Damping mechanism

Abstract

Damping mechanism (4), comprising: a first body of revolution (2) with a pair of first inclined surfaces (21e, 22e) inclined with respect to a radial direction; a second body of revolution (3) arranged in such a way that it can rotate relative to the first body of revolution (2); a spring (41,42) which elastically connects the first body of revolution (2) to the second body of revolution (3) in one direction of rotation; and a spring seat (43,44) which is an element that supports an end region of the spring (41,42) and which provides a pair of second inclined surfaces (43d; 44d) which are inclined with respect to the radial direction and which are designed as sliding surfaces that can slide relative to the pair of first inclined surfaces (21e, 22e), wherein the pair of second inclined surfaces (43d, 44d) is arranged symmetrically, wherein the spring seat (43,44) has a seat main body (43c,44c), which is in contact with an end region of the spring (41,42) in the direction of rotation, has an outer support area (43a,44a) which extends in the direction of rotation from a radially outer area of ​​the seat main body (43c,44c), and having an inner support area (43b,44b) extending in the direction of rotation from a radially inner area of ​​the seat main body (43c,44c) and having the pair of second inclined surfaces (43d; 44d).

Description

[0001] The present invention relates to a damping mechanism.

[0002] A vehicle's drive train contains various devices for transmitting the power generated by an engine. Examples of such devices include coupling devices and flywheel assemblies. These devices employ a damping mechanism to dampen torsional vibrations (see, for example, patent documents 1 to 9). Patent literature 1: Japanese published patent publication no. JP H07 - 208 547 A Patent literature 2: Japanese published patent publication no. JP H09 - 242 825 A Patent literature 3: European published patent specification no. EP 0 763 673 B1 Patent literature 4: German patent application no. DE 44 44 196 A1 Patent literature 5: German publication no. DE 196 09 041 A1 Patent literature 6: German patent application no. DE 41 41 723 C2 Patent literature 7: German patent application no. DE 101 33 694 A1 Patent literature 8: German patent application no. DE 41 28 868 A1 Patent literature 9: German publication no. DE 100 23 113 A1

[0003] This type of damping mechanism comprises, for example, an input element, an output element, a plurality of springs that elastically connect the input and output elements in one direction of rotation, and spring seats for supporting the end sections of the springs. In such a case, the input and output elements are force transmission components.

[0004] In this damping mechanism, the input element rotates relative to the output element when force is applied to it. As a result, the springs between the input and output elements are compressed, damping torsional vibrations.

[0005] With a conventional damping mechanism, it is difficult to stabilize the function of a spring seat because the movement of the spring seat in a radial direction is not sufficiently limited. If the function of the spring seat is unstable, the vibration damping function of the damping mechanism is also unstable.

[0006] The object of the invention is to provide a damping mechanism that enables stabilization of the vibration damping performance.

[0007] This problem is solved by a damping mechanism according to claim 1. Advantageous embodiments of the invention are the subject of the dependent claims.

[0008] A damping mechanism according to one embodiment of the invention comprises a first rotating body, a second rotating body, a spring, and a spring seat. The first rotating body has a pair of first inclined surfaces inclined with respect to a radial direction. The second rotating body is arranged such that it can rotate relative to the first rotating body. The spring elastically connects the first rotating body to the second rotating body in one direction of rotation. The spring seat is an element that supports an end section of the spring and has a seat body, an outer support area, and an inner support area. The seat body is in contact with an end section of the spring in the direction of rotation. The outer support area extends in the direction of rotation from a radially outer region of the seat body.The inner support area extends in the direction of rotation from a radially inner region of the main seat body and features a pair of secondary inclined surfaces. This pair of secondary inclined surfaces is inclined with respect to a radial direction and designed as sliding surfaces that can slide relative to the pair of primary inclined surfaces. The pair of secondary inclined surfaces is symmetrical.

[0009] This damping mechanism stabilizes the function of the spring seat and enables stabilization of the vibration damping performance, as the second inclined surfaces of the spring seat can slide relative to the first inclined surfaces of the first rotating body.

[0010] In an advantageous embodiment of the damping mechanism, the first rotating body has a first housing area that accommodates the spring and the spring seat, and a second housing area whose shape is more constricted in an axial direction than that of the first housing area; wherein the first pair of the first inclined surfaces is formed in a constricted area of ​​the second housing area.

[0011] It is preferably provided that the first body of revolution has a first plate element, a second plate element attached to the first plate element and an annular housing space formed by the first plate element and the second plate element, which accommodates the spring and the spring seat; and that the first housing area and the second housing area are formed by the first plate element and the second plate element.

[0012] It is further preferred that the first plate element has an annular first inclined region with one of the first inclined surfaces of the pair of first inclined surfaces, a first side region extending outwards in a radial direction from an outer circumferential region of the first inclined region and able to slide relative to a side surface of the spring seat, and an annular region extending in an axial direction from an outer circumferential region of the first side region; and that the second plate element has an annular second inclined region with the other of the second inclined surfaces of the pair of second inclined surfaces and a second side region extending inwards in a radial direction from an outer circumferential region of the first inclined region, able to slide relative to a side surface of the spring seat and is attached to the cylindrical region.

