JP4235939B2 - Torsional vibration damper - Google Patents

Description

The present invention includes a primary side of a drive side, a secondary side that is pivotally supported with respect to the primary side, and an elastic device that connects the primary side and the secondary side to each other. The present invention relates to a torsional vibration damper having a drive-side power transmission part through an interaction between the primary side and a primary side, and a driven side power transmission part through an interaction between the primary side and an elastic device.

  Such torsional vibration dampers are well known from the prior art, in which many embodiments of these vibration dampers are each adapted to special requirements. A known disadvantage of all these torsional vibration dampers is that once a structural design is selected, it is extremely difficult to adapt it to different structural given conditions, especially other types of vehicles. That is the point. As a rule, new designs of torsional vibration dampers are required, so that new tools have to be prepared, in particular for sheet metal processing, in particular.

  The object of the present invention is to avoid the above disadvantages.

  In order to solve the above-mentioned problems, the present invention provides a drive-side power transmission portion through the interaction between the drive device and the primary side in the central member, while the driven-side power transmission through the interaction between the primary side and the elastic device. A torsional vibration damper of the kind described at the beginning is proposed, characterized in that the part is provided on the connecting member. In this case, according to the present invention, the central member and the connecting member form separate primary units fixedly coupled to each other.

  This arrangement has the advantage that, during manufacturing, only one of both units, and thus only the central member or the connecting member, must be adapted for structural adaptation. Thus, for example, one connecting member can be used for different central members, for example for cooperation with different crankshafts, so that no new tool needs to be prepared for the connecting member.

  However, changes made especially in the circumferential direction can also be realized by appropriate mutual displacement of the central member and the connecting member adapted to the given conditions. In addition, for example, the connecting member can be attached axially forward or axially rearward of the central member, which allows for the possibility of changes that allow structural adaptation without the need for new tools during manufacture. It is done.

  Further, as proved from the experiment, the vibration is excellently damped or canceled by the coupling between the central member and the connecting member. Therefore, even if the entire structure of the apparatus is the same, both power transmission parts are single. It has a more stable structure than an apparatus based on the prior art provided in one unit.

  Therefore, in actual use, for example, the driving force derived from the crankshaft of the engine, for example, is a driving side power transmission part, and thus via the central member to the connecting member, and thus the driven side power transmission part via the interaction between the primary side and the elastic device Is transmitted to. The force is further transmitted through this elastic device to the secondary side that functions as the driven side of the torsional vibration damper.

  From the prior art, multi-body primary bodies are known which have in particular a starter ring gear and a signal plate or central flange for indicating the radial position of the torsional vibration damper, but all these devices Basically, one integrated unit is responsible for receiving the force on the drive side radially inward and transmitting it radially outward to the elastic device, possibly with further units on the radially inner side. It is fixed to the power transmission part. However, there is no torque transmission joint between the two units that conduct the force from the radially inner side to the radially outer side.

  The central member and / or the connecting member is preferably formed as a plate forming member. In this case, the device according to the invention makes it possible to use various materials or members--for example, plate-formed members, forged members, etc .-- as central members or connecting members. The plate forming member is particularly suitable because the manufacturing cost is relatively low due to mass production. On the other hand, the device according to the invention has to be manufactured with very few other types of members, for example for prototype production, only one of them, especially as a plate-forming member, or otherwise. When it is necessary, it can be provided at low cost. In particular, the primary side consisting of two plate-molded members joined to each other that guide the force radially outward from the radially inner side through the coupling between the two plate-formed members is also suitable for separation from the other features of the present invention. is there.

  It is preferable that a single joint portion is provided directly between the central member and the connecting member to couple them together. However, in a separate embodiment, it is also possible to arrange one joint material between the two so that the joint material is coupled to both by one joint location. Similarly, if necessary, a plurality of joint materials may be provided.

  The joint location is preferably arranged radially outward of the drive side coupling between the central member and the drive device. With such an arrangement, the joint location does not prevent the normal connection of the central member to the drive device, for example the crankshaft of the motor vehicle.

  Therefore, it is preferable to arrange the joint portion on the radially inner side of the elastic device. This ensures that the joint location does not infringe or greatly infringe on the function of the elastic device. Furthermore, this makes it possible to arrange the joint location radially inside the spring chamber in which the spring is housed and the grease is arranged. The latter ensures that the joint location does not necessarily need to be anti-grease-formed, since the grease is basically arranged radially outward by centrifugal force.

