Flexible fly wheel

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 a rotating machine such as an internal combustion engine of a vehicle, a flywheel is attached to one end of a 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, it is possible to obtain a stable rotational motion of the shaft.

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

[0004] [Patent Document 1] JP 2007-162792 A Summary of the Invention [Problem to be solved by the invention]

[0005] Incidentally, the inertial mass of a flexible flywheel is usually provided so as to protrude toward the opposite side of the shaft to prevent interference with the shaft. Therefore, the centrifugal force acting on the inertial mass pulls the inertial mass toward the opposite side of the shaft and diagonally outward. This pull causes the flywheel to warp toward the opposite side of the shaft, and the force caused by this warping acts on the inner periphery of the elastic plate. This force may damage the elastic plate, so it is necessary to ensure rigidity against such damage, which causes a problem of reducing the vibration damping effect caused by the bending of the elastic plate.

[0006] The present invention has been made in consideration of the above circumstances, and has an object to provide a flexible flywheel that has a vibration damping effect due to the bending of an elastic plate and a friction damping effect due to frictional resistance, as well as the ability to 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 comprises: 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 therebetween; A flexible flywheel comprising: The flywheel body is an elastic plate that attenuates vibration acting on the shaft by bending the elastic plate itself; 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 an opposite side to the shaft; a contact 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 than the inertial mass and between a fastening portion fixed to the shaft and the inertial mass.

[0009] The flexible flywheel of the third invention is a plurality of the abutment portions are provided in a circumferential direction of the inertial mass, The friction generating member has a disk shape, and a portion of an outer circumferential edge 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 is in contact with the abutted portion while biasing the abutted portion toward the shaft.

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

[0013] The seventh aspect of the flexible flywheel is as follows: the elastic plate is a plurality of elastic spokes extending radially between the main body fastening portion fixed to the end portion of the shaft and the inertial mass, and connecting the two, The abutment portion is 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. Effect 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 formed in contact with each other on the opposite side of the shaft from the elastic plate, so that when the shaft vibrates, friction occurs between the abutting portion and the abutted portion. In addition to vibration damping by the elastic plate, the vibration of the shaft can be damped by the friction resistance. Even if the inertial mass is pulled diagonally outward on the opposite side of the shaft by the centrifugal force acting on the inertial mass and the flywheel body tries to warp forward, the abutting portion of the friction generating member abuts on the abutted portion of the flywheel body from the opposite side of the shaft, thereby suppressing the warping. This suppression makes it possible to suppress the warping of the flywheel body. In this way, since the abutting portion of the friction generating member abuts on the abutted portion of the flywheel body on the opposite side of the shaft, a flexible flywheel can be obtained in which vibration damping by friction resistance is achieved and warping of the flywheel body due to centrifugal force is suppressed.

[0015] According to the second aspect of the present invention, the portion where the abutting portion and the abutted portion abut is provided on the outer periphery of the flywheel body, which can further enhance the suppression effect compared to suppressing warping 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 rather there are 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 making it possible to further enhance the warpage suppression effect.

[0017] According to the fourth aspect of the present invention, since the friction generating member is housed in the space formed inside the inertial mass, there is no need to provide a separate space for the friction generating member, and the space formed by the inertial mass can be effectively utilized. This allows the friction generating member to be provided separately from the flywheel body without interfering with the installation space of the devices provided around the flexible flywheel.

[0018] According to the fifth aspect of the present invention, the frictional resistance between the contact portion and the contacted portion can be further increased. In addition, by adjusting the biasing force, the contact state between the contact 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 increasing 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 resistance to 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 fastening part is fixed to the end of the shaft together with the friction generating member, a flexible flywheel is formed. In other words, when the flywheel body and the friction generating member are fastened together with a fastener and assembled to the shaft, a flexible flywheel is provided on 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 description of the drawings]

[0021] [Figure 1] FIG. [Diagram 2] FIG. [Diagram 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 the state before fixing and (b) shows the state after fixing. [Diagram 5] An enlarged view of part X in FIG. 4(b). [Figure 6] FIG. 13 is a schematic diagram of a flexible wheel for explaining a warpage suppression function. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0022] Hereinafter, an embodiment of the present invention will be described 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 the crankshaft 40, and are integrated to form the flexible flywheel 10. In the description of this embodiment, the side on which the crankshaft 40 is disposed 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 inertial mass 23, and a plate receiving portion 24, and is shaped like a steering wheel of an automobile as a whole. The body fastening portion 21, elastic spokes 22, inertial 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 part 21. When the back surface 21b of the main body fastening part 21 abuts against the end face 42 of the fastened part 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 axis lines are aligned.