[0013] Further advantages of other preferred embodiments and uses of the invention are explained below.

[0014] In conventional power transmission components within damping mechanisms, if the contact area between the input element and the spring seat is small, the surface pressure increases, causing rapid wear of a resin-based spring seat. Conversely, if a large contact area is ensured, the weight of the input element increases undesirably.

[0015] In a conventional damping mechanism, a friction generation mechanism is provided to increase vibration damping performance. This friction generation mechanism comprises a sleeve, a friction plate, and a conical spring. The sleeve is positioned so that it can rotate integrally with the input element. The friction plate is positioned so that it can rotate integrally with the output element. The conical spring lies axially between the sleeve and the input element and presses the sleeve and friction plate against the output element. When the input element rotates relative to the output element, the friction plate slides on the sleeve, generating frictional resistance in one direction of rotation. This frictional resistance causes hysteresis to develop between the input and output elements, effectively damping torsional vibrations.

[0016] To increase the vibration damping performance of the damping mechanism, it is sometimes necessary to increase the hysteresis torque generated by the friction mechanism. However, if the effective radius of the friction element is increased, the friction mechanism undesirably expands in a radial direction.

[0017] A flywheel assembly comprises, for example, a first flywheel, a second flywheel, and a damping mechanism. The first flywheel is fixed to a crankshaft of an engine. The damping mechanism elastically connects the first flywheel to the second flywheel in one direction of rotation. A ring gear is attached to the first flywheel to apply force to the crankshaft when the engine is started.

[0018] In a conventional flywheel assembly, however, one outer circumferential surface of the first flywheel must be machined, since the first flywheel is fitted into the ring gear. This increases the manufacturing costs of the flywheel assembly.

[0019] An increase in the machining effort required for positioning a ring-shaped element in a radial direction is undesirable due to the resulting higher manufacturing costs.

[0020] However, if the contact area between the input element and the spring seat is small in a conventional damping mechanism, the resin-made spring seat will wear out quickly.

[0021] An advantage of a further embodiment of the invention is the provision of a damping mechanism that can ensure a large force transmission area while avoiding increased weight.

[0022] An advantage of a further embodiment of the invention is the provision of a damping mechanism which can increase the vibration damping performance while avoiding an increase in size.

[0023] An advantage of a further embodiment of the invention is the provision of a power transmission component and a flywheel arrangement, enabling reduced manufacturing costs.

[0024] An advantage of a further embodiment of the invention is the provision of a damping mechanism that can reduce the wear of a spring seat.

[0025] A force transmission element of a damping mechanism of an advantageous embodiment is a part for transmitting force and comprises an annular main body region and a plate-like transmission region. The transmission region has a first projecting region extending radially outward from the main body region, and a second projecting region extending axially from a circumferentially oriented edge region of the first projecting region to a first side.

[0026] This force transmission element, for example, allows for an increase in the force transmission area of ​​the second projecting section because the second projecting section extends axially from the circumferentially oriented edge region of the first projecting section to a first side. Furthermore, since the transmission area is plate-like, an increase in the weight of the force transmission element can be prevented.

[0027] A damping mechanism according to a further embodiment of the invention comprises a first rotating body, a second rotating body, a first element, a second element, a first friction element, a second friction element, and a pressure body. The second rotating body is arranged such that it can rotate relative to the first rotating body. The first element is arranged such that it can rotate integrally with the first rotating body. The second element is arranged such that it can rotate integrally with the second rotating body. The first friction element is sandwiched axially between the first element and the second element and is arranged such that it can rotate relative to both the first and second elements.The pressure element presses the second element against the second rotating body in an axial direction.

[0028] This damping mechanism allows for an increase in the friction surface area because the first friction element is sandwiched axially between the first and second elements, and the second friction element is sandwiched axially between the first element and the rotating body. This allows the vibration damping performance of the damping mechanism to be increased without increasing the radial dimensions of the first and second friction elements.

[0029] Preferably, the damping mechanism further comprises: a spring that elastically connects the first body of revolution to the second body of revolution in the direction of rotation, wherein the first rotating body has an annular main body region with a notch provided in an inner circumferential region and a transmission region that projects outwards from the main body region in a radial direction and contacts the spring in the direction of rotation; wherein the first element has an annular first element main body that is arranged axially between the first friction element and the second friction element, and a projection that projects outwards from the first element main body in a radial direction and is inserted into the notch.

[0030] In a preferred embodiment of this damping mechanism, the second rotating element has an annular sliding area that slides relative to the second friction element; wherein the main body area is arranged in an axial direction essentially in the same position as the sliding area and in a radial direction essentially in the same position as an outside of the sliding area.

