flexible flywheel

Abstract

To provide a flexible fly wheel capable of suppressing warpage caused by centrifugal force, in addition to a vibration damping effect by bending of an elastic plate and a friction damping effect by frictional resistance.SOLUTION: A flexible fly wheel includes: a fly wheel main body 20; and a frictional plate 30 disposed on an end portion of a crank shaft via the fly wheel main body 20. The fly wheel main body 20 includes; an elastic spoke 22 for damping vibration by its bending; an inertia mass 23 disposed on an outer peripheral portion of the elastic spoke 22; and a plate receiving portion 24 having a surface 24c disposed at a front surface side with respect to the elastic spoke 22. The frictional plate 30 includes a flange 32 to be kept into contact with a surface 24c of the plate receiving portion 24 in a case where it is disposed on the end portion of the crank shaft with the fly wheel main body 20.SELECTED DRAWING: Figure 3

Description

[Technical Field]

[0001] The present invention relates to a flexible flywheel. [Background technology]

[0002] Generally, in rotating machines such as internal combustion engines for vehicles, a flywheel is attached to one end of the shaft. The flywheel has an annular inertial mass, and the rotational energy accompanying the rotational motion of the shaft is stored by the moment of inertia obtained by the inertial mass. Therefore, by attaching a flywheel, stable rotational motion of the shaft can be obtained.

[0003] A flexible flywheel is known as one type of flywheel. A flexible flywheel has an elastic plate fixed to a shaft, and an inertial mass is attached to the outer periphery of the elastic plate. In a flexible flywheel, vibrations acting on the shaft are damped by the flexure of the elastic plate. In addition to vibration damping by this elastic disk, there is also known a flywheel that damps vibrations by generating friction between a disc spring provided between the elastic disk and the inertial mass and the elastic disk or the inertial mass, and by this frictional resistance (see, for example, Patent Document 1). [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Japanese Patent Application Laid-Open No. 2007-162792 Summary of the Invention [Problem to be solved by the invention]

[0005] The inertial mass of a flexible flywheel is usually arranged to protrude away from the shaft to prevent interference with the shaft. Therefore, centrifugal force acting on the inertial mass pulls it toward the opposite side of the shaft and diagonally outward. This tension causes the flywheel to warp toward the opposite side of the shaft, and the resulting force acts on the inner periphery of the elastic plate. This force could damage the elastic plate, so it is necessary to ensure sufficient rigidity to prevent such damage. This reduces the vibration damping effect of the elastic plate's deflection.

[0006] The present invention has been made in consideration of the above circumstances, and aims to provide a flexible flywheel that not only has a vibration damping effect due to the bending of the elastic plate and a friction damping effect due to frictional resistance, but also can suppress warping due to centrifugal force. [Means for solving the problem]

[0007] In order to solve the above problems, the flexible wheel of the first invention is a circular flywheel body provided at an end of a shaft of a rotary machine; a friction generating member provided at an end of the shaft with the flywheel body interposed therebetween; A flexible flywheel comprising: The flywheel body is an elastic plate that attenuates vibrations acting on the shaft by its own deflection; an annular inertial mass provided on an outer periphery of the flywheel body, connected to the elastic plate, and protruding beyond the elastic plate on the opposite side of the shaft; an abutment portion provided on the opposite side of the shaft from the elastic plate; Equipped with The friction generating member is characterized by having an abutting portion that abuts against the abutted portion from the opposite side of the shaft when the friction generating member is provided at the end of the shaft together with the flywheel body.

[0008] The flexible flywheel of the second invention is The abutment portion is provided at a position closer to the inertial mass between the fastening portion fixed to the shaft and the inertial mass.

[0009] The flexible flywheel of the third invention is a plurality of the abutted portions are provided in the circumferential direction of the inertial mass, The friction generating member has a disk shape, and the portion of the outer periphery of the disk that comes into contact with the contacted portion serves as the contact portion.

[0010] The flexible flywheel of the fourth invention is a space is formed inside a portion of the inertial mass that protrudes beyond the elastic plate, The friction generating member is accommodated in the space.