  The joint location preferably has at least one connecting surface extending in the axial direction. In this case, different members can be fixed to the connecting surfaces extending in the axial direction at different axial positions. In this way, the torsional vibration damper according to the invention can be easily adapted to the given structural conditions, in particular in the axial direction.

  Therefore, it is preferable that each of the central member and / or the connecting member has one connection surface, and both are coupled to each other or the intermediate member via the surface. In this way, the configuration of the primary body can be easily realized as a sufficiently stable one.

  In this case, the connection surfaces may be positively formed with each other in the circumferential direction. This makes it possible to guarantee the mutual mutual alignment of both units easily and reliably. On the other hand, it is also preferable that the connecting surfaces are formed in a cylindrical shape or a conical shape in the circumferential direction and are aligned in proper coordination with each other. This allows the units to be linked to each other during assembly, thereby increasing the variability of the structural type that can be produced, even with the same production tool. It is particularly preferred that at least one of these connection surfaces is cylindrical, and thus axial, so that it can also be axially adapted during assembly.

  Thus, in a preferred embodiment, at least one connection surface is axially oriented. This is given anyway if it is a cylindrical connection surface, but such an axial orientation can be used for a connection surface that allows positive coupling or a connection surface with a variable spacing from the central axis of the torsional vibration damper. In some cases, both units can be easily displaced, with the favorable result that they can be connected to one another at different axial heights if necessary.

  In this case, the connection can be made, for example, by welding, soldering, caulking, flange splicing and / or riveting.

  The invention makes it possible to produce the central member and the connecting member with different materials, different methods and in particular different wall thicknesses. It is particularly preferable that the central member is formed thicker than the connecting member. This allows the central member to better absorb axial vibrations / impacts caused by the drive device, in particular, for example, the crankshaft of an internal combustion engine, so that the device has a single wall even with the same weight. It has a structure that is much more stable than a device composed of thickness. On the other hand, it is also possible to use a small press and a mold tool since only a thick material needs to be deformed by being punched out of a plate, for example, only for a central member having a small radius. From this it is possible to save considerable costs. This type of wall thickness difference has suitable advantages even when separated from other features of the present invention, in particular when separated from the multi-body formation of the primary torque transmission.

  A connecting member which is not so heavily loaded by this kind of axial vibration / impact can therefore be a conventional thin plate or a thinner plate. Furthermore, the connecting member, which is simply formed with the required wall thickness, offers space advantages, particularly in the axial direction, leaving many places for other units.

  In a preferred embodiment, the incrementer is integrally coupled with the primary torque transmission unit. An incrementer is understood in the context of the present invention as a unit used to indicate the torsion position of a torsional vibration damper, for example the torsion position of a crankshaft coupled with a torsional vibration damper. In particular, a typical automobile is usually provided with a sensor for detecting a twist position indicated by an incrementer. Thus, this type of incrementer has, for example, a magnet, ridge, bulge or similar signal sensed by the sensor, as is known from the prior art. This type of signal device is therefore provided directly in the primary torque transmission unit according to the invention. Such an incrementer can on the one hand simply emit a signal of various torsional positions by emitting a signal of a constant twist position, for example a dead point, or by regularly arranging the signalers. In this case, in particular, it is possible to generate both signals of a constant twist position and signals of various angular positions. This can be done, for example, by omitting any signal when placing the signals in the circumferential circuit at regular torsional angles, or by providing an auxiliary signal or special signal, exactly at that point- Otherwise, this can be achieved by having a specific twist position marked instead of only being issued a signal of a rotation angle increment.

  While the incrementer is integrated with the primary torque transmission unit, the manufacturing costs are significantly reduced, since there is no need for an additional unit for this purpose. By eliminating the need for such a unit, the position accuracy of the incrementer is further increased because the torque transmission unit of the torsional vibration damper is manufactured very precisely, while an additional unit such as an incrementer is provided. This is usually not the case for signal boards already for cost reasons. For this reason, the incrementer is also set very accurately directly in the proposed solution, but this is also not usually the case with conventional prior art incrementers or at a considerable cost. For example, it can be realized only by setting a signal board that requires a great deal of cost.

  To that extent, it is self-evident that an integral formation of this kind, in particular also a device consisting of a torsional vibration damper with an incrementer and the sensor, is suitable for being separated from the other features of the invention.