[0031] A force transmission component of a damping mechanism according to a further embodiment is a component for transmitting force and comprises a ring element and a plate element. The plate element has a disk-like main body area and a plurality of support projections that extend axially from the main body area and serve to position the ring element relative to the main body area.

[0032] This power transmission component allows for easy positioning of the ring element relative to the plate element, as the plate element has support projections. This means the ring element can be positioned simply by providing support projections, thus reducing manufacturing costs.

[0033] Furthermore, the manufacturing costs of a flywheel equipped with this power transmission component can also be reduced.

[0034] In the force transmission part of the damping mechanism according to this embodiment, it is preferred that the support projections are arranged on a radially inwardly pointing side of the ring element.

[0035] This power transmission component preferably further comprises: a fastening area that is arranged in a circumferential direction between adjacent support projections and serves to fasten the gear ring to the main body area.

[0036] In the force transmission part of the damping mechanism according to this design, it is preferred that the plate element has a recess which is formed as support projections on axially opposite sides of the main body area and is recessed in the axial direction.

[0037] Furthermore, a flywheel arrangement is preferred, comprising: a damping mechanism according to a preferred embodiment of the invention.

[0038] A damping mechanism according to a further embodiment of the invention comprises a first rotating body, a second rotating body, at least one spring, and a first spring seat. The second rotating body is arranged such that it can rotate relative to the first rotating body. The spring elastically connects the first rotating body to the second rotating body in one direction of rotation and is arranged such that it acts in series between the first and second rotating bodies. The first spring seat is rotatably arranged between the second rotating body and the first end section of the spring and rests against the second rotating body in one direction of rotation. The contact area between the first spring seat and the second rotating body is 250 mm². 2 or more.

[0039] This damping mechanism allows for a reduction in the wear of the first spring seat, as the contact area between the first spring seat and the second rotating body is 250 mm. 2 or larger. BRIEF DESCRIPTION OF THE DRAWINGS Fig. Figure 1 shows a flywheel arrangement in top view; Fig. 2 is a sectional view along line II-II of Fig. 1; Fig. Figure 3 shows a flywheel arrangement in top view; Fig. Figure 4 shows a flywheel arrangement in top view; Fig. 5 is a section view along line VV of Fig. 3; Fig. 6 is a section view along line VI-VI of Fig. 4; Fig. 7 (A) shows a first spring seat in top view and Fig. 7(B) is a sectional view of the first spring seat; Fig. 8(A) shows a second spring seat in top view and Fig. 8(B) is a sectional view of the first spring seat; Fig. 9 is a sectional view along line IX-IX of Fig. 3. DESCRIPTION OF EXECUTION FORMS Overall configuration

[0040] A flywheel arrangement 1 is described below using the Fig. 1, Fig. 2, Fig. 3, Fig. 4, Fig. 5, Fig. 6, Fig. 7, Fig. 8 to Fig. 9 explained. Fig. 2, Fig. 5 and Fig. Figure 6 shows an engine (not shown) on the left side and a gearbox (not shown) on the right side. The left side is described below. Fig. 2, Fig. 5 and Fig. 6 is designated as the “engine side” (example of the first side in axial direction) and the right side as the “gearbox side”.

[0041] How Fig. Figure 1 shows that the flywheel assembly 1 is a device for transmitting a force generated by the engine to the transmission via a clutch device (not shown). The flywheel assembly 1 comprises a first flywheel 2 (example of a first rotating body), a second flywheel 3 (example of a second rotating body), a damping mechanism 4, and a friction generating mechanism 5. First flywheel

[0042] The first flywheel 2 is an element that is subjected to a force generated by the engine and is attached to a crankshaft (not shown) of the engine by a bolt 28. The first flywheel 2 has a first plate 21, a second plate 22, a support element 23, and a thrust plate 26.

[0043] The first plate 21 has a first plate main body 21a, two first side regions 21b and a cylindrical region 21c, which extends in an axial direction from an outer circumferential region of the first plate main body 21a and the first side region 21b.

[0044] The first side regions 21b are regions that bulge outwards towards the motor beyond the first main plate body 21a and are manufactured, for example, by a compression molding process. The two side regions 21b are arranged equidistant in one direction of rotation. The first side regions 21b are configured and dimensioned to accommodate four spring seats 49 (explained later). An inclined surface 21e (example of a first inclined surface), inclined with respect to an axial direction, is formed on an inner circumferential region of the first side regions 21b. The inclined surface 21e can slide relative to a first inclined sliding surface 44d (explained later) of a first spring seat 44 and to a second inclined sliding surface 43d (explained later) of a second spring seat 43.

[0045] The second plate 22 is an annular element attached to a cylindrical area 21c and has a wide plate main body 22a, two second side areas 22b, an inner cylindrical area 22c, a plurality of support projections 22d and a plurality of recesses 22f.