[0011] The flexible flywheel of the fifth invention is The abutting portion abuts against the abutted portion while biasing the abutted portion toward the shaft.

[0012] The flexible flywheel of the sixth invention is The receiving portion having the contact portion is characterized in that it is formed to be thicker than the elastic plate.

[0013] The seventh invention of the flexible flywheel is the elastic plate is a plurality of elastic spokes extending radially between the main body fastening portion fixed to the end of the shaft and the inertial mass, connecting them; the abutted portions are provided between the elastic spokes, The main body fastening portion, the elastic spokes, the inertial mass, and the receiving portion having the abutment portion are integrally formed by casting or forging. [Effects of the Invention]

[0014] According to the first aspect of the present invention, the abutting portion of the friction generating member and the abutted portion of the flywheel body are in contact with each other on the opposite side of the shaft from the elastic plate. Therefore, when the shaft vibrates, friction occurs between the abutting portion and the abutted portion. In addition to vibration damping provided by the elastic plate, the frictional resistance damps shaft vibration. Furthermore, even if centrifugal force acting on the inertial mass pulls the inertial mass diagonally outward on the opposite side of the shaft, causing the flywheel body to warp forward, the abutting portion of the friction generating member abutting the abutted portion of the flywheel body from the opposite side of the shaft prevents the warping. This clamping mechanism prevents warping of the flywheel body. In this way, the abutting portion of the friction generating member abuts the abutted portion of the flywheel body on the opposite side of the shaft, providing vibration damping through frictional resistance and preventing warping of the flywheel body due to centrifugal force.

[0015] According to the second aspect of the present invention, the portion where the abutting portion and the abutted portion abut is located closer to the outer periphery of the flywheel body, which can further enhance the suppression effect compared to suppressing warpage of the flywheel body on the inner periphery.

[0016] According to the third aspect of the present invention, since the contact portions are not provided so as to extend radially in the radial direction but have portions that fill the gaps between the contact portions, the rigidity of the contact portions is increased by the portions that fill the gaps between the contact portions when the contact portions receive warpage, thereby further enhancing the warpage suppression effect.

[0017] According to the fourth aspect of the present invention, the friction generating member is housed in a space formed inside the inertial mass, eliminating the need to provide a separate space for the friction generating member and making effective use of the space formed by the inertial mass. This allows the friction generating member to be provided separately from the flywheel body without interfering with the installation space of devices provided around the flexible flywheel.

[0018] According to the fifth aspect of the present invention, the frictional resistance between the contacting portion and the contacted portion can be further increased. Also, by adjusting the biasing force, the contact state between the contacting portion and the contacted portion can be maintained without being released by vibration of the flywheel body. As a result, when vibration occurs in the shaft, the vibration damping effect due to the increased frictional resistance can be constantly obtained, thereby further improving the vibration damping effect.

[0019] According to the sixth aspect of the present invention, even if the contacted portion is worn due to friction with the contact portion, it is possible to improve durability against the wear.

[0020] According to the seventh aspect of the present invention, the flywheel body is integrally formed by casting or forging, and when the body is fastened to the end of the shaft together with the friction generating member by the body fastening part, it becomes a flexible flywheel. In other words, when the flywheel body and the friction generating member are fastened together with fasteners and assembled to the shaft, a flexible flywheel is attached to the shaft. This reduces the number of parts that make up the flexible flywheel, and reduces the costs of manufacturing and assembling each part. [Brief explanation of the drawings]

[0021] [Figure 1] FIG. [Figure 2] FIG. [Figure 3] FIG. [Figure 4] 2A and 2B are cross-sectional views taken along the line AA in FIG. 1 showing a manner of fixing to a crankshaft, where (a) shows before fixing and (b) shows after fixing. [Figure 5] Enlarged view of part X in Figure 4(b). [Figure 6] FIG. 10 is a schematic diagram illustrating a flexible wheel for explaining a warpage suppression function. DETAILED DESCRIPTION OF THE INVENTION

[0022] An embodiment of the present invention will be described below with reference to the drawings. In this embodiment, the rotating machine is assumed to be an internal combustion engine (engine) of a vehicle, and a flexible flywheel fixed to the crankshaft of the engine will be described.

