JP5974064B2 - Flywheel - Google Patents

Description

  The present invention relates to a flyhole.

  Generally, in a rotating machine such as an internal combustion engine of a vehicle, a fly hole is attached to one end of a crankshaft. The flywheel has a relatively large moment of inertia, whereby the rotational energy associated with the rotational motion of the crankshaft is conserved, so that a stable rotational motion of the crankshaft is obtained.

  2. Description of the Related Art Conventionally, a fly hole including a metal elastic disk (flexible plate) that absorbs and attenuates bending vibration acting on a crankshaft by elastic deformation is known as a kind of such a fly hole. Such a fly hole is generally called a flexible flywheel, and an elastic disc is fixed to a crankshaft by a bolt or the like, and a mass portion is provided on a peripheral portion of the elastic disc (see, for example, Patent Document 1). ).

  By the way, various attempts have been made to reduce the vibration generated in the vehicle or the like, and a configuration that can contribute to the reduction of the vibration of the vehicle is also required for the flexible flyhole. Therefore, in the flexible flywheel, the natural value of the elastic disk and the power generation part are suppressed so that the natural value (natural frequency) of the elastic disk resonates with the natural value of the power generation part of the rotating machine to suppress vibration amplification. It is proposed to distribute the eigenvalues of.

  In order to achieve such dispersion of eigenvalues, it is preferable to arbitrarily adjust the eigenvalues of the elastic disk in accordance with the eigenvalues of the power generation portion. Is required.

Japanese Utility Model Publication No. 58-151734

  As a means for adjusting the eigenvalue of the elastic disk, for example, changing the thickness of the elastic disk can be considered. This is based on the fact that the eigenvalue of the elastic disk depends on the value of the section modulus. For example, by increasing the thickness of the elastic disk, the numerical value of the section modulus increases, and thereby the eigenvalue of the elastic disk can be shifted to the high frequency side.

  However, when the elastic disk is made thick, the original function of vibration absorption required for the elastic disk is lost, and it is difficult to absorb bending vibrations acting on the crankshaft. turn into. For this reason, in the method of adjusting the eigenvalue by changing the plate thickness, there is a limit in expanding the adjustment range of the eigenvalue, and a sufficient adjustment range cannot be obtained.

  On the other hand, a method of adjusting the eigenvalue by opening a hole for eigenvalue adjustment in the elastic disk is also conceivable. This is a technique that utilizes the fact that the eigenvalue of the elastic disk changes by arbitrarily changing the size, shape, and number of holes. Certainly, the eigenvalue can also be adjusted with this method, and since the plate thickness is not changed, the elastic force does not decrease.However, in the method of making this hole, the range in which the eigenvalue can be adjusted is narrow. I know that I can't get enough adjustment.

  Accordingly, the main object of the present invention is to obtain a flyhole capable of expanding the adjustment range of the eigenvalue while maintaining the elastic force of the elastic disk.

  In order to solve the above problems, the following means were adopted.

In the first aspect of the present invention, an elastic disc that is fixed to an end portion of the shaft of the rotating machine and absorbs vibrations acting on the shaft, and a mass portion provided on the outer peripheral portion of the elastic disc, The elastic disk includes a first elastic disk and a second elastic disk provided closer to the shaft than the first elastic disk, and the elastic disk includes: On the rotation center side, the portions near the inner periphery of the first elastic disc and the second elastic disc are fixed to the end of the shaft in a state of being overlapped with each other, and on the outer periphery side, the first elastic disc A portion near the outer periphery of the disc and the second elastic disc is fixed to the mass portion in a state of being overlapped with each other, and the mass portion is interposed between the first elastic disc and the second elastic disc. The eigenvalue of the elastic disc is adjusted closer to the center of rotation than the fixed part. Wherein the eigenvalues adjusting space for are provided.

  According to the first aspect of the present invention, since the eigenvalue adjustment space is provided between the first elastic disk and the second elastic disk, one elastic circle formed by combining both elastic disks. The section modulus as a plate is determined as having a plate thickness including an eigenvalue adjustment space. A state in which the first elastic disk and the second elastic disk are combined is referred to as an integrated elastic disk.

  By changing the shape and size of the eigenvalue adjustment space (length in the direction of the rotation center axis and length in the radial direction) and changing the thickness of the integrated elastic disk as desired, the numerical value of the section modulus can be set as desired. Can be set to a desired eigenvalue. Since the eigenvalue (natural frequency) can be shifted to the higher frequency side as the eigenvalue adjustment space is expanded, the thickness of one elastic disk is increased, or two elastic disks are stacked. The adjustment range of the eigenvalue can be widened compared to the configuration in which the plate thickness is only increased.