[0046] The second side regions 22b are regions that bulge outwards towards the gear unit than the second main plate body 22a and are manufactured, for example, by a compression molding process. The two side regions 22b are arranged at an equal distance in one direction of rotation. The second side regions 22b are configured and dimensioned to accommodate four spring seats 49 (explained later). An inclined surface 22e (example of a first inclined surface), inclined with respect to an axial direction, is formed on an inner circumferential region of the second side regions 22b. The inclined surface 22e forms a pair with the inclined surface 21e and can slide relative to a first inclined sliding surface 44d (explained later) of the first spring seat 44 and to the second inclined sliding surface 43d (explained later) of the second spring seat 43.

[0047] Since the second side regions 22b face the first side regions 21b in an axial direction, the first side regions 21b and the second side regions 22b can form a relatively large space for the arrangement of the spring seats 49 in an outer circumferential region of the first flywheel 2. Since, as Fig. Figure 9 shows that an edge region of the first side regions 21b and an edge region of the second side regions 22b, pointing in a direction of rotation, can come into contact with the first spring seat 44 in a direction of rotation. The first side regions 21b and the second side regions 22b support the first spring seats 44 in a direction of rotation. In the first flywheel 2, a support region 2a serves as a region that supports the first spring seat 44 in a direction of rotation.

[0048] The support projections 22d extend from the second side regions 22b towards the gearbox and are produced, for example, by an embossing process. In addition to the support projections 22d, recesses 22f, which are pressed in towards the gearbox, are formed on the side axially opposite the support projections 22d. The support projections 22d are arranged at equal intervals in a circumferential direction, and the recesses 22f are also arranged at equal intervals in a circumferential direction. The inner cylindrical region 22c is a cylindrical region that extends from an inner circumferential region of the second main plate body 22a towards the motor and abuts a sealing ring 38 (explained later).

[0049] The support element 23 has an annular support element main body 23a, an annular projection 23b, and an annular sliding area 23c. The support element main body 23a, together with the first plate 21, is attached to the crankshaft by the bolt 28. The annular projection 23b is an annular area that extends from an inner circumferential region of the support element main body 32a toward the engine and serves to position the first plate 21 in a radial direction. The sliding area 23c is an area that extends from the support element main body 32a in a radial direction and slides relative to a second rail 55 of the friction generating mechanism 5. A bearing 39 is mounted on an outer circumferential region of the support element main body 23.

[0050] The thrust plate 26 is an element that acts on the bearing 39 in an axial direction and is attached to the crankshaft by the bolt 28 together with the first plate 21 and with the support element 23. Second flywheel

[0051] The second flywheel 3 is an element arranged so that it can rotate relative to the first flywheel 2, and it has a second flywheel main body 31 and an output plate 33 (example of a power transmission part). The second flywheel 3 is held by the bearing 39 so that it can rotate relative to the first flywheel 2.

[0052] The second flywheel main body 31 is an annular element that is arranged on a gear side of the second plate 22 and has a support area 31a and a friction area 31b.

[0053] The support area 31a is an annular area supported by the bearing 39 so that it can rotate relative to the first flywheel 2 and is arranged radially inside the second support plate 22. A sealing ring 38 sits in a groove 31c of the support area 31a. The sealing ring 38 serves to seal the housing chamber S of the first flywheel 2 against a space outside the first flywheel 2. The housing chamber 2 is filled with lubricating oil. The output plate 33 is fastened to the support area 31a by rivets 32.

[0054] The friction area 31b is an annular area against which a friction lining (not shown) of a clutch disc assembly is pressed and is provided on an outer circumferential area of ​​the support area 31a. The friction area 31b is arranged on a transmission side of the second plate 22 and is bulged closer to the transmission than the support area 31a.

[0055] The output plate 33 is arranged in the housing space S and fixed to the support area 31a. The output plate 33 has an annular main body area 33a and two transmission areas 33e, which extend radially from the main body area 33a.

[0056] The main body section 33a is an annular area fixed to the support section 31a. A plurality of notches 33d are formed in an inner circumferential region of the main body section 33 and arranged at equal intervals in a circumferential direction. Projections 52b of a second friction plate 52 are inserted into the notches 33d. This allows the second friction plate 52 and the second flywheel 3 to rotate as an integral unit.

[0057] The transmission areas 33e are areas to which force transmitted to the first flywheel 2 is transferred via the four spring seats 49, each having a first projecting area 33c and a pair of second projecting areas 33b. The first projecting area 33c and the second projecting areas 33b are manufactured, for example, by a press forming process.

[0058] The first projecting region 33c is a plate-like area that projects radially outward from the main body region 33a. The first projecting region 33c has a central region 33h (example of the first projecting main body region) that is axially aligned with the main body region 33a, and a pair of outer regions 33i that bulge axially further outward than the central region 33h toward the gearbox. The pair of outer regions 33i are arranged in a rotational direction on both sides of the central region 33h.