  The primary body torque transmission unit is preferably a plate forming member. In the case of a plate-shaped member, the signals required for the incrementer, such as bulges, depressions or protrusions, can be easily realized directly during manufacture.

  Therefore, this embodiment relates to a device in which the torque applied to the elastic device received by the drive side power transmission unit through the interaction between the drive device and the primary side is transmitted by the torque transmission unit of the primary body.

  In another preferred embodiment, it is proposed to arrange the incrementer on the starter ring gear or on the non-drive side or on the anti-crankshaft side of the elastic device. Similarly, as an additional or alternative, the incrementer can be arranged radially outside the elastic device. In addition or as an alternative, the incrementer can be arranged radially outside the secondary body. This allows the incrementer and possibly the sensor that interacts with it in a relatively simple manner to be arranged relatively far from the drive, which provides more space for the sensor and in particular disturbs the drive. Such as casing vibration, electrical or electromagnetic interference, etc. can be reduced.

  In another embodiment, it is proposed to place the incrementer in the radial direction, or in the radial direction, or on the radial projection. The incrementer may additionally or alternatively have an axially extending signal surface. This makes the incrementer relatively insensitive to axial shocks or vibrations due to, for example, the drive or clutch-in process. While torsional vibration dampers are typically set very accurately in the radial direction, disturbance disturbances can occur exclusively in the axial direction. In an apparatus known from the prior art, the incrementer acts in the axial direction, so that this type of axial disturbance affects the measurement accuracy. For this reason, for example, the sensor must have a sufficiently large spacing with respect to the incrementer, which is not the case with the present device. Since the influence of axial displacement on the measurement accuracy is only minor, the sensor can be installed much closer to the incrementer, for example, so that cheaper sensors can be used or more precise Will result in an inaccurate measurement.

  The incrementer preferably has radial grooves, bulges and / or protrusions, so that a radial arrangement can be realized very easily.

  For the reasons described above, the arrangement of the incrementer or the unity between the torque transmission unit and the incrementer is preferably separated from the other features of the present invention.

  In the torsional vibration damper according to the invention, it is preferred that the force is transmitted from the radially inner side to the spring damper device on the primary side, especially when the elastic device of the torsional vibration damper has a spring damper device. It is. This type of spring damper device is recognized when the device includes both elastic and frictional properties. This type of friction characteristic may be formed, for example, by friction between the wall surface and the spring. Also, hydrodynamic friction loss or a separate friction unit can be used to impart damping characteristics to the torsional vibration damper.

  In this type of torsional vibration damper in which the force is transmitted from the radially inner side to the spring damper device or elastic device on the primary side, the primary side does not need to transmit force or torque far away radially outward Therefore, a relatively light and inexpensive structure can be obtained. In particular, it is possible to abandon the torque transmission plate and simply provide a protective plate. This type of torsional vibration damper can be constructed from a different surface than previously known torsional vibration dampers, which-according to the overall arrangement-can achieve additional advantages, so that additional or different As a rule, structural advantages can be achieved. Furthermore, the heat load normally received by the primary side of this type of torsional vibration damper is far less than that of the secondary side. Thus, the thermally unloaded side of the elastic device is moved radially inward, and accordingly, the thermally loaded side is further radially outward. Since the mass distribution and the rotation speed are large on the outer side in the radial direction, the heat energy can be distributed in a large volume or a large mass to improve heat removal.

  It goes without saying that this type of device, in which the force is transmitted from the radially inner side to the spring damper device on the primary side, is also suitable to be disconnected from the other features of the torsional vibration damper according to the invention.

  Accordingly, in a torsional vibration damper having an anti-elastic device connecting surface having a surface element whose primary side faces the circumferential direction, it is additionally or separately arranged that at least a part of the connecting surface is arranged radially inside the elastic device. It is suitable as a method. This is especially true when a connecting surface with circular polygonal elements is used, which is suitably provided radially inward and arranged on the primary side.

  When the torsional vibration damper has a spring damper device and an auxiliary damper device, and the auxiliary damper device further has a friction body that frictionally interacts with the secondary side via the friction plate, the friction plate has a heat insulating material, particularly It is suitable as an additional or alternative method to be connected to the secondary side via an intermediate member.

  In this way, for example, thermal effects that are caused by the clutch-in process on the secondary side and can result in undesirable friction characteristic fluctuations can be avoided or significantly reduced. This is also the case when hydrodynamic or other effective damping is performed instead of the friction body.

  It is obvious that this type of thermal insulation can be used preferably even if it is separated from the other characteristics of the torsional vibration damper.