[0027] 2 and 3, a plurality of bolt insertion holes 26 are provided around the main body positioning hole 25 in an annular shape and are arranged at equal intervals. As shown in FIG. 4(b), a bolt hole 44 corresponding to the bolt insertion hole 26 is 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. As a result, the main body fastening portion 21 is fastened 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 a wide flat plate shape, and the flat plate portion 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 in order to make the flywheel body 20 flexible. Compared to the plate portion of the flywheel that is not intended to obtain a vibration damping effect, the elastic spokes 22 are made thinner, so that the surface rigidity of the elastic spokes 22 is reduced and the elastic spokes 22 is more flexible. Therefore, when vibrations generated in the crankshaft 40 are transmitted to the elastic spokes 22, the elastic spokes 22 bend to obtain 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 provided closer to the shaft side than the surface 21a of the main body fastening portion 21. In other words, in the central axial direction of the flywheel body 20, when viewed from the front side, the surfaces 22a of the elastic spokes 22 are provided closer to the back side (shaft side) than the surface 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 arranged in the circumferential direction of the flywheel body 20. Therefore, when imaginary lines L1 to L3 are imagined connecting 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 Fig. 1 and Fig. 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 end of the elastic spokes 22 extending radially from the body fastening part 21. At the outer connecting part 28 where the elastic spokes 22 are connected to the inertia mass 23, both side edges 28a, 28b in the circumferential direction are rounded. When the flywheel body 20 rotates, a relatively large moment of inertia force is obtained by the weight of the inertia mass 23, stabilizing the rotational operation of the crankshaft 40. The inertia mass 23 is formed with a screw hole 23a 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, on the inner periphery side of the inertia mass 23, a space 29 is formed 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 in a front view.

[0034] As shown in Figs. 1 to 3, the plate receiving portion 24 is provided between each of the three elastic spokes 22. One plate receiving portion 24 is provided between each of the elastic spokes 22, and a total of three plate receiving portions 24 are provided. Each plate receiving portion 24 has the same configuration. The plate receiving portion 24 is provided on the inner peripheral portion of the inertial mass 23 so as to form an arc shape along the circumferential direction, and is not connected to the main body fastening portion 21. The inner peripheral edge of the plate receiving portion 24 is also arc-shaped. Both side edges 24a, 24b in the circumferential direction of the plate receiving portion 24 are curved and connected to the inner peripheral portion of the inertial mass 23. As shown in Fig. 2, the elastic spokes 22 are provided on the opposite side of the plate receiving portion 24 across the main body fastening portion 21 in the radial direction of the flywheel body 20. That is, the plate receiving portion 24 is provided on the extension line of each imaginary line L1 to L3 extending at the center of the width direction 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 provided on the front side of the surface 22a of the elastic spokes 22 and on the back side of 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 provided on the same plane, but are provided side by side in this order from the front side to the back side.

[0036] The above is a description of the flywheel body 20, and next, a description will be given of the friction plate 30. As shown in Figures 1 to 3, the friction plate 30 is in the shape of a disk having a diameter smaller than the circular space 29 formed on the inner periphery side of the inertial mass 23 and larger than the diameter of the imaginary circle formed by the inner periphery of the plate receiving 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 is the outer peripheral edge portion of the friction plate 30, is provided in an annular shape over the entire circumferential direction 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 arranged on the back surface side, and is fixed to the fastening portion 41 of the crankshaft 40 together with the flywheel body 20.

[0038] The circular flat portion at the center of the truncated cone portion 31 is the plate fastening portion 33. A plate positioning hole 34 is provided at the center of the plate fastening portion 33. After the tip projection 43 of the crankshaft 40 is inserted into the body positioning hole 25 of the flywheel body 20, the tip projection 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 accommodated in the space 29 on the inner periphery side of the inertial mass 23. The back surface 33b of the plate fastening portion 33 abuts against the 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 projection 43 of the fastened portion 41 into the plate positioning hole 34, the friction plate 30 is positioned so that the rotational center axis of the crankshaft 40 and the rotational center axis of the friction plate 30 are aligned.

[0039] 1 and 3, bolt insertion holes 35 are provided annularly around the plate positioning hole 34, and are arranged at equal intervals, the same number as the 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 by using the bolt B. As shown in FIG. 4(b), the friction plate 30 is also fixed to the fastened portion 41 of the crankshaft 40 by using the bolt B used for the fixing.

[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 positions 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 fixing in a compressed state, as shown in Fig. 4(a), a 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 an 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 difference in dimensions, when 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 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. Of the entire back surface 32b of the flange 32, the part 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. Since the friction plate 30 is formed of spring steel, the flange 32 abuts against the plate receiving portion 24 from the front side while biasing the plate receiving portion 24. Thus, while the flange 32 abuts against the plate receiving portion 24, the flange 32 does not abut against the elastic spokes 22, and the two are separated from each other.

[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 is 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 together with the crankshaft 40, a moment of inertia is generated by the inertial mass 23, which provides 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 the vibration of the crankshaft 40 is transmitted to the flywheel body 20, friction occurs between the plate receiving 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. The frictional resistance also damps the vibration generated in the crankshaft 40. In this case, the flange 32 is in contact with the plate receiving portion 24 with a biasing force, so that the contact between the two is prevented from being released due to vibration, and the contact state between the two is maintained. As a result, friction is reliably generated between the flange 32 and the plate receiving portion 24, and vibration damping due to frictional resistance is reliably obtained. Moreover, when friction occurs in the contact region R, the flange 32 is not in contact with the elastic spokes 22, so the presence of the friction plate 30 does not hinder the flexure of the elastic spokes 22. As a result, the crankshaft 40 can perform stable rotational operation while vibration caused by the driving of the engine is suppressed.