[0059] The second projecting areas 33b are areas that extend axially from the rotationally oriented edge areas of the first projecting area 33c (in particular the outer areas 33i) towards the motor and each have a contact area 33f and a reinforcement area 33g. The contact area 33f is an area that extends radially and has a contact surface 33j that can come into contact with the first spring seat 44 (explained later) in a direction of rotation. The thickness direction of the contact area 33f (the direction of the line perpendicular to the contact surface 33j) is essentially the same as the direction of rotation.The reinforcement area 33g is an area that connects a radially inner end region of the contact area 33f with an outer circumferential area of ​​the main body area 33a and extends from the radially inner end region of the contact area 33f to a side facing the contact surface 33. As in . Fig. 3 and Fig. As shown in Figure 4, the reinforcement area 33g has a curved section. An axial dimension of the reinforcement area 33g is the same as an axial dimension of the contact area 33f. Since the outer sections 33i are curved further outwards towards the gearbox than the central section 33h, the axial dimension L of the contact area 33f can be comparatively large. This also allows for a large area of ​​the contact surface 33j. In particular, the contact area between the contact area 33f and the first spring seat 44 is 250 mm². 2 or more. Damping mechanism

[0060] The damping mechanism 4 is a mechanism that elastically connects the first flywheel 2 to the second flywheel 3 in one direction of rotation and has eight spring groups 49, four first spring seats 44 and six second spring seats 43. The damping mechanism 4 includes the first plate 21, the second plate 22 and the output plate 33, which have already been described.

[0061] The spring groups 49 have first springs 41 and second springs 42. The second springs 42 are arranged inside the first springs 41 such that they act in parallel. The four spring groups 49 are arranged in a pre-compressed state in a first housing section B1, which is formed by the first side sections 21b, the second side sections 22b, and the cylindrical section 21c, such that they can operate in series. In this state, the first spring seats 44, which are arranged between the spring seats 49 and the transmission sections 33e, contact the rotationally oriented edge regions of the first side sections 21b and the rotationally oriented edge regions of the second side sections 22b in one direction of rotation.

[0062] In particular, the first spring seats 44 each have a seat body 44c, a first outer support area 44a, and a first inner support area 44b. The first seat body 44c supports an end region of a spring assembly 49 in a direction of rotation. The first outer support area 44a is a region that extends in a direction of rotation from a radially outer region of the first seat body 44c and serves to support an end region of a spring assembly 49 in a radial direction. The first outer support area 44a can slide relative to the cylindrical region 21c of the first plate 21.

[0063] The first inner support areas 44b are areas that extend in a direction of rotation from radially inner areas of the first seat main bodies 44c and serve to support the end areas of the spring assemblies 49 in a radial direction. The first inner support areas 44b and the first outer support areas 44a support the end areas of the spring assemblies 49 not only in a radial direction but also in an axial direction.

[0064] The first inner support areas 44b are shorter in one direction of rotation than the first outer support areas 44a. Each of the first inner support areas 44b has a pair of first inclined sliding surfaces 44d (example of a second inclined surface) arranged symmetrically on axially opposite sides of the first inner support area 44b. The first inclined sliding surfaces 44d are inclined with respect to both the axial and radial directions and extend over the entire first inner support area 44b in the direction of rotation. For example, the first inclined sliding surfaces 44d are inclined at approximately 45 degrees with respect to one axis of rotation. The first inclined sliding surfaces 44d can slide relative to the inclined surfaces 21e.

[0065] The second spring seats 43 are arranged between spring assemblies 49. In particular, each second spring seat 43 has a second seat body 43c, a second outer support area 43a, and a second inner support area 43b. The second seat body 43c supports the end regions of spring assemblies 49 in one direction of rotation. The second outer support area 43a is a region that extends in both directions of rotation from a radially outer region of the second seat body 43c and serves to support the end regions of the spring assemblies 49 in a radial direction. The second outer support area 43a can slide relative to the cylindrical region 21c.

[0066] The second inner support area 43b is an area extending from a radially inner area of ​​the second seat main body 43c in both radial directions and serves to support end regions of the spring assemblies 49 in a radial direction. The second inner support area 43b and the second outer support area 43a support end regions of the spring assemblies 49 not only in a radial direction but also in an axial direction.

[0067] The second inner support areas 43 are shorter in one direction of rotation than the second outer support areas 43a. Each of the two inner support areas 43b has a pair of second inclined surfaces 43d (example of a second inclined surface) arranged symmetrically on axially opposite sides of the second inner support area 43b. The second inclined sliding surfaces 43d are inclined with respect to both the axial and radial directions and extend over the entire second inner support area 43b in the direction of rotation. For example, the second inclined sliding surfaces 43d are inclined at approximately 45 degrees with respect to one axis of rotation. The second inclined sliding surfaces 43d can slide relative to the inclined surfaces 21e.

