Damping mechanism

Abstract

Damping mechanism (4), comprising: a first rotation body (2); a second rotary body (3) having a force transmission part (33) and arranged to rotate relative to the first rotary body (2); a spring which elastically connects the first rotational body (2) to the second rotational body (3) in a rotational direction and which is compressible between the first rotational body (2) and the transmission region (33e) of the force transmission part (33); and a spring seat (44) arranged between the first rotary body (2) and the transmission portion and supporting one end portion of the spring, wherein the force transmission part (33) configured to transmit force comprises: an annular main body portion (33a) and a plate-like transmission portion (33e) having a first projecting portion (33c) extending outwardly from the main body portion (33a) in a radial direction, and a pair of second projecting portions (33b) each extending axially toward a first side from a circumferentially facing pair of edge portions of the first projecting portion (33c), characterized in that the first projecting portion (33c) and the pair of second projecting portions (33b) are manufactured by a press-molding process, wherein the first projecting portion (33c) has a central portion (33h), which is arranged in an axial direction in the same position as the main body portion (33a), and has a pair of outer regions (33i) which bulge further in an axial direction than the central region (33h) towards a second side opposite the first side, wherein the pair of outer regions (33i) are arranged in a rotational direction on both sides of the central region (33h), wherein the pair of second projecting portions (33b) each extend in an axial direction from the pair of outer portions (33i) of the first projecting portion (33c) facing in the direction of rotation, wherein the pair of second projecting portions (33b) are arranged to face each other in the rotational direction without any other member being arranged between the pair of second projecting portions (33b).

Description

TECHNICAL FIELD

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

[0002] A vehicle's drive train incorporates various devices for transmitting the power generated by an engine. Examples of such devices include clutch devices and flywheel assemblies. These devices utilize a damping mechanism to dampen torsional vibrations (see, for example, Patent Documents 1 to 8). DOCUMENT LISTPATENT LITERATURE Patent Literature 1: Japanese Patent Laid-Open Publication No. JP H07 - 208 547 A Patent Literature 2: Japanese Patent Laid-Open Publication No. JP H09 - 242 825 A Patent Literature 3: European Patent Application Laid-Open No. EP 0 763 673 B1 Patent literature 4: German laid-open specification No. DE 44 44 196 A1 Patent literature 5: German laid-open specification No. DE 196 09 041 A1 Patent literature 6: German laid-open specification No. DE 199 58 811 A1 Patent literature 7: German laid-open specification No. DE 41 41 723 A1 Patent literature 8: German patent specification No. DE 198 82 160 B4 BRIEF SUMMARY OF THE INVENTION

[0003] This type of damping mechanism includes, for example, an input element, an output element, a plurality of springs that elastically connect the input element and the output element in a rotational direction, and spring seats for supporting the end portions of the springs. In such a case, the input element and the output element are power transmission parts.

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

[0005] However, in conventional power transmission components, if the contact area between the input element and the spring seat is small, the surface pressure increases, causing a spring seat made of resin to wear quickly. On the other hand, if a large contact area is ensured, the weight of the input element increases undesirably.

[0006] In a conventional damping mechanism, a friction generating mechanism is provided to increase vibration damping performance. The friction generating mechanism includes a sleeve, a friction plate, and a conical spring. The sleeve is arranged to rotate integrally with the input member. The friction plate is arranged to rotate integrally with the output member. The conical spring is axially interposed between the sleeve and the input member, pressing the sleeve and friction plate against the output member. When the input member rotates relative to the output member, the friction plate slides on the sleeve, generating frictional resistance in a rotational direction. The frictional resistance causes hysteresis to develop between the input member and the output member, effectively damping torsional vibrations.

[0007] To increase the vibration damping performance of the damping mechanism, it is sometimes necessary to increase the hysteresis torque generated by the friction generating mechanism. However, if the effective radius of the friction element is increased, the friction generating mechanism undesirably increases in a radial direction.