[0023] As shown in Figures 1 and 2, the flexible flywheel 10 has a circular shape as a whole and includes a flywheel body 20 and friction plates 30. The friction plates 30 correspond to friction generating members. As shown in Figure 4(b), the flywheel body 20 and the friction plates 30 are both fixed to the end of a crankshaft 40, thereby integrating them into the flexible flywheel 10. In the description of this embodiment, the side on which the crankshaft 40 is located is referred to as the back side of the flexible flywheel 10, and the opposite side, i.e., the side opposite the shaft, is referred to as the front side or front face side.

[0024] First, the flywheel body 20 will be described. As shown in Figures 1 to 3, the flywheel body 20 has a body fastening portion 21, elastic spokes 22, an inertia mass 23, and a plate receiving portion 24, and is shaped as a whole like a steering wheel of an automobile. The body fastening portion 21, elastic spokes 22, inertia mass 23, and plate receiving portion 24 are castings made of cast iron or the like, and are integrally formed by casting or forging. The plate receiving portion 24 corresponds to a receiving portion.

[0025] As shown in Fig. 4(b), the main body fastening part 21 is fastened to the end of the crankshaft 40. As shown in Figs. 1 to 3, the main body fastening part 21 is formed in a disk shape and is provided in the center of the flexible flywheel 10. As shown in Fig. 4(b), the back surface 21b of the main body fastening part 21 abuts against the end face 42 of the fastened part 41 provided at the end of the crankshaft 40 when attached to the crankshaft 40.

[0026] 2 and 3, a main body positioning hole 25 is provided in the center of the main body fastening portion 21. When the back surface 21b of the main body fastening portion 21 abuts against the end face 42 of the fastened portion 41 of the crankshaft 40, as shown in FIG. 4(b), the tip protrusion 43 provided on the end face 42 is inserted into the main body positioning hole 25. This positions the crankshaft 40 and the flywheel body 20 so that their central rotational axes are aligned.

[0027] 2 and 3, a plurality of bolt insertion holes 26 are provided in an annular shape around the main body positioning hole 25 and are arranged at equal intervals. As shown in FIG. 4(b), bolt holes 44 corresponding to the bolt insertion holes 26 are provided in the fastened portion 41 of the crankshaft 40. With the back surface 21b of the main body fastening portion 21 abutting against the end face 42 of the fastened portion 41 of the crankshaft 40 and the tip protrusion 43 inserted into the main body positioning hole 25, the position of the bolt insertion hole 26 is aligned with the position of the bolt hole 44, and a bolt B is screwed into the bolt hole 44. This fastens the main body fastening portion 21 to the fastened portion 41, and the flywheel main body 20 is fixed to the crankshaft 40.

[0028] 1 to 3, the elastic spokes 22 extend radially from the main body fastening part 21 along the radial direction of the flexible flywheel 10. The elastic spokes 22 are formed in the shape of a wide flat plate, and the flat part is perpendicular to the central axis of rotation of the flexible flywheel 10. At the inner connecting part 27 where the elastic spokes 22 are connected to the main body fastening part 21, both side edges 27a, 27b in the circumferential direction are rounded.

[0029] As shown in FIG. 4(a), the elastic spokes 22 are formed thinner than the body fastening portion 21 to make the flywheel body 20 more flexible. Compared to the plate portion of the flywheel, which is not intended to provide a vibration damping effect, the elastic spokes 22 are thinner, which reduces their surface rigidity and makes them more flexible. Therefore, when vibrations generated by the crankshaft 40 are transmitted to the elastic spokes 22, the elastic spokes 22 bend, providing a vibration damping effect. The thickness of the elastic spokes 22 is arbitrary, but is set to a dimension of 4 mm or less, for example. The elastic spokes 22 correspond to an elastic plate.