[0068] The spring assemblies 49, the first spring seats 44, and the second spring seats 43 are housed in the housing space S of the first flywheel 2. Specifically, the first spring assemblies 49, the first spring seats 44, and the second spring seats 43 are located in a first housing region B1, which is formed by the first side regions 21b, the cylindrical region 21c, and the second side regions 22b. The aforementioned pair of inclined surfaces 21e is formed in the second housing region B2, which is more constricted in an axial direction than the first housing region B1. Consequently, the first spring seats 44 and the second spring seats 43 are arranged in the first housing region B1 such that they can rotate in one direction when their movement relative to the first flywheel 2 is restricted in both an axial and a radial direction. Friction generation mechanism

[0069] The friction generation mechanism 5 is a mechanism for generating a resistance force in one direction of rotation between the first flywheel 2 and the second flywheel 3 and comprises a first friction plate 53, a second friction plate 52, a first sleeve 54, a second sleeve 55 and a conical spring 51.

[0070] The first friction plate 53 is designed in such a way that it can rotate integrally with the first flywheel 2, and it is arranged on the motor side of the first sleeve 54.

[0071] The second friction plate 52 is designed such that it can rotate integrally with the second flywheel 3, and it has an annular plate body 52a (example of a main body of a first element) and a plurality of projections 52b that extend radially outwards from the plate body 52a. The plate body 52a is arranged axially between the first sleeve 54 and the second sleeve 55 and can slide relative to the first sleeve 54 and second sleeve 55. The projections 52b are inserted into the aforementioned notches 33d.

[0072] The first sleeve 54 is axially sandwiched between the first friction plate 53 and the second friction plate 52 and arranged so that it can rotate relative to the first flywheel 2 and the second flywheel 3. The second sleeve 55 is axially sandwiched between the second friction plate 52 and the sliding area 23c and arranged so that it can rotate relative to the second friction plate 52 and the first flywheel 2. The conical spring 51 is axially arranged between the first friction plate 53 and the first plate 21 and presses the first friction plate 53 towards the transmission. Operating mode

[0073] When the clutch disc assembly is pressed against the second flywheel 3, force is transmitted from the engine to the transmission and the clutch disc assembly via the flywheel 1. This means, in particular, that the rotation of the first flywheel 2 relative to the second flywheel 3 begins in a rotational drive direction. This initially compresses the spring assemblies 49 between the first flywheel 2 and the second flywheel 3. Specifically, the spring assemblies 49 are compressed in a rotational direction by the first flywheel 2 and the transmission area 3e of the second flywheel 3. Since the end regions of the spring assemblies 49 are covered by the first spring seats 44 and the second spring seats 43, sliding of the end regions of the spring seats 49 on the first flywheel 2 is prevented.

[0074] When the first flywheel 2 rotates relative to the second flywheel 3, frictional resistance is generated in the friction generation mechanism 5. Since the second friction plate 52 rotates relative to the first friction plate 53, the first sleeve 54 slides relative to the first friction plate 53 or the second friction plate 52. Furthermore, since the sliding area 23c of the support element 23 rotates relative to the second friction plate 52, the second sleeve 55 slides relative to the second friction plate 52 or the sliding area 23c. Consequently, resistance (e.g., a hysteresis torque) is generated in one direction of rotation between the first flywheel 2 and the second flywheel 3.

[0075] As the first flywheel 2 continues to rotate relative to the second flywheel 3, the first outer support area 44a of the first spring seat 44 and the second outer support area 43a of the second spring seats 43 come into contact with each other in one direction of rotation. This causes the first spring seat 44 and the second spring seat 43 to be wedged between the transmission area 33e and the support area 2a of the first flywheel 2, and the relative rotation of the first flywheel 2 and the second flywheel 3 is stopped. As a result, force is transmitted from the first flywheel 2 to the second flywheel 3 via the first spring seats 44 and the second spring seats 43. Distinguishing features

[0076] The characteristic features of the flywheel arrangement described above are set out below. (1-1)

[0077] Since the second projecting areas 33b of this starting plate 33 extend axially from a circumferentially oriented edge region of the first projecting area towards the motor, for example, a surface area of ​​the contact surface 33j of the second projecting area 33 can be made large. This reduces the wear of the second projecting area 33b and the first spring seats 44 (which are in contact with the second projecting area 33b). (1-2)

[0078] Since the contact areas 33f and the main body area 33a are connected by the reinforcement areas 33g in this output plate 33, the stability of the entire transmission area 33e can be increased. (1-3)

[0079] Since the reinforcement areas 33g are curved in this starting plate 33, the stress cannot easily concentrate in the reinforcement areas 33g, thus preventing damage to the second protruding areas 33b. (1-4)

[0080] Since the reinforcement areas 33g of this starting plate 33 extend to where the contact surfaces 33j face each other, a tensile force – not a compressive force – acts on the reinforcement areas 33g during force transmission through the transmission areas 33e. This increases the overall stability of the projecting areas and the transmission areas 33e. (1-5)

[0081] With this starting plate 33, a large force transmission area can easily be ensured, since the thickness direction of the contact areas 33f is essentially the same as the direction of rotation. (1-6)