[0008] A flywheel assembly, for example, includes a first flywheel, a second flywheel, and a damping mechanism. The first flywheel is attached to a crankshaft of an engine. The damping mechanism elastically connects the first flywheel to the second flywheel in one rotational direction. A ring gear is attached to the first flywheel to apply force to the crankshaft when the engine is started.

[0009] However, in a conventional flywheel assembly, an outer peripheral surface of the first flywheel must be machined because the first flywheel is fitted into the ring gear. This increases the manufacturing cost of the flywheel assembly.

[0010] An increase in machining effort in the context of positioning an annular element in a radial direction is not desirable due to the resulting higher manufacturing costs.

[0011] Furthermore, with a conventional damping mechanism, it is difficult to stabilize the function of the 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 will also be unstable.

[0012] However, in a conventional damper mechanism, if a contact area between the input element and the spring seat is small, rapid wear of the resin-made spring seat will occur.

[0013] The object of the invention is to provide a damping mechanism that can ensure a large force transmission area while avoiding a higher weight

[0014] The problem is solved by the subject matter of the independent patent claim. Preferred developments are the subject matter of the dependent patent claims.

[0015] An idea of ​​the invention is to provide a damping mechanism that can increase the vibration damping performance while avoiding an increase in size.

[0016] Another idea of ​​the invention is to provide a damping mechanism that enables stabilization of the vibration damping performance.

[0017] Another idea of ​​the invention is to provide a damping mechanism that can reduce the wear of a spring seat.

[0018] A power transmission part according to a first aspect is a part for transmitting power and includes an annular main body portion and a plate-like transmission portion. The transmission portion has a first protruding portion extending outward from the main body portion in a radial direction and a second protruding portion extending from a circumferential edge portion of the first protruding portion to a first side in an axial direction.

[0019] This power transmission part, for example, enables an increase in the power transmission area of ​​the second protruding portion because the second protruding portion extends from the circumferential edge portion of the first protruding portion in an axial direction to a first side. Furthermore, since the transmission portion is plate-like, an increase in the weight of the power transmission part can be prevented.

[0020] A damper mechanism according to a second aspect includes 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 to rotate relative to the first rotating body. The first element is arranged to rotate integrally with the first rotating body. The second element is arranged to 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 to rotate relative to the first element and the second element. The first friction element is sandwiched between the first element and the second element and is arranged to rotate relative to the first element and the second rotating body.The pressure element presses the second element in an axial direction against the second rotation body.

[0021] This damping mechanism allows for an increase in the friction surface area because the first friction element is sandwiched axially between the first element and the second element, 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 friction element and the second friction element.

[0022] A power transmission part according to a third aspect is a part for transmitting power and includes a ring member and a plate member. The plate member has a circular disk-like main body portion and a plurality of support projections that protrude in an axial direction from the main body portion and serve to position the ring member relative to the main body portion.

[0023] This force transmission part allows for easy positioning of the ring element relative to the plate element, as the plate element has support projections. This means that the ring element can be positioned simply by providing support projections, thus reducing manufacturing costs.

[0024] In addition, the manufacturing costs of a flywheel equipped with this power transmission part can also be reduced.

[0025] A damper mechanism according to a fourth aspect includes 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 to be rotatable relative to the first rotating body. The spring elastically connects the first rotating body to the second rotating body in a rotational direction. The spring seat is a member that supports an end portion of the spring and has a pair of second inclined surfaces inclined with respect to a radial direction and slidable relative to the pair of first inclined surfaces.

[0026] This damping mechanism stabilizes the function of the spring seat and enables stabilization of the vibration damping performance because the second inclined surfaces of the spring seat can slide relative to the first inclined surfaces of the first rotating body.

[0027] A damping mechanism according to a fifth aspect 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 a rotational direction and is arranged such that it acts in series between the first rotating body and the second rotating body. The first spring seat is rotatably arranged between the second rotating body and the first end portion of the spring and abuts the second rotating body in a rotational direction. A contact area between the first spring seat and the second rotating body is 250 mm. 2 or more.