[0030] The surfaces 22a of the elastic spokes 22 are located closer to the shaft than the surfaces 21a of the main body fastening portion 21. In other words, in the direction of the central axis of the flywheel main body 20, when viewed from the front side, the surfaces 22a of the elastic spokes 22 are located closer to the back (shaft) than the surfaces 21a of the main body fastening portion 21.

[0031] 1 to 3, three elastic spokes 22 are provided, all of which have the same configuration. The three elastic spokes 22 are evenly spaced around the circumferential direction of the flywheel body 20. Therefore, when imaginary lines L1 to L3 are imagined to connect the center of each elastic spoke 22 in the width direction to the center of the flywheel body 20 in a front or rear view, the angle between the imaginary lines L1 to L3 is set to 120 degrees.

[0032] As shown in Figures 1 and 3, the inertia mass 23 is formed in an annular shape on the outer periphery of the flywheel body 20. The inner periphery of the inertia mass 23 is connected to the tip ends of the elastic spokes 22, which extend radially from the body fastening portion 21. At the outer connecting portion 28 where the elastic spokes 22 are connected to the inertia mass 23, both circumferential edges 28a, 28b are rounded. When the flywheel body 20 rotates, a relatively large moment of inertia is generated by the weight of the inertia mass 23, stabilizing the rotational movement of the crankshaft 40. The inertia mass 23 is formed with a screw hole 23a and the like for attaching a damper (not shown). The presence or absence of a damper is optional.

[0033] 3 and 4, the inertia mass 23 is provided so as to protrude further forward than the elastic spokes 22, which are formed as thin elastic plates. Therefore, a space 29 is formed on the inner periphery of the inertia mass 23, further forward than the main body fastening portion 21 and the elastic spokes 22. As shown in FIG. 1, the space 29 has a circular shape when viewed from the front.

[0034] As shown in FIGS. 1 to 3 , a plate support portion 24 is provided between each of the three elastic spokes 22. One plate support portion 24 is provided between each of the elastic spokes 22, for a total of three plate support portions 24. All of the plate support portions 24 have the same configuration. The plate support portions 24 are provided on the inner periphery of the inertial mass 23 in an arc-like shape along the circumferential direction and are not connected to the main body fastening portion 21. The inner periphery of the plate support portion 24 also has an arc-like shape. Both circumferential side edges 24a, 24b of the plate support portion 24 are rounded and connected to the inner periphery of the inertial mass 23. As shown in FIG. 2 , an elastic spoke 22 is provided on the radial opposite side of the flywheel body 20, sandwiching the main body fastening portion 21 between the plate support portion 24. In other words, the plate support portions 24 are provided on extensions of the imaginary lines L1 to L3 extending through the widthwise center of the elastic spokes 22. The plate receiving portion 24 is symmetrical with respect to the extension lines of the imaginary lines L1 to L3.

[0035] 4, the plate receiving portion 24 is flat and thicker than the elastic spokes 22. The surface 24c of the plate receiving portion 24 is located closer to the front than the surface 22a of the elastic spokes 22 and closer to the back than the surface 21a of the main body fastening portion 21. In other words, the surface 21a of the main body fastening portion 21, the surface 24c of the plate receiving portion 24, and the surface 22a of the elastic spokes 22 are not located on the same plane, but are located side by side in this order from the front side to the back side.

[0036] The above has explained the flywheel body 20, and next we will explain the friction plate 30. As shown in Figures 1 to 3, the friction plate 30 is in the shape of a disk whose diameter is smaller than the circular space 29 formed on the inner periphery of the inertial mass 23 and larger than the diameter of the imaginary circle formed by the inner periphery of the plate support portion 24. The friction plate 30 has a truncated cone portion 31 and a flange 32. The truncated cone portion 31 and the flange 32 are formed by drawing a circular flat plate made of spring steel.