[0082] Since, in this output plate 33, the outer areas 33i of the first projecting area 33c are more bulged towards the gearbox than the central area 33h, the second projecting areas 33b, which extend axially from edge areas of the outer areas 33i towards the motor, can have larger dimensions in an axial direction. This means that the surface areas of the contact surfaces 33j of the transmission area 33e can be enlarged even further. (1-7)

[0083] Since such an output plate 33 is used in the flywheel 1, a large power transmission area can be ensured, and the wear of the first spring seats 44 can be reduced. (2-1)

[0084] In this damping mechanism 4, the friction surface can be increased because the first sleeve 54 is sandwiched axially between the first friction plate 53 and the second friction plate 52, and the second sleeve 55 is sandwiched between the first friction plate 53 and the second flywheel 3. This increases the vibration damping performance of the damping mechanism. (2-2)

[0085] Since in this damping mechanism 4 the projections 52b of the second friction plate 52 are inserted into the notches 33d of the output plate 33, an arrangement can be achieved with structurally simple means in which the second friction plate 52 rotates integrally with the second flywheel 3. (2-3)

[0086] Since in this damping mechanism 4 the sliding area 23c of the support element 23 is arranged radially inside the main body area 33a of the output plate 33, an arrangement can be achieved with structurally simple means in which the second sleeve 55 is sandwiched axially between the second friction plate 52 and the sliding area 23c. (3-1)

[0087] Since the second plate 22 of this initial plate 33 has a plurality of support projections 22d, the toothed ring 29 can be easily positioned relative to the second plate 22. This means that the toothed ring 29 can be positioned on the second plate 22 by means of simple support projections 22d, thereby reducing manufacturing costs. (3-2)

[0088] Since the support projections 22d of this initial plate 33 are arranged on a radially inwardly directed side of the toothed ring 29, it is possible to prevent the axial dimension of the second plate 22 from increasing due to the support projections 22d. (3-3)

[0089] Since the welding areas 29a are provided in the circumferential direction between adjacent support projections 22d on this starting plate 33, the toothed ring 29 can be arranged and fastened in a small space. (3-4)

[0090] In this output plate 33, the increase in weight caused by the support projections 22d can be reduced, since the second plate 22 has recesses 22f which are provided on the motor side of the support projections 22d. (3-5)

[0091] With this flywheel arrangement 1, the manufacturing costs can be reduced, since the second flywheel 3 has such an output plate 33. (4-1)

[0092] Since in this damping mechanism 4 the first inclined sliding surfaces 44d of the first spring seats 44 can slide relative to the inclined surfaces 21e, 22e of the first flywheel 2, the function of the first spring seats 44 is stable, and the vibration damping performance can be stabilized.

[0093] Since the second inclined sliding surfaces 43d of the second spring seats 43 can slide relative to the inclined surfaces 21e, 22e of the first flywheel 2, the function of the second spring seats 43 is also stable, and the vibration damping performance can be stabilized. (4-2)

[0094] Since in this damping mechanism 4 the pair of first inclined sliding surfaces 44d is formed on a first inner support area 44b extending in one direction of rotation, the length of the first inclined sliding surfaces 44d in one direction of rotation can be made larger and the function of the first spring seats 44 can be better stabilized.

[0095] Since the pair of second inclined sliding surfaces 43d is formed on a second inner support area 43b extending in a direction of rotation, the length of the second inclined sliding surfaces 43d can also be made larger and the function of the second spring seats 43 can be better stabilized. (4-3)

[0096] Since in this damping mechanism 4 the pairs of inclined surfaces 21e and 22e are formed in a narrowed area of ​​the second housing region B2, the axial dimension of the second housing region B2 can be shortened and the function of the first spring seats 44 and the second spring seats 43 can be stabilized. (4-4)

[0097] Since in this damping mechanism 4 the first housing area B1 and the second housing area B2 are formed by the first plate 21 and the second plate 22, the first housing area B1 and the second housing area B2 can be designed in a simple manner. (4-5)

[0098] In this damping mechanism 4, the first spring seats 44 and the second spring seats 43 are guided in one direction of rotation, since the first spring seats 44 and the second spring seats 43 are supported in an axial direction and in a radial direction by the first side regions 21b, the cylindrical region 21c and the second side regions 22b. With this configuration, the function of the first spring seats 44 and the second spring seats 43 is stable in one direction of rotation. (5-1)

[0099] With this damping mechanism 4, the wear of the first spring seats 44 can be reduced, since a contact area between the second projecting areas 33b (especially the contact areas 33f) of the first flywheel 2 and the first spring seats 44 is at least 250 mm². 2 amounts. (5-2)

[0100] In this damping mechanism 4, a stop mechanism that limits a relative rotation angle between the first flywheel 2 and the second flywheel 3 can be achieved with the first spring seat 44 and the second spring seats 43. Other embodiments

[0101] The present invention is not limited to the embodiments described above. Various variations and modifications are possible without departing from the scope of protection of the present invention. (1)

[0102] Although in the embodiment described above the second projecting areas 33b extend axially from the first projecting area 33c towards the motor, it is acceptable if the second projecting areas 33b extend axially from edge regions of the first projecting areas 33c both towards the motor and towards the gearbox, provided that the entire first projecting area 33c is arranged in the same position axially as the main body area 33a. In this way, the overall stability of the transmission areas 33e can be increased. (2)

[0103] Although in the embodiment described above a flywheel arrangement 1 is specified as a device having the output plate 33, it is acceptable if the device having the output plate is another device that serves to transmit power.