[0028] This damping mechanism allows a reduction in the wear of the first spring seat, since 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. 1 shows a flywheel arrangement in plan view; Fig. 2 is a sectional view along line II-II of Fig. 1; Fig. 3 shows a flywheel arrangement in plan view; Fig. 4 shows a flywheel arrangement in plan view; Fig. 5 is a sectional view along line VV of Fig. 3; Fig. 6 is a sectional view along line VI-VI of Fig. 4; Fig. 7 (A) shows a first spring seat in plan view and Fig. 7(B) is a sectional view of the first spring seat; Fig. 8(A) shows a second spring seat in plan 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 EMBODIMENTS Overall configuration

[0029] A flywheel arrangement 1 is described below with reference to Fig. 1 to 9. In Fig. 2, Fig. 5 and Fig. 6, an engine (not shown) is arranged on a left side and a transmission (not shown) on a right side. In the following, the left side is referred to as Fig. 2, Fig. 5 and Fig. 6 is called the “engine side” (example of the first side in axial direction) and the right side is called the “gearbox side”.

[0030] How Fig. As shown in Figure 1, the flywheel assembly 1 is a device for transmitting power generated by the engine to the transmission via a clutch device (not shown). The flywheel assembly 1 includes 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

[0031] The first flywheel 2 is an element that receives 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.

[0032] The first plate 21 has a first plate main body 21a, two first side portions 21b, and a cylindrical portion 21c extending in an axial direction from an outer peripheral portion of the first plate main body 21a and the first side portion 21b.

[0033] The first side portions 21b are portions that bulge outward toward the engine further than the first plate main body 21a and are formed, for example, by a press-forming process. The two side portions 21b are arranged at an equal pitch in a rotational direction. The first side portions 21b are configured and sized to receive 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 peripheral portion of the first side portions 21b. The inclined surface 21e can slide relative to a first inclined sliding surface 44d (explained later) of a first spring seat 44 and a second inclined sliding surface 43d (explained later) of a second spring seat 43.

[0034] The second plate 22 is an annular member fixed to a cylindrical portion 21c, and has a wide plate main body 22a, two second side portions 22b, an inner cylindrical portion 22c, a plurality of support projections 22d, and a plurality of recesses 22f.

[0035] The second side portions 22b are portions that bulge outward toward the transmission further than the second plate main body 22a and are formed, for example, by a press-forming process. The two side portions 22b are arranged at an equal pitch in a rotational direction. The second side portions 22b are configured and sized to receive 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 peripheral portion of the second side portions 22b. The inclined surface 22e pairs 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 the second inclined sliding surface 43d (explained later) of the second spring seat 43.

[0036] Since the second side portions 22b face the first side portions 21b in an axial direction, the first side portions 21b and the second side portions 22b can form a relatively large space for the arrangement of the spring seats 49 in an outer peripheral portion of the first flywheel 2. Since, as Fig. As shown in Figure 9, an edge portion of the first side portions 21b facing in a rotational direction and an edge portion of the second side portions 22b facing in a rotational direction can abut against the first spring seat 44 in a rotational direction. The first side portions 21b and the second side portions 22b support the first spring seats 44 in a rotational direction. In the first flywheel 2, a support portion 2a serves as a portion that supports the first spring seat 44 in a rotational direction.

[0037] The support projections 22d protrude from the second side portions 22b toward the transmission and are formed, for example, by a stamping process. In addition to forming the support projections 22d, recesses 22f, which are indented toward the transmission, 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 portion 22c is a cylindrical portion extending from an inner peripheral portion of the second plate main body 22a toward the engine and abutting a seal ring 38 (explained later).

[0038] The support member 23 includes an annular support member main body 23a, an annular projection 23b, and an annular sliding portion 23c. The support member main body 23a is fixed to the crankshaft together with the first plate 21 by the bolt 28. The annular projection 23b is an annular portion that protrudes from an inner peripheral portion of the support member main body 32a toward the engine and serves to position the first plate 21 in a radial direction. The sliding portion 23c is a portion that extends from the support member 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 peripheral portion of the support member main body 23.