[0037] The truncated cone portion 31 is provided at the center of the friction plate 30, and a flange 32, which forms the outer peripheral edge of the friction plate 30, is provided in an annular shape over the entire circumferential area of ​​the truncated cone portion 31. As shown in Figures 3 and 4, the friction plate 30 is fitted to the flywheel body 20 with the bottom of the truncated cone portion 31 and the flange 32 located on the back surface side, and then the friction plate 30 and the flywheel body 20 are fixed to the fastened portion 41 of the crankshaft 40.

[0038] The circular flat portion at the center of the truncated cone portion 31 serves as a plate fastening portion 33. A plate positioning hole 34 is provided in the center of the plate fastening portion 33. After the tip protrusion 43 of the crankshaft 40 is inserted into the body positioning hole 25 of the flywheel body 20, the tip protrusion 43 protruding from the body positioning hole 25 is inserted into the plate positioning hole 34. As a result, the friction plate 30 is provided on the front side of the flywheel body 20 and housed in the space 29 on the inner circumferential side of the inertia mass 23. The back surface 33b of the plate fastening portion 33 abuts against the front surface 21a of the body fastening portion 21, and is attached to the fastened portion 41 of the crankshaft 40 via the body fastening portion 21. By inserting the tip protrusion 43 of the fastened portion 41 into the plate positioning hole 34, the friction plate 30 is positioned so that the rotational axis of the crankshaft 40 and the rotational axis of the friction plate 30 are aligned.

[0039] 1 and 3, bolt insertion holes 35 are provided in a ring shape around the plate positioning hole 34, and are arranged at equal intervals, the number of which is the same as the number of bolt insertion holes 26 provided in the main body fastening portion 21. As described above, the flywheel main body 20 is fixed to the fastened portion 41 of the crankshaft 40 using bolts B. As shown in FIG. 4(b), the friction plate 30 is also fixed to the fastened portion 41 of the crankshaft 40 using bolts B used for this fixation.

[0040] That is, the back surface 33b of the plate fastening portion 33 abuts against the front surface 21a of the main body fastening portion 21 from the front side, and the tip protrusion 43 is also inserted into the plate positioning hole 34. The position of the bolt insertion hole 35 of the plate fastening portion 33 is aligned with the position of the bolt insertion hole 26 and the bolt hole 44 of the main body fastening portion 21, and the bolt B is screwed into the bolt hole 44. As a result, the plate fastening portion 33 is fastened together with the main body fastening portion 21 to the fastened portion 41, and the friction plate 30 is fixed to the crankshaft 40 integrally with the flywheel main body 20.

[0041] When the friction plate 30 is fixed to the crankshaft 40 together with the flywheel body 20, the friction plate 30 is fixed to the crankshaft 40 while being compressed in its thickness direction. To achieve this fixed state in a compressed state, as shown in Figure 4(a), the pre-compression dimension W1 between the back surface 33b of the plate fastening portion 33 and the back surface 32b of the flange 32 is set to be larger than the installation dimension W2 between the front surface 22a of the body fastening portion 21 in the flywheel body 20 and the front surface 24c of the plate receiving portion 24.

[0042] Due to this dimensional difference, the back surface 33b of the plate fastening portion 33 abuts against the front surface 21a of the main body fastening portion 21 from the front side, and when both are fixed to the crankshaft 40, the friction plate 30 is compressed in its thickness direction, and the back surface 32b of the flange 32 abuts against the front surface 24c of the plate receiving portion 24, as shown in FIG. 5. The entire back surface 32b of the flange 32 that abuts against the front surface 24c of the plate receiving portion 24 corresponds to the abutting portion, and the front surface 24c of the plate receiving portion 24 corresponds to the abutted portion. Because the friction plate 30 is made of spring steel, the flange 32 abuts against the front surface of the plate receiving portion 24 while biasing the plate receiving portion 24. While the flange 32 abuts against the plate receiving portion 24 in this way, the flange 32 does not abut against the elastic spokes 22, and the two are spaced apart.

