim 1, wherein the space between the bearing ring and the plastic is pre-mounted by injection or injection of plastic. 16. Insulator (24; 125, 126; 225, 22
16. The torque transmitting device according to claim 1, wherein 6) simultaneously serves as a sealing element for the bearings (16, 116, 216). 17． Insulator (24; 125, 126; 225, 22
6) seals (25b, 26b, 125b, 126b, 225b, 2) for the bearings (16, 116, 216)
The torque transmitting device according to claim 1, wherein the torque transmitting device has 26b) in one piece. 18. The heat insulator (24; 125, 126; 225) is constituted by at least one ring (25, 26) having an L-shaped cross section, and this ring has one leg (25a, 26).
a; 125a, 126a, 225a) axially covers and grips one of the bearing rings (17, 117, 217) and the other leg (25b, 26b, 125b,
126b, 225b) and the other bearing ring (19, 11).
9, 219) in the radial direction.
The torque transmission device according to any one of claims 7 to 7. 19. L-shaped heat insulator (24; 125, 126; 22)
5) The radially extending legs (25b, 26b, 125)
b, 126b, 225b) extend at least partially radially over bearing rings (19, 119, 219) which are not axially covered by insulation. 19. The torque transmitting device according to claim 18, supported by a). 20. Two rings with an L-shaped cross section (25,
26; 125, 126), each of which is one of the bearing rings (17; 117).
20. The torque transmitting device according to claim 1, wherein the torque transmitting device is attached to one of the two members from one side. 21. Insulation ring having an L-shaped cross section (25, 26; 12
5, 126, 225) have radially inwardly directed legs (25b, 26b, 125b, 126b,
225b) and the outer bearing ring (17, 117,
21. The torque transmitting device according to claim 1, which is received at 217). 22. Insulation rings (25, 26; 125, 126, 22)
5) The radially extending legs (25b, 26b, 125)
b, 126b, 225b) are axially stored in the energy storage devices (27, 2).
22. The torque transmitting device according to claim 1, wherein the torque transmission is applied by a radial direction toward the bearing ring (19, 119, 219) not covered by the legs. 23. 23. The torque transmitting device according to claim 22, wherein the energy storage device is formed by a disc spring (27, 28, 227). 24. Belleville springs (27, 28) are supported radially outward on a second flywheel mass (4) that can be coupled to the input (10) of the transmission, and radially inward on the seal ring (25, 28). 26) Radial legs (25b, 26b)
22 or 2 in which the end regions of the two are axially loaded.
3. The torque transmission device according to 3. 25. The heat insulator (25, 26; 125, 126) has a sleeve-like area (25a, 26a; 125a, 126a), which area is the bearing (1) of one of the flywheel masses (4).
24. The torque transmitting device according to claim 22, wherein the torque transmitting device is press-fitted into a notch (18, 118) for receiving the torque transmitting device. 26. 26. The thermal insulator (24) is first mounted on the bearing (16, 116) and then pressed together with the bearing into the notch (18, 118) of one of the flywheel masses (4). Torque transmission device. 27. The sleeve-shaped area of the insulator that holds the bearing,
27. Viewed in the axial direction, having different thicknesses or diameter ranges, only the regions having the larger diameters or thicknesses are received in the bearing receiving recesses with a press fit.
The torque transmission device according to any one of claims 1 to 4. 28. The legs (12) of the L-shaped ring (125, 126) axially cover and grip one of the bearing rings (117).
The seal (145, 146) is provided between the bearing ring (117) and the bearing ring (117).
28. The torque transmission device according to any one of items 27 to 27. 29. 29. The torque transmitting device according to claim 28, wherein the seal is formed by an O-ring (145, 146). 30. The seal (145, 146) is a heat insulator (125, 1).
26), legs (125a, 126a) extending in the axial direction
3. An outer bearing ring (117) is received in a notch, e.g.
29. The torque transmission device according to 7 or 28. 31. End faces of the legs where the seal extends in the axial direction of the insulator;
30. A torque transmitting device according to claim 28 or claim 29, wherein the torque transmitting device is fastened between the shoulder of the outer bearing ring. 32. 2. The heat insulator is configured as a conical or conical heat insulation ring (225) in cross section between the holding area (218) of the second flywheel mass (4) and the bearing (216). 3. 32. The torque transmission device according to any one of items 31 to 31. 33. 32. The torque transmitting device according to claim 31, wherein the bearing (216) and / or the holding area (218) have a conical or cone-shaped peripheral surface adapted to the insulating ring (225). 34. 33. The torque transmitting device according to claim 31, wherein the heat insulating ring, which is conical or conical in cross section, is axially biased in a tapering direction. 35. 34. The torque transmitting device according to claim 31, wherein the insulating ring has a slit, that is, has an open circumference. 36. The heat insulation ring (225) has a seal (225b) for the bearing (216) in one piece and is constructed or arranged according to at least one of the claims 20 to 26. The torque transmission device according to any one of claims 1 to 4.