[0039] The thrust plate 26 is an element which acts on the bearing 39 in an axial direction and which is fixed to the crankshaft together with the first plate 21 and the support element 23 by the bolt 28. Second flywheel

[0040] The second flywheel 3 is a member arranged to rotate relative to the first flywheel 2, and includes a second flywheel main body 31 and an output plate 33 (an example of a power transmission part). The second flywheel 3 is supported by the bearing 39 so that it can rotate relative to the first flywheel 2.

[0041] The second flywheel main body 31 is an annular member disposed on a transmission side of the second plate 22 and has a support portion 31a and a friction portion 31b.

[0042] The support portion 31a is an annular portion supported by the bearing 39 so that it can rotate relative to the first flywheel 2, and is arranged radially inward of the second support plate 22. A seal ring 38 is seated in a groove 31c of the support portion 31a. The seal ring 38 serves to seal the housing space S of the first flywheel 2 from a space outside the first flywheel 2. The housing space 2 is filled with lubricating oil. The output plate 33 is attached to the support portion 31a with rivets 32.

[0043] The friction portion 31b is an annular portion against which a friction lining (not shown) of a clutch disc assembly is pressed, and is provided on an outer peripheral portion of the support portion 31a. The friction portion 31b is located on a transmission side of the second plate 22 and is bulged closer to the transmission than the support portion 31a.

[0044] The output plate 33 is arranged in the housing space S and fixed to the support portion 31a. The output plate 33 has an annular main body portion 33a and two transmission portions 33e extending in a radial direction from the main body portion 33a.

[0045] The main body portion 33a is an annular portion fixed to the support portion 31a. A plurality of notches 33d are formed in an inner peripheral portion of the main body portion 33 and arranged at equal intervals in a circumferential direction. Projections 52b of a second friction plate 52 are fitted into the notches 33d. This allows the second friction plate 52 and the second flywheel 3 to rotate as an integral unit.

[0046] The transmission portions 33e are portions to which the power transmitted to the first flywheel 2 is transmitted through the four spring seats 49, and each includes a first protruding portion 33c and a pair of second protruding portions 33b. The first protruding portion 33c and the second protruding portions 33b are formed, for example, by a press-forming process.

[0047] The first protruding portion 33c is a plate-like portion that protrudes outward from the main body portion 33a in a radial direction. The first protruding portion 33c has a central portion 33h (example of the first main body protruding portion) positioned co-axially with the main body portion 33a, and a pair of outer portions 33i that bulge outward toward the gear box farther in an axial direction than the central portion 33h. The pair of outer portions 33i are arranged on both sides of the central portion 33h in a rotational direction.

[0048] The second protruding portions 33b are portions extending in an axial direction from the rotational-direction edge portions of the first protruding portion 33c (specifically, the outer portions 33i) toward the engine, and each have a contact portion 33f and a reinforcement portion 33g. The contact portion 33f is a portion extending in a radial direction and has a contact surface 33j that can contact the first spring seat 44 (explained later) in a rotational direction. A thickness direction of the contact portion 33f (the direction of the line perpendicular to the contact surface 33j) is substantially the same as the rotational direction.The reinforcement portion 33g is a portion connecting a radially inner end portion of the contact portion 33f with an outer peripheral portion of the main body portion 33a and extending from the radially inner end portion of the contact portion 33f to a side facing the contact surface 33. As shown in FIG. Fig. 3 and Fig. As shown in Figure 4, the reinforcement portion 33g has a curved portion. An axial dimension of the reinforcement portion 33g is the same as an axial dimension of the contact portion 33f. Since the outer portion 33i is bulged outward toward the transmission further than the central portion 33h, the axial dimension L of the contact portion 33f can be made comparatively large. As a result, the surface area of ​​the contact surface 33j can also be large. In particular, the contact area between the contact portion 33f and the first spring seat 44 is 250 mm. 2 or more. Damping mechanism

[0049] The damping mechanism 4 is a mechanism that elastically connects the first flywheel 2 to the second flywheel 3 in one rotation direction, 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.