[0043] The contact area R between the flange 32 and the plate receiving portion 24 has a certain width in the radial direction. The width of the contact area R is set by adjusting the diameter of the friction plate 30, the radial width dimension of the flange 32, and the radial width dimension of the plate receiving portion 24. In addition, the force with which the flange 32 urges the plate receiving portion 24 can be adjusted by adjusting the pre-compression dimension W1 and the installation dimension W2.

[0044] Next, the operation of the flexible flywheel 10 when it is fixed to the fastened portion 41 of the crankshaft 40 will be described.

[0045] When the flexible flywheel 10 rotates in conjunction with the rotation of the crankshaft 40, a moment of inertia is generated by the inertial mass 23, which results in stable rotation of the crankshaft 40. When the crankshaft 40 vibrates due to the engine running, the vibration is transmitted to the main body fastening portion 21 of the flexible flywheel 10. When the vibration is further transmitted to the elastic spokes 22, the elastic spokes 22 bend and dampen the vibration.

[0046] In addition to vibration damping due to the flexure of the elastic spokes 22, when vibrations of the crankshaft 40 are transmitted to the flywheel body 20, friction occurs between the plate support portion 24 and the flange 32 in the contact region R between the flywheel body 20 and the friction plate 30, as shown in FIG. 5 . This frictional resistance also damps vibrations generated in the crankshaft 40. In this case, because the flange 32 abuts against the plate support portion 24 with a biasing force, the abutment between the two is prevented from being released due to vibration, and the abutment state between the two is maintained. As a result, friction is reliably generated between the flange 32 and the plate support portion 24, and vibration damping due to frictional resistance is reliably achieved. Moreover, when friction occurs in the contact region R, because the flange 32 is not abutting against the elastic spokes 22, the presence of the friction plate 30 does not hinder the flexure of the elastic spokes 22. As a result, the crankshaft 40 can rotate stably while vibrations caused by engine operation are suppressed.

[0047] In addition to the vibration damping described above, the friction plate 30 also suppresses warping of the flywheel body 20. When the crankshaft 40 rotates, centrifugal force acts on the flywheel body 20, which includes the inertial mass 23. This centrifugal force pulls the flywheel body 20 diagonally upward toward the front side from which the inertial mass 23 protrudes, causing warping toward the front side, as shown in FIG. 6 . However, because the flange 32 of the friction plate 30 abuts against the plate support portion 24 of the flywheel body 20, the friction plate 30 acts as a clamp against the warping, suppressing the warping. In particular, the plate support portion 24 is located on the outer periphery of the flywheel body 20, closer to the inertial mass 23. This provides a greater warping suppression effect than suppressing warping on the inner periphery. This eliminates the need to increase the rigidity of the elastic spokes 22 to suppress damage to the elastic spokes 22 due to warping, thereby sacrificing vibration damping effect.

[0048] To summarise the above, the flexible flywheel 10 of this embodiment can provide the following advantages.

[0049] (1) The flange 32 of the friction plate 30 and the plate support portion 24 of the flywheel body 20 come into contact with each other on the front side of the elastic spokes 22, providing a contact area R between them. Therefore, when the crankshaft 40 vibrates, friction occurs between the flange 32 and the plate support portion 24. This frictional resistance can damp vibrations of the crankshaft 40 in addition to vibration damping by the elastic spokes 22. Furthermore, even if the centrifugal force acting on the inertial mass 23 pulls the inertial mass 23 toward the front side and diagonally outward, causing the flywheel body 20 to warp toward the front side, the flange 32 abutting the plate support portion 24 from the front side prevents the warping. This also suppresses warping of the flywheel body 20.

[0050] (2) The flange 32 of the friction plate 30 abuts against the plate support portion 24 of the flywheel body 20 but does not abut against the elastic spokes 22, so the presence of the friction plate 30 does not impede the vibration damping function caused by the flexure of the elastic spokes 22. In addition, because no friction occurs between the flange 32 and the elastic spokes 22, it is possible to prevent the elastic spokes 22 from wearing down due to friction between the two and thereby prevent a decrease in the rigidity of the elastic spokes 22.