  In the present invention, in order to obtain a section modulus equivalent to that obtained when the plate thickness is simply increased, it is sufficient to adjust the size of the eigenvalue adjustment space, and the plate thicknesses of the first elastic disc and the second elastic disc are sufficient. There is no need to make it unnecessarily thick. That is, the plate thicknesses of the first elastic disc and the second elastic disc are set to thicknesses that can obtain an elastic force that does not hinder vibrations acting on the shaft. Therefore, according to the present invention, it is possible to shift the eigenvalue by changing the size of the eigenvalue adjustment space while maintaining the elastic force of the integrated elastic disk, and to widen the adjustment range of the eigenvalue. In addition, by combining the first elastic disk and the second elastic disk, the rigidity of the integrated elastic disk is increased, so that the durability can be improved.

  According to a second aspect of the present invention, in the first aspect, the eigenvalue adjustment space includes a portion where the first elastic disc and the second elastic disc are fixed to the mass portion and a portion fixed to the shaft. Is provided so as to form an annular shape in a region excluding the portion near the shaft.

  According to the second aspect of the present invention, since the eigenvalue adjustment space is provided so as to form an annular shape in a region excluding the portion near the shaft (near the rotation center), the first elastic disc and the second The area portion where the elastic disk overlaps is reduced. A portion where the first elastic disc and the second elastic disc overlap has a thick plate thickness due to the overlap, and there is a concern that the elastic force may decrease in the portion, but such a region portion is reduced. As a result, even when the rigidity is improved by overlapping the two elastic disks, it is possible to suppress the elastic force of the integrated elastic disk from being unnecessarily lowered by only improving the rigidity appropriately.

In the invention according to claim 3, an elastic disc fixed to the end portion of the shaft of the rotating machine and absorbing vibration acting on the shaft, and a mass portion provided on the outer peripheral portion of the elastic disc, The elastic disk includes a first elastic disk and a second elastic disk provided closer to the shaft than the first elastic disk, and the both are overlapped. In this state, the elastic disc is fixed to the end portion of the shaft on the rotation center side and to the mass portion on the outer peripheral side, and between the first elastic disc and the second elastic disc, An eigenvalue adjustment space for adjusting the eigenvalue of the elastic disc is provided closer to the center of rotation than the fixed portion with the mass portion, and the second elastic disc is closer to the outer periphery fixed to the mass portion. The part has an outer peripheral bulge that bulges in the axial direction of the shaft. The eigenvalue adjustment space is formed using the outer circumferential bulging portion, and a detected object for detecting the number of rotations of the shaft is installed closer to the rotation center than the outer circumferential bulging portion. A detected object installation space is formed.

  According to the third aspect of the present invention, the eigenvalue adjustment space is formed by using the outer peripheral side bulged portion of the second elastic disk, whereby not only the eigenvalue adjustment range can be widened, but also Further, a detected object installation space for installing the detected object is provided on the inner periphery side. As a result, the detected object installation space is formed while widening the adjustment range of the eigenvalue, so that the space can be effectively used.

  According to a fourth aspect of the present invention, in any one of the first to third aspects, the first elastic disk is formed in a flat disk shape and attached to the shaft, An intermediate annular portion that extends from the outer peripheral portion of the mounting disc portion and inclines or curves toward the opposite side of the shaft; and an outer annular portion that extends from the outer peripheral portion of the intermediate annular portion to the mass portion, The eigenvalue adjustment space is formed by using a bulge due to the inclination or curvature of the intermediate annular portion, and the first elastic circle is located on the opposite side of the first elastic disc from the second elastic disc. A disk member fixed to an end of the shaft is provided together with the plate and the second elastic disk, and the disk member includes a contact disk part that contacts the mounting disk part, and a contact circle thereof Provided around the plate part and formed along the intermediate annular part Characterized in that it has a peripheral portion.

  According to the fourth aspect of the present invention, the first elastic disk has the disk member superimposed on the side opposite to the second elastic disk, and is fixed to the shaft in this state. When vibration is applied to the rotating shaft and the integrated elastic disk is elastically deformed, stress due to the elastic deformation concentrates on the portion of the first elastic disk near the rotation center including the mounting disk part and the intermediate annular part. Cheap. In particular, since the stress applied to the rotation center side is greater than that on the outer peripheral side, considerable stress acts on the intermediate annular portion. In that respect, due to the presence of the disc member, elastic deformation in a range including the intermediate annular portion is received by the disc member, so that the rigidity in the intermediate annular portion having a large stress load is increased, and the durability of the first elastic disc is increased. Can be increased.

  According to a fifth aspect of the present invention, in the fourth aspect, the outer annular portion includes a first outer annular portion that extends from the intermediate annular portion, and extends from the first outer annular portion, and is inclined or inclined toward the shaft side. A second outer annular portion that is curved, and a third outer annular portion that extends from the second outer annular portion and is provided with the mass portion at an outer peripheral edge portion. The eigenvalue adjustment space includes the intermediate annular portion and the intermediate annular portion. The second outer annular portion is formed by using a bulge caused by an inclination or a curve.