[0050] The spring groups 49 include first springs 41 and second springs 42. The second springs 42 are arranged inside the first springs 41 so that they act in parallel. The four spring groups 49 are arranged in a pre-compressed state in a first housing section B1 formed by the first side portions 21b, the second side portions 22b, and the cylindrical portion 21c so 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 portions 33e, contact the rotationally facing edge portions of the first side portions 21b and the rotationally facing edge portions of the second side portions 22b in a rotational direction.

[0051] Specifically, the first spring seats 44 each include a seat main body 44c, a first outer support portion 44a, and a first inner support portion 44b. The first seat main body 44c supports one end portion of a spring group 49 in a rotational direction. The first outer support portion 44a is a portion extending in a rotational direction from a radially outer portion of the first seat main body 44c and serving to support one end portion of a spring group 49 in a radial direction. The first outer support portion 44a is slidable relative to the cylindrical portion 21c of the first plate 21.

[0052] The first inner support portions 44b are portions extending in a rotational direction from radially inner portions of the first seat main bodies 44c and serving to support the end portions of the spring groups 49 in a radial direction. The first inner support portions 44b and the first outer support portions 44a support the end portions of the spring groups 49 not only in a radial direction but also in an axial direction.

[0053] The first inner support portions 44b are shorter in a rotational direction than the first outer support portions 44a. Each of the first inner support portions 44b has a pair of first inclined sliding surfaces 44d (example of a second inclined surface) symmetrically arranged on axially opposite sides of the first inner support portion 44b. The first inclined sliding surfaces 44d are inclined with respect to both the axial direction and the radial direction and are formed over the entire first inner support portion 44b in the rotational direction. For example, the first inclined sliding surfaces 44d are inclined approximately 45 degrees with respect to a rotational axis. The first inclined sliding surfaces 44d can slide relative to the inclined surfaces 21e.

[0054] The second spring seats 43 are arranged between spring groups 49. Specifically, the second spring seats 43 each include a second seat main body 43c, a second outer support portion 43a, and a second inner support portion 43b. The second seat main body 43c supports end portions of spring groups 49 in one rotational direction. The second seat main body 43c supports end portions of spring groups 49 in one rotational direction. The second outer support portion 43a is a portion extending in both rotational directions from a radially outer portion of the second seat main body 43c and serving to support the end portions of the spring groups 49 in a radial direction. The second outer support portion 43a is slidable relative to the cylindrical portion 21c.

[0055] The second inner support portion 43b is a portion extending from a radially inner portion of the second seat main body 43c in both radial directions and serving to support end portions of the spring groups 49 in a radial direction. The second inner support portion 43b and the second outer support portion 43a support end portions of the spring groups 49 not only in a radial direction but also in an axial direction.

[0056] The second inner support portions 43 are shorter in a rotational direction than the second outer support portions 43a. Each of the two inner support portions 43b has a pair of second inclined surfaces 43d (example of a second inclined surface) symmetrically arranged on axially opposite sides of the second inner support portion 43b. The second inclined sliding surfaces 43d are inclined with respect to both the axial direction and the radial direction and are formed over the entire second inner support portion 43b in the rotational direction. For example, the second inclined sliding surfaces 43d are inclined approximately 45 degrees with respect to a rotational axis. The second inclined sliding surfaces 43d can slide relative to the inclined surfaces 21e.