  Hereinafter, other advantages, features, and objects of the present invention will be described with reference to the accompanying drawings showing examples of various torsional vibration dampers.

  The torsional vibration damper 1 according to the present invention can be applied to, for example, a power train 2 of an automobile 3 as shown in FIG. In this case, this type of powertrain typically has an engine 4, which is operatively associated with a transmission 6 via a clutch 5 having a torsional vibration damper 1, and then through the transmission the appropriate torque is transmitted by a differential 7. It is transmitted to the drive wheel 8. It is obvious that this type of torsional vibration damper 1 can be suitably used for damping torsional vibrations in other devices. In particular, this type of torsional vibration damper can be provided in other parts of the power train 2 of the automobile 3.

  In this embodiment, the torsional vibration damper includes a primary side 10 on the driving side, a secondary side 20 that is pivotally supported with respect to the primary side, and an elastic device 12 that operatively connects the primary side 10 and the secondary side 11 to each other. Including. In this case, the secondary side 11 is a component of the clutch device including in particular the pressure plate 13 and the friction plate 14, and the pressure plate 13 is pressed against the friction plate 14 in order to realize the connection.

  In the embodiments described herein, the torsional vibration damper 1 basically includes an elastic device 12 including a plurality of spring damper devices 15 between the primary side 10 and the secondary side 12 via the spring damper devices. Most of the interaction is represented as a guaranteed device. Furthermore, this interaction is assisted by an auxiliary damper device 16 which performs an auxiliary vibration damping action. With respect to this, in these embodiments, there is provided an auxiliary damper device 16 that directly exerts a frictional action and also acts via hydrostatic and hydrodynamic effects. Similarly, the interaction between the primary side 10 and the secondary side 11 is influenced by a sliding bearing 17 which allows one torsional vibration freedom between both sides 10, 11 (see in particular FIGS. 2 and 3). ). Obviously, these individual elements can be omitted or replaced by elements that are similar in operation. Therefore, for example, a rolling bearing may be provided. Furthermore, a spring device that is directly damped by hydraulic pressure can be provided. Similarly, the damping can be basically realized by a hydraulic damping device. It can also be envisaged that an appropriate damping effect is achieved by the friction of the springs on the material surface.

  As shown in FIG. 2, in this embodiment, each individual spring damper device 15 includes two push pistons 18 that are pushed by one or more springs 19 in opposite directions. They are separated (representative examples are labeled). In this case, since the push piston 18 is in close contact with the primary side 10 on the one hand and the secondary side 11 on the other hand, the mutual relative movement from the rest positions of these two sides 10, 11 causes the compression of the spring 19. The energy of the system being absorbed by the push piston 18 as well as the auxiliary damper device 16, so that the torsional vibrations can be damped.

  On the primary side, the torsional vibration damper 1 is connected to the engine 4 through holes 20, and screws for fixing the torsional vibration damper 1 to the crankshaft of the engine 4 are inserted into these holes. It is obvious that this kind of central joint can also be provided for other power generators or torque generators.

  As shown as a representative example in FIG. 3, a friction surface 21 is provided on the secondary side, and the torsional vibration damper 1 interacts with the friction plate 14 via the friction surface. The clutches 13 themselves are fixed by holes 22 (see FIG. 3). It is obvious that this kind of connection to the fixed or friction plate may not be provided or may be provided at other places depending on the specific application case of the torsional vibration damper.

  Furthermore, the auxiliary damper device 16 in these embodiments has a body 23 made of a friction material, which interacts with the primary side 10 or the secondary side 11 respectively. This interaction takes place on the one hand by direct contact between the friction body 23 and the units connected to the primary side 10 to the secondary side 11 respectively. On the other hand, since the space containing the friction body 23 is filled with liquid, interaction due to hydrostatic pressure and dynamic fluid pressure also occurs.

  In the embodiment of the present invention, the embodiment shown in FIGS. 2 to 5 has a central member 24 that can be fixed to the drive shaft of the vehicle through the hole 20 together with the central flange 25. In this case, the central flange is used to form a bearing portion on which the secondary side 11 is supported. Drive side torque is transmitted to the primary side 10 via the central member 24. The central member 24 is provided with a connecting member 26 radially outward, and the member has a polygonal surface for interaction with the elastic device 12. In particular, as can be seen from FIG. 5, the central member and the connecting member are connected to each other via a welded joint portion 27. In this case, the central member 24 and the connecting member 26 are positively coupled in the radial direction. At this time, a connecting surface 28 extending in the axial direction is provided, and the connecting member 26 is connected to the central member 24 through this. On the other hand, it is possible to arrange them at different positions in the axial direction.