[0051] (3) The plate receiving portion 24 is provided between the main body fastening portion 21 and the inertial mass 23, closer to the inertial mass 23, and the contact area R between the flange 32 and the plate receiving portion 24 is provided on the outer periphery side of the flywheel main body 20. Therefore, the contact area R is provided on the inner periphery side of the flywheel main body 20, and the warpage can be suppressed more effectively than if the contact area R were provided on the inner periphery side of the flywheel main body 20 and warpage were suppressed on the inner periphery side.

[0052] (4) The plate receiving portion 24 is provided between each of the three elastic spokes 22, and the friction plate 30 has a disk shape. Therefore, unlike a configuration in which three contact portions that contact the plate receiving portion 24 are provided extending radially in the radial direction, only a portion of the annular flange 32 contacts the plate receiving portion 24, and the truncated cone portion 31 and flange 32 exist between the contact portions to fill the gaps. As a result, the truncated cone portion 31 and flange 32 that fill the gaps between the contact portions increase the rigidity of the contact portions, and the warp suppression effect can be further improved.

[0053] (5) A space 29 is formed on the inner periphery of the inertial mass 23, in front of the elastic spokes 22, and the friction plate 30 is housed in this space 29. Therefore, there is no need to provide a separate space for the friction plate 30, and the space 29 formed by the inertial mass 23 can be effectively utilized. This allows the friction plate 30 to be provided as a separate part from the flywheel body 20 without interfering with the installation space of devices provided around the flexible flywheel 10.

[0054] (6) The flange 32 of the friction plate 30 abuts against the plate support portion 24 while biasing the plate support portion 24 toward the crankshaft 40, thereby further increasing the frictional resistance between them. In addition, by adjusting the biasing force, the abutment state between the flange 32 and the plate support portion 24 can be maintained without being released by vibration of the flywheel body 20. This allows the vibration damping effect to be constantly obtained due to the increased frictional resistance, thereby further increasing the vibration damping effect.

[0055] (7) The plate receiving portion 24 of the flywheel body 20 is formed thicker than the elastic spokes 22. Therefore, even if the plate receiving portion 24 is worn due to friction with the flange 32, the plate receiving portion 24 can have improved resistance to the wear.

[0056] (8) The flywheel body 20 is formed by integrally casting or forging the body fastening portion 21, elastic spokes 22, inertia mass 23, and plate receiving portion 24. The flywheel body 20 and friction plate 30 are fixed to the fastened portion 41 of the crankshaft 40 with bolts B as fasteners to form the flexible flywheel 10. This reduces the number of parts that make up the flexible flywheel 10, and reduces the costs of manufacturing and assembling each part.

[0057] The flexible flywheel 10 is not limited to the above embodiment, and may have the following configuration, for example.

[0058] (a) In the above embodiment, three elastic spokes 22 are provided on the flywheel body 20. Alternatively, the number of elastic spokes 22 may be four, or any other number may be provided.

[0059] (b) In the above embodiment, one plate receiving portion 24 is provided between each pair of elastic spokes 22. Alternatively, a configuration may be adopted in which a plurality of plate receiving portions 24 are provided between each pair of elastic spokes 22, or a different number of plate receiving portions 24 are provided. Even in this case, it is preferable that the plate receiving portions 24 are arranged symmetrically with respect to the extensions of the imaginary lines L1 to L3 along which the elastic spokes 22 extend.

[0060] (c) In the above embodiment, the friction generating member, friction plate 30, is a disk having a truncated cone portion 31 and a flange 32. Alternatively, the friction generating member may be a flat disk without the truncated cone portion 31, a polygonal friction generating member having corners corresponding to the number of plate holders 24, or a propeller-shaped friction generating member. A propeller-shaped friction generating member has blades extending radially from the main body fastening portion 21 toward the plate holders 24. In this case, the rear surfaces of the tips of the blades form contact portions that come into contact with the plate holders 24.