[0057] The spring groups 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 groups 49, the first spring seats 44, and the second spring seats 43 are located in a first housing portion B1 formed by the first side portions 21b, the cylindrical portion 21c, and the second side portions 22b. The aforementioned pair of inclined surfaces 21e is formed in the second housing portion B2, which is more constricted in an axial direction than the first housing portion B1. Consequently, the first spring seats 44 and the second spring seats 43 are arranged in the first housing portion B1 such that they can move in a rotational direction in a state where their movement relative to the first flywheel 2 is restricted in an axial direction and a radial direction. Friction generation mechanism

[0058] The friction generating mechanism 5 is a mechanism for generating a resistance force in a rotational direction between the first flywheel 2 and the second flywheel 3 and includes a first friction plate 53, a second friction plate 52, a first sleeve 54, a second sleeve 55, and a conical spring 51.

[0059] The first friction plate 53 is formed to rotate integrally with the first flywheel 2 and is disposed on the engine side of the first sleeve 54.

[0060] The second friction plate 52 is configured to rotate integrally with the second flywheel 3, and includes an annular plate main body 52a (an example of a main body of a first member) and a plurality of protrusions 52b projecting outward from the plate main body 52a in a radial direction. The plate main body 52a is axially disposed between the first sleeve 54 and the second sleeve 55 and is slidable relative to the first sleeve 54 and the second sleeve 55. The protrusions 52b are inserted into the aforementioned notches 33d.

[0061] The first sleeve 54 is sandwiched axially between the first friction plate 53 and the second friction plate 52 and arranged to rotate relative to the first flywheel 2 and the second flywheel 3. The second sleeve 55 is sandwiched axially between the second friction plate 52 and the sliding portion 23c and arranged to rotate relative to the second friction plate 52 and the first flywheel 2. The conical spring 51 is arranged axially between the first friction plate 53 and the first plate 21 and urges the first friction plate 53 toward the transmission. Operating mode

[0062] When the clutch disc assembly is pressed against the second flywheel 3, power is transmitted from the engine to the transmission and the clutch disc assembly through 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. As a result, the spring groups 49 between the first flywheel 2 and the second flywheel 3 are initially compressed. In particular, the spring groups 49 are compressed by the first flywheel 2 and the transmission portion 3e of the second flywheel 3 in a rotational direction. Since the end portions of the spring groups 49 are covered by the first spring seats 44 and the second spring seats 43, the end portions of the spring seats 49 can be prevented from sliding on the first flywheel 2.

[0063] When the first flywheel 2 rotates relative to the second flywheel 3, frictional resistance is generated in the friction generating mechanism 5. Specifically, 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 second friction plate 52. Further, since the sliding portion 23c of the support member 23 rotates relative to the second friction plate 52, the second sleeve 55 slides relative to the second friction plate 52 or the sliding portion 23c. Consequently, resistance (e.g., hysteresis torque) is generated in a rotational direction between the first flywheel 2 and the second flywheel 3.

[0064] As the first flywheel 2 continues to rotate relative to the second flywheel 3, the first outer support portion 44a of the first spring seat 44 and the second outer support portion 43a of the second spring seats 43 come into contact with each other in a rotational direction. As a result, the first spring seat 44 and the second spring seat 43 are sandwiched between the transmission portion 33e and the support portion 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, power is transmitted from the first flywheel 2 to the second flywheel 3 through the first spring seats 44 and the second spring seats 43. Characteristic features

[0065] Characteristic features of the flywheel arrangement described above are set out below. (1-1)

[0066] In this output plate 33, since the second protruding portions 33b extend axially toward the engine from a circumferential edge portion of the first protruding portion, for example, a surface area of ​​the contact surface 33j of the second protruding portion 33 can be made large. This reduces wear on the second protruding portion 33b and the first spring seats 44 (which are in contact with the second protruding portion 33b). (1-2)

[0067] In this output plate 33, since the contact portions 33f and the main body portion 33a are connected by the reinforcement portions 33g, the stability of the entire transmission portion 33e can be increased. (1-3)

[0068] Since the reinforcement portions 33g of this base plate 33 are curved, the stress cannot easily concentrate in the reinforcement portions 33g, thereby preventing damage to the second projecting portions 33b. (1-4)