  Furthermore, since the connection surface 28 is provided so as to be rotationally symmetric with respect to the rotation axis because of the cylindrical shape, adaptation in the circumferential direction is possible.

  As can be readily seen, in this embodiment, force or torque is transmitted from the radially inner side to the elastic device 12 on the primary side. By such a method, it is possible to form the connecting member 26 thinner than in the conventional technique.

  The connecting member 26 carries a starter ring gear 29 and an additional body radially outward. This additional body simultaneously functions as an incrementer 30 and has a groove 31 as a signal device. As can be seen immediately, the incrementer is arranged on the counter drive side of the starter ring gear 29 in the axial direction. As can be readily seen, if the groove 31 extends relatively long in the axial direction so that the sensor 32 acts essentially in the radial direction, the sensor mechanism of this type of incrementer Axial influence obstacles can be avoided or reduced.

  On the secondary side, the embodiment shown in FIGS. 2 to 5 has a friction surface carrier 33 which in this embodiment interacts with the elastic device 12 via an intermediate member 34 riveted to the friction surface carrier 33. . This type of arrangement can ensure thermal insulation between the elastic device 12 and the friction surface carrier 33. Further, the auxiliary friction device 16 having a friction plate that performs a friction action or a damping action in cooperation with the friction body 23 and / or the liquid also acts on the friction surface carrier via the intermediate member 34. In order to improve the thermal insulation, a further hole 35 is provided, which results in an undercut or open space between the friction surface carrier 33 and the intermediate member 34 and thus forms a thermal insulation.

  In this embodiment, the central member 24, the central flange 25, the connecting member 26, and the intermediate member 24 are each manufactured as a plate-forming member, and therefore relatively inexpensive. In this case, the central member 24 that must be directly opposed to the torque of the drive device is formed to be the thickest. In particular, as can be seen immediately from FIG. 5, the connection point 27 between the connecting member 26 and the central member 24 is on the one hand radially inward of the elastic device 12 and on the other hand between the central member 24 and the drive device. It is provided on the radially outer side of the drive side coupling portion. On the other hand, the incrementer 31 is disposed radially outside the elastic device 12. Further, the friction body 23 is directly supported by the intermediate member 34 on the secondary side.

FIG. 6 shows a separate embodiment in place of the two-body secondary body, and in this embodiment is used for mechanical connection with the friction surface carrier 41 and the elastic device 19 and / or the auxiliary damper device 16. The connecting elements 42 are both combined into a single unit by the unit 40, in which case these two functional elements 41, 42 are thermally insulated by a thermal resistance 43 formed by one groove in this embodiment. Yes. This groove 43 reduces the heat transfer cross-sectional area on the one hand and enables rear ventilation on the other hand, and additionally provides thermal insulation, but this is also suitable as an alternative. can do. This kind of arrangement is relatively simple in structure since it is only necessary to provide a suitable groove 43 and this groove can be easily provided after the fact, for example. Such an integral formation eliminates the need for a separate manufacturing step for joining the friction surface carrier 41 and the intermediate member 42. Furthermore, such an arrangement is structurally relatively stable due to the integral connection. It goes without saying that this type of configuration can be suitably applied even when separated from the other features of the present invention.

  The embodiment shown in FIGS. 7 and 8 is also consistent with the embodiment shown in FIGS. This embodiment also has a central member 24 on the primary side, which is welded to the connecting member 26 at a connecting point 27 located radially inward of the elastic device 12. However, in this embodiment, the central member 24 formed to be relatively thick extends to the outside in the radial direction, so that it can be used as an additional body. Furthermore, this central member 24 is integrally connected with the incrementer 30, which is radially outward of the elastic device 19 and in this embodiment, with respect to the starter ring gear 29 and the elastic device 12. It is arranged on the axial drive side. In an alternative embodiment, the central member 24 can be integrally coupled with the starter ring gear while the incrementer is provided in the auxiliary unit.