[0061] (d) In the above embodiment, the plate receiving portion 24 is provided on the inner periphery of the inertial mass 23 and is not connected to the main body fastening portion 21. Conversely, a configuration may be adopted in which the plate receiving portion 24 is provided on the outer periphery of the main body fastening portion 21 and is not connected to the inertial mass 23.

[0062] (e) In the above embodiment, the flywheel body 20 is formed by integrally casting or forging the body fastening portion 21, the elastic spokes 22, the inertia mass 23, and the plate receiving portion 24. Alternatively, these portions may be formed as separate members, which are then assembled to form the flywheel body.

[0063] (f) In the above embodiment, the elastic spokes 22 are elastic plates, but the elastic plates may be disk-shaped instead of spoke-shaped. In this case, the disk-shaped elastic plate may have lightening holes in various places.

[0064] (g) In the above embodiment, the rotating machine is assumed to be an internal combustion engine (engine) for a vehicle. The present invention can be applied to any object, such as a flywheel used in a press machine, as long as it is used for the purpose of stabilizing rotation using the moment of inertia and preserving rotational energy. [Explanation of symbols]

[0065] 10...Flexible flywheel, 20...Flywheel body, 21...Body fastening portion, 22...Elastic spoke (elastic plate), 23...Inertial mass, 24...Plate receiving portion (receiving portion), 24c...Surface of plate receiving portion (contact portion), 29...Space portion, 30...Friction plate (friction generating member), 32a...Back surface of flange (contact portion), 40...Crankshaft

Claims

1. a circular flywheel body provided at an end of a shaft of a rotary machine; a friction generating member provided at an end of the shaft with the flywheel body interposed therebetween; A flexible flywheel comprising: The flywheel body is an elastic plate that attenuates vibrations acting on the shaft by its own deflection; an annular inertial mass provided on an outer periphery of the flywheel body, connected to the elastic plate, and protruding beyond the elastic plate on the opposite side of the shaft; an abutment portion provided on the opposite side of the shaft from the elastic plate; Equipped with the friction generating member includes a contact portion that contacts the contacted portion from the opposite side of the shaft when the friction generating member is provided at the end of the shaft together with the flywheel body, a plurality of the abutted portions are provided in the circumferential direction of the inertial mass, The friction generating member has a disk shape, and the portion of the outer periphery of the disk that comes into contact with the contacted portion constitutes the contact portion.

2. a circular flywheel body provided at an end of a shaft of a rotary machine; a friction generating member provided at an end of the shaft with the flywheel body interposed therebetween; A flexible flywheel comprising: The flywheel body is an elastic plate that attenuates vibrations acting on the shaft by its own deflection; an annular inertial mass provided on an outer periphery of the flywheel body, connected to the elastic plate, and protruding beyond the elastic plate on the opposite side of the shaft; an abutment portion provided on the opposite side of the shaft from the elastic plate; Equipped with the friction generating member includes a contact portion that contacts the contacted portion from the opposite side of the shaft when the friction generating member is provided at the end of the shaft together with the flywheel body, A flexible flywheel characterized in that the receiving portion having the contact portion is formed to be thicker than the elastic plate.

3. a circular flywheel body provided at an end of a shaft of a rotary machine; a friction generating member provided at an end of the shaft with the flywheel body interposed therebetween; A flexible flywheel comprising: The flywheel body is an elastic plate that attenuates vibrations acting on the shaft by its own deflection; an annular inertial mass provided on an outer periphery of the flywheel body, connected to the elastic plate, and protruding beyond the elastic plate on the opposite side of the shaft; an abutment portion provided on the opposite side of the shaft from the elastic plate; Equipped with the friction generating member includes a contact portion that contacts the contacted portion from the opposite side of the shaft when the friction generating member is provided at the end of the shaft together with the flywheel body, the elastic plate is a plurality of elastic spokes extending radially between the main body fastening portion fixed to the end of the shaft and the inertial mass, connecting them; the abutted portions are provided between the elastic spokes, A flexible flywheel characterized in that the main body fastening portion, the elastic spokes, the inertial mass, and the receiving portion having the abutment portion are integrally formed by casting or forging.

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