[0069] Since the reinforcement areas 33g of this output 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)

[0070] With this output plate 33, a large force transmission area can be easily secured because a thickness direction of the contact areas 33f is substantially the same as a rotation direction. (1-6)

[0071] Since in this output plate 33, the outer regions 33i of the first protruding portion 33c are bulged further toward the transmission than the central region 33h, the second protruding portions 33b, which extend axially from edge regions of the outer regions 33i toward the engine, can have larger dimensions in an axial direction. This means that the surface areas of the contact surfaces 33j of the transmission portion 33e can be further increased. (1-7)

[0072] 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)

[0073] In this damping mechanism 4, a friction area 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 can increase the vibration damping performance of the damping mechanism. (2-2)

[0074] 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 in which the second friction plate 52 rotates integrally with the second flywheel 3 can be achieved with a structurally simple means. (2-3)

[0075] Since in this damping mechanism 4 the sliding portion 23c of the support element 23 is arranged radially inward of the main body portion 33a of the output plate 33, an arrangement in which the second sleeve 55 is sandwiched axially between the second friction plate 52 and the sliding portion 23c can be achieved with structurally simple means. (3-1)

[0076] Since the second plate 22 of this output plate 33 has a plurality of support projections 22d, the gear ring 29 can be easily positioned relative to the second plate 22. That is, the gear ring 29 can be positioned on the second plate 22 simply by means of the support projections 22d, thereby reducing manufacturing costs. (3-2)

[0077] Since in this output plate 33 the support projections 22d are arranged on a radially inward side of the gear ring 29, the axial dimension of the second plate 22 can be prevented from increasing due to the support projections 22d. (3-3)

[0078] Since in this starting plate 33 the welding areas 29a are provided in the circumferential direction between adjacent support projections 22d, the gear ring 29 can be arranged and fixed in a small space. (3-4)

[0079] In this output plate 33, the increase in weight caused by the support projections 22d can be reduced because the second plate 22 has recesses 22f provided on the motor side of the support projections 22d. (3-5)

[0080] With this flywheel arrangement 1, the manufacturing costs can be reduced because the second flywheel 3 has such an output plate 33. (4-1)

[0081] In this damping mechanism 4, since the first inclined sliding surfaces 44d of the first spring seats 44 can slide relative to the inclined surfaces 2e of the first flywheel 2, the function of the first spring seats 44 is stable, and the vibration damping performance can be stabilized.

[0082] Since the second inclined sliding surfaces 43d of the second spring seats 43 can slide relative to the inclined surfaces 21e 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)

[0083] In this damper mechanism 4, since the pair of first inclined sliding surfaces 44d is formed on a first inner support portion 44b extending in a rotational direction, the length of the first inclined sliding surfaces 44d in a rotational direction can be made longer and the function of the first spring seats 44 can be better stabilized.

[0084] Since the pair of second inclined sliding surfaces 43d is formed on a second inner support portion 43b extending in a rotational direction, the length of the second inclined sliding surfaces 43d can also be made longer and the function of the second spring seats 43 can be better stabilized. (4-3)

[0085] In this damper mechanism 4, since the pairs of inclined surfaces 21e and 22e are formed in a narrowed region of the second housing portion B2, the axial dimension of the second housing portion B2 can be shortened and the function of the first spring seats 44 and the second spring seats 43 can be stabilized. (4-4)

[0086] Since in this damping mechanism 4 the first housing portion B1 and the second housing portion B2 are formed by the first plate 21 and the second plate 22, the first housing portion B1 and the second housing portion B2 can be structurally simple. (4-5)

[0087] In this damper mechanism 4, the first spring seats 44 and the second spring seats 43 are guided in a rotational direction because 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 portions 21b, the cylindrical portion 21c, and the second side portions 22b. With this configuration, the function of the first spring seats 44 and the second spring seats 43 in a rotational direction becomes stable. (5-1)