  However, in the embodiment shown in FIGS. 7 and 8, the elastic device 12 and the auxiliary friction device 16 are connected to the friction surface carrier 33 by separate units 44 and 45. Particularly in this embodiment, the space containing the friction body 23 of the auxiliary damper device 16 is surrounded by different plates, which are connected to the primary side 10 or the secondary side 11 respectively. On the one hand, this can be done by welding, soldering and / or riveting. However, it has been found that coking is particularly stable, and in that case, a sealing material may be further provided in some cases. The plates may be sealed together on the one hand in a contact manner or on the other in a non-contact manner, in which case a labyrinth arrangement is preferred in the case of non-contact plates. A space in which the friction body 23 and / or the damper liquid is arranged can be formed by the wall surfaces of these plates or other primary or secondary units. Accordingly, the sealing measures are appropriately selected so that the space is sufficiently protected from the outflow of liquid and the intrusion of dust or similar particles according to the specific shape. It goes without saying that all the solutions shown in the embodiments in this connection can be used favorably apart from the other features of the embodiments shown here.

  The embodiment shown in FIGS. 7 and 8 thus realizes that the torque is brought to the elastic device 12 from the radially inner side on the primary side. Therefore, both the central member 24 and the connecting member 26 are provided. Furthermore, this arrangement also achieves thermal insulation via the intermediate member 45 with respect to the auxiliary damper device 16. Also in this embodiment, both the central member 24 and the connecting member 26 are formed as plate forming members, and the central member 24 is thicker than the connecting member 26.

In the embodiment of FIGS. 9 and 10, the central member 24 and the connecting member 26 are caulked together at a joint 27 and subsequently welded. In this embodiment, the intermediate member 50 is coupled to the friction surface carrier 33, which on the one hand interacts with the elastic device 12 from the radially inner side and on the other hand forms the eccentric 51 from the radially inner side, It interacts with the friction body 23. In this embodiment, the cover plate 39 is caulked with the connecting member 26 by using a sealing material, which can considerably simplify the assembly.

It is the figure which showed the powertrain of the motor vehicle. It is the figure which cut and showed the 1st torsional vibration damper by this invention partially. It is sectional drawing which cut | disconnected the torsional vibration damper of FIG. 2 by the III-III line. It is the figure which expanded and showed a part of cross section similar to FIG. 2 which cut | disconnected the torsional vibration damper shown to FIG. 2, 3 by the IV-IV line of FIG. It is sectional drawing which cut | disconnected the torsional vibration damper shown in FIGS. 2-4 by the VV line of FIG. It is the figure which showed separate embodiment which replaces with a 2 body type secondary body. It is sectional drawing similar to FIG. 4 which cut | disconnected the 3rd torsional vibration damper by the IX-IX line of FIG. 6 is a cross-sectional view similar to FIG. 5, wherein the torsional vibration damper of FIG. 7 is cut along line XX of FIG. It is sectional drawing similar to FIG. 4 which cut | disconnected the 6th torsional vibration damper by the XV-XV line | wire of FIG. FIG. 10 is a cross-sectional view similar to FIG. 5, wherein the torsional vibration damper of FIG. 9 is cut along line XVI-XVI of FIG. 9.

Claims (5)

A torsional vibration damper,
Preferably a drive side primary side fixed to the crankshaft;
A secondary side pivotally supported with respect to the primary side;
An elastic device for connecting the primary side and the secondary side to each other;
In the torsional vibration damper, the primary side includes a drive device such as a drive side power transmission unit through the interaction between the crankshaft and the primary side, and a driven side power transmission unit through the interaction between the primary side and the elastic device. The driving side power transmission part is provided in the central member, and the driven side power transmission part is provided in the connection member, and the central member and the connection member are coupled to each other to form separate primary units,
The torsional vibration damper includes a spring damper device and an auxiliary damper device, and the auxiliary damper device includes a friction body that frictionally interacts with the secondary side via a friction plate, and the friction plate passes through the intermediate member to the secondary member. Coupled to the side and thermally insulated by way of the intermediate member,
Torsional vibration damper, characterized in that thermal insulation is ensured by radial cuts (grooves). The torsional vibration damper according to claim 1 , wherein a joint portion is provided between the central member and the connecting member, and the joint portion has at least one connection surface extending in the axial direction.   The torsional vibration damper according to claim 2, wherein the central member and the connecting member each have one connecting surface extending in the axial direction. The center member and the connecting member each have one connection surface, and the connection surface is formed in a cylindrical shape or a conical shape in the circumferential direction. The torsional vibration damper according to item 1.   The torsional vibration damper according to any one of claims 1 to 4, wherein the central member is formed thicker than the connecting member.

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