[0047] In addition to the vibration damping as described above, the warping of the flywheel body 20 is suppressed by the friction plate 30. When the crankshaft 40 rotates, centrifugal force acts on the flywheel body 20 having the inertial mass 23. As shown in FIG. 6, this centrifugal force pulls the flywheel body 20 obliquely upward from the front side where the inertial mass 23 protrudes, causing warping toward the front side. However, since the flange 32 of the friction plate 30 abuts against the plate receiving 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 receiving portion 24 is provided on the outer periphery side of the flywheel body 20, which is closer to the inertial mass 23. Therefore, the warping suppression effect is enhanced compared to suppressing the warping on the inner periphery side. This makes it unnecessary to increase the rigidity of the elastic spokes 22 in order to suppress damage to the elastic spokes 22 due to warping, thereby sacrificing the vibration damping effect.

[0048] In summary, 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 receiving portion 24 of the flywheel body 20 come into contact with each other on the front side of the elastic spokes 22, and a contact area R between them is provided. Therefore, when the crankshaft 40 vibrates, friction occurs between the flange 32 and the plate receiving portion 24. In addition to the vibration damping by the elastic spokes 22, the vibration of the crankshaft 40 can be damped by the frictional resistance. Also, even if the inertial mass 23 is pulled toward the front side and diagonally outward due to the centrifugal force acting on the inertial mass 23, and the flywheel body 20 tries to warp toward the front side, the flange 32 comes into contact with the plate receiving portion 24 from the front side to suppress the warping. This can also suppress the warping of the flywheel body 20.

[0050] (2) The flange 32 of the friction plate 30 abuts against the plate receiving 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, which would otherwise reduce 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 the 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 the flange 32 are present between the contact portions to fill the gaps. As a result, the truncated cone portion 31 and the 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 on the front side of the elastic spokes 22, and the friction plate 30 is housed in the space 29. Therefore, there is no need to provide a separate space for accommodating 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 separately 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 receiving portion 24 while biasing the plate receiving portion 24 toward the crankshaft 40, so that the frictional resistance between them can be further increased. In addition, by adjusting the biasing force, the abutment state between the flange 32 and the plate receiving portion 24 can be maintained without being released by vibration of the flywheel body 20. As a result, the vibration damping effect due to the increased frictional resistance can be constantly obtained, so that the vibration damping effect can be further increased.

[0055] (7) The plate receiving portion 24 of the flywheel body 20 is formed to be 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 forming the body fastening portion 21, the elastic spokes 22, the inertial mass 23, and the plate receiving portion 24 by casting or forging. The flywheel body 20 and the friction plate 30 are fixed to the fastening portion 41 of the crankshaft 40 by the bolt B serving as a fastener to form the flexible flywheel 10. This reduces the number of parts constituting 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 of elastic spokes 22 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 so as to be symmetrical with respect to the extension line of the imaginary lines L1 to L3 along which the elastic spokes 22 extend.

[0060] (c) In the above embodiment, the friction plate 30 serving as the friction generating member is disk-shaped having the truncated cone portion 31 and the flange 32. Alternatively, the friction generating member may be a flat disk-shaped member without the truncated cone portion 31, a polygonal friction generating member having angles corresponding to the number of the plate receiving portions 24, or a propeller-shaped friction generating member. In the propeller-shaped friction generating member, a wing portion is provided extending radially from the main body fastening portion 21 toward the plate receiving portion 24. In this case, the back surface of the tip of the wing portion becomes the abutment portion that abuts against the plate receiving portion 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 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, may be employed.

[0062] (e) In the above embodiment, the flywheel body 20 is integrally formed by casting or forging the body fastening portion 21, the elastic spokes 22, the inertia mass 23, and the plate receiving portion 24. Alternatively, each of these portions may be made 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 disc-shaped instead of spoke-shaped. In this case, the disc-shaped elastic plate may have lightening portions in various places.

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

[0065] DESCRIPTION OF THE PREFERRED EMBODIMENTS 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...reverse side 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 therebetween; A flexible flywheel comprising: The flywheel body is an elastic plate that attenuates vibration acting on the shaft by bending the elastic plate itself; 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 an opposite side to the shaft; a contact 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 an 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 abutment portions are provided in a 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 abuts against the abutted portion constitutes the abutting 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 therebetween; A flexible flywheel comprising: The flywheel body is an elastic plate that attenuates vibration acting on the shaft by bending the elastic plate itself; 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 an opposite side to the shaft; a contact 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 an 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 therebetween; A flexible flywheel comprising: The flywheel body is an elastic plate that attenuates vibration acting on the shaft by bending the elastic plate itself; 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 an opposite side to the shaft; a contact 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 an 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 portion of the shaft and the inertial mass, and connecting the two, The abutment portion is provided between the elastic spokes, A flexible flywheel, characterized in that the main body fastening portion, the elastic spokes, the inertial mass, and a receiving portion having the abutment portion are integrally formed by casting or forging.

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