[0088] In this damping mechanism 4, the wear of the first spring seats 44 can be reduced because a contact area between the second projecting portions 33b (especially the contact portions 33f) of the first flywheel 2 and the first spring seats 44 is at least 250 mm 2 amounts. (5-2)

[0089] 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. Further embodiments

[0090] The present invention is not limited to the embodiments described above. Various variations and modifications are possible without departing from the scope of the present invention. (1)

[0091] Although in the above-described embodiment, the second protruding portions 33b extend axially from the first protruding portion 33c toward the engine, it is acceptable for the second protruding portions 33b to extend axially from edge portions of the first protruding portions 33c toward both the engine and the transmission, provided that the entire first protruding portion 33c is positioned co-axially with the main body portion 33a. In this way, the overall stability of the transmission portions 33e can be increased. (2)

[0092] Although in the above-described embodiment, a flywheel assembly 1 is indicated as a device having the output plate 33, it is acceptable if the device having the output plate is another device used for power transmission. INDUSTRIAL APPLICABILITY

[0093] The present invention is useful in the field of power transmission devices. REFERENCE NUMBERS 1 flywheel arrangement 2 first flywheel 21 first record 21a first main 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 main body 22b second side area 22c inner cylindrical area 22d support projection 22e inclined surface (example of the first inclined surface) 22f recess 23 Support element 23a Support element main body 23b annular projection 23c gliding area 29 Gear 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 of the first section) 33g gain range (example of the second section) 33h Middle area (example of the main body of the first projecting area) 33i outdoor area 33j contact surface 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 rotation body (2); a second rotary body (3) having a force transmission part (33) and arranged to rotate relative to the first rotary body (2); a spring which elastically connects the first rotational body (2) to the second rotational body (3) in a rotational direction and which is compressible between the first rotational body (2) and the transmission region (33e) of the force transmission part (33); and a spring seat (44) arranged between the first rotary body (2) and the transmission portion and supporting one end portion of the spring, wherein the force transmission part (33) configured to transmit force comprises: an annular main body portion (33a) and a plate-like transmission portion (33e) having a first projecting portion (33c) extending outwardly from the main body portion (33a) in a radial direction, and a pair of second projecting portions (33b) each extending axially toward a first side from a circumferentially facing pair of edge portions of the first projecting portion (33c), characterized by that the first projecting portion (33c) and the pair of second projecting portions (33b) are manufactured by a press-molding process, wherein the first projecting portion (33c) has a central portion (33h), which is arranged in an axial direction in the same position as the main body portion (33a), and has a pair of outer regions (33i) which bulge further in an axial direction than the central region (33h) towards a second side opposite the first side, wherein the pair of outer regions (33i) are arranged in a rotational direction on both sides of the central region (33h), wherein the pair of second projecting portions (33b) each extend in an axial direction from the rotationally facing pair of outer portions (33i) of the first projecting portion (33c), wherein the pair of second projecting portions (33b) are arranged to face each other in the rotational direction without any other member being arranged between the pair of second projecting portions (33b). [2] The damper mechanism (4) according to claim 1, wherein each second projecting portion (33b) has a first portion (33f) extending in a radial direction and a second portion (33g) connecting a radially inner end portion of the first portion (33f) to an outer peripheral portion of the main body portion (33a). [3] The damping mechanism (4) according to claim 2, wherein the second portion (33g) comprises a curved portion. [4] Damping mechanism (4) according to claim 2 or 3, wherein the first portion (33f) has a transmission surface facing in the circumferential direction for transmitting the force, and wherein the second portion (33g) extends to a side in the direction of which the transmission surface faces. [5] The damping mechanism (4) according to any one of claims 2 to 4, wherein a thickness direction of the first portion (33f) is the same as the circumferential direction. [6] The damping mechanism (4) according to any one of claims 1 to 5, wherein the transmission portion (33e) extends axially from the pair of circumferential edge portions of the first projecting portion (33c) also toward a side opposite to the first side.

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