[0104] The present invention is useful in the field of devices for power transmission. REFERENCE NUMBERS 1 Flywheel assembly 2 first flywheel 21 first record 21a first plate body 21b first page area 21c cylindrical section 21e inclined surface (example of the first inclined surface) 22 second plate (example of the plate element) 22a second plate body 22b second page area 22c inner cylindrical area 22d support projection 22e inclined surface (example of the first inclined surface) 22f Exclusion 23 Support element 23a Support element main body 23b ring-shaped protrusion 23c Glide range 29 Toothed ring (example of the ring element) 3 second flywheel 31 second flywheel main body 32 rivets 33 Output plate (example of the power transmission part) 33a Main body area 33b second projecting area 33c first projecting area 33d notch 33e Transmission range 33f Contact area (example from the first section) 33g amplification range (example from the second section) 33h Central area (example of the main body of the first projecting area) 33i Outdoor area 33j contact area 4 Damping mechanism 41 first spring 42 second spring 43 second spring seat 43a second external support area 43b second inner support area 43c Main body of the second seat 43d second inclined sliding surface (example of the second inclined surface) 44 first spring seat 44a first external support area 44b first internal support area 44c Main body of the first seat 44d first inclined sliding surface (example of the second inclined surface) 5 Friction generation mechanism 51 Conical spring (example of the pressure part) 52 Second friction plate (example of the second element) 52a Plate main body (Example of the main body of the first element) 53 First friction plate (example of the first element) 54 first sleeve (example of the first friction element) 55 second sleeve (example of the second friction element) S housing space B1 first housing area B2 second housing area

Claims

[1] Damping mechanism (4), comprising: a first body of revolution (2) with a pair of first inclined surfaces (21e, 22e) inclined with respect to a radial direction; a second body of revolution (3) arranged in such a way that it can rotate relative to the first body of revolution (2); a spring (41,42) which elastically connects the first body of revolution (2) to the second body of revolution (3) in one direction of rotation; and a spring seat (43,44) which is an element that supports an end region of the spring (41,42) and which provides a pair of second inclined surfaces (43d; 44d) which are inclined with respect to the radial direction and which are designed as sliding surfaces that can slide relative to the pair of first inclined surfaces (21e, 22e), wherein the pair of second inclined surfaces (43d, 44d) is arranged symmetrically, wherein the spring seat (43,44) has a seat main body (43c,44c), which is in contact with an end region of the spring (41,42) in the direction of rotation, has an outer support area (43a,44a) which extends in the direction of rotation from a radially outer area of ​​the seat main body (43c,44c), and having an inner support area (43b,44b) extending in the direction of rotation from a radially inner area of ​​the seat main body (43c,44c) and having the pair of second inclined surfaces (43d; 44d). [2] Damping mechanism (4) according to claim 1, wherein the first rotating body (2) has a first housing area (B1) which accommodates the spring (41,42) and the spring seat (43,44), and a second housing area (B2) whose shape is more constricted in an axial direction than that of the first housing area (B1); and wherein the first pair of the first inclined surfaces (21e, 22e) is formed in a constricted area of ​​the second housing area (B2). [3] Damping mechanism (4) according to claim 2, wherein the first rotating body (2) has a first plate element (21), a second plate element (22) attached to the first plate element (21) and an annular housing space (S) formed by the first plate element (21) and the second plate element (22) and accommodating the spring (41,42) and the spring seat (43,44); and wherein the first housing area (B1) and the second housing area (B2) are formed by the first plate element (21) and the second plate element (22). [4] Damping mechanism (4) according to claim 3, wherein the first plate element (21) has an annular first inclined region with one of the first inclined surfaces (21e) of the pair of first inclined surfaces (21e, 22e), a first side region (21b) extending outwards in a radial direction from an outer circumferential region of the first inclined region and able to slide relative to a side surface of the spring seat (43, 44), and an annular region extending in an axial direction from an outer circumferential region of the first side region (21b);and wherein the second plate element (22) has an annular second inclined region with the other first inclined surface (22e) of the pair of first inclined surfaces (21e, 22e) and a second side region (22b) which extends inwards in a radial direction from an outer circumferential region of the first inclined region, can slide relative to a side surface of the spring seat (43, 44) and is attached to the cylindrical region.

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