  In the configuration of the fifth aspect of the present invention, the inclined or curved portion of the first elastic disk includes not only the intermediate annular portion but also the second outer annular portion in a portion closer to the outer periphery. Even in that case, although the disc member is provided for the intermediate annular portion, the disc member is not provided for the second outer annular portion. This is because the second outer annular portion is on the outer peripheral side of the intermediate annular portion, so the magnitude of the stress applied thereto is not as high as that of the intermediate annular portion, but conversely, the disk member is provided up to the second outer annular portion. If a structure is employ | adopted, the elastic force of an integrated elastic disc will be reduced on the contrary. Therefore, even if there are a plurality of inclined or curved parts, the elastic force can be maintained while increasing the rigidity by providing the disk member only in the part near the rotation center where the stress load is large.

  According to a sixth aspect of the present invention, in the fourth or fifth aspect, the outer peripheral portion of the disc member extends to reach the outer annular portion of the first elastic disc.

  According to the sixth aspect of the present invention, since the outer peripheral portion of the disc member extends to the outer annular portion of the first elastic disc, the intermediate annular portion, the outer annular portion, The boundary portion is also a receiving region by the disk member. Since the stress load is relatively large even in such a boundary part, the rigidity of the integrated elastic disk can be increased and the durability can be further improved by receiving the part by the disk member.

  In addition, in the portion near the rotation center of the integrated elastic disc, the plate thickness increases by overlapping with the disc member, and the value of the section modulus increases accordingly, and the eigenvalue is shifted to the higher frequency side accordingly. be able to. Thereby, by providing the disk member, the adjustment range of the eigenvalue can be further widened.

Sectional drawing of a flexible flywheel. It is sectional drawing of the member which comprises a flexible plate, (a) is a 2nd plate, (b) is a 1st plate, (c) has shown each cross section of a center plate. The exploded perspective view of a flexible flywheel. The partial cross section figure which shows the flywheel of another embodiment.

  Hereinafter, an embodiment in which the present invention is applied to a flexible flywheel connected to a crankshaft of an internal combustion engine (engine) of a vehicle as a rotating machine will be described with reference to FIGS. 1 to 3. In addition, FIG. 1 is sectional drawing of a flexible flywheel. 2A and 2B are cross-sectional views of members constituting the flexible plate, where FIG. 2A shows the second plate, FIG. 2B shows the first plate, and FIG. 2C shows each cross section of the center plate. FIG. 3 is an exploded perspective view of the flexible flywheel.

  As shown in FIG. 1, the flexible flywheel 10 includes a flexible plate 11 as an elastic disk and an inertia ring 12. The flexible flywheel 10 is fixed to the crankshaft S by being bolted to the front end of the crankshaft S with a fastening bolt B1 at the center of the flexible plate 11. A circular positioning hole 11 a is formed in the central portion of the flexible plate 11. By inserting the tip protrusion Sa of the crankshaft S into the positioning hole 11a, positioning is performed so that the rotation center of the crankshaft S and the center of the flexible plate 11 are the same.

  The flexible plate 11 includes a first plate 13 as a first elastic disk and a second plate 14 as a second elastic disk, and is configured by superimposing these two plates 13 and 14. Has been. Subsequently, the first plate 13 and the second plate 14 will be described in detail.

  As shown in FIGS. 2 and 3, the first plate 13 and the second plate 14 are both made of metal such as iron and have a disk shape as a whole. Both plates 13 and 14 have the same diameter and the same plate thickness.

  As shown in FIG. 2B and FIG. 3, the first plate 13 includes a mounting disc portion 21, an annular ridge portion 22, and an outer edge annular portion 23. The attachment disc portion 21 is formed in a flat disc shape and has a larger diameter than the tip attachment surface of the crankshaft S. A central hole 21 a having a circular shape is formed in the central portion of the attachment disc portion 21. The positioning hole 11a of the flexible plate 11 is formed by the central hole 21a and the central hole 31a of the second plate 14 described later.

  The annular raised portion 22 is formed in a raised state when viewed from the side (hereinafter referred to as “front side”) opposite to the side where the crankshaft S is present (the engine is present) in the axial direction of the crankshaft S. . The annular raised portion 22 is provided so as to form an annular shape around the attachment disk portion 21, and has an inner tapered portion 24, an annular flat portion 25, and an outer tapered portion 26.

  The inner taper portion 24 extends from the outer peripheral portion of the attachment disc portion 21 and is inclined toward the side opposite to the crankshaft S. The annular flat surface portion 25 extends from the outer peripheral portion of the inner tapered portion 24 and is parallel to the mounting disk portion 21. The outer tapered portion 26 extends from the outer peripheral portion of the annular flat portion 25 and is inclined toward the side where the crankshaft S is present (the engine is present) in the axial direction of the crankshaft S (hereinafter referred to as “back side”). ing.

  The outer edge annular portion 23 is an outer edge portion of the first plate 13 formed so as to extend from the outer peripheral side of the outer tapered portion 26, and is parallel to the attachment disc portion 21. In the present embodiment, the inner tapered portion 24 corresponds to an intermediate annular portion, and the annular raised portion 22 and the outer edge annular portion 23 constitute an outer annular portion. Further, the annular flat portion 25 corresponds to the first outer annular portion, the outer tapered portion 26 corresponds to the second outer annular portion, and the outer edge annular portion 23 corresponds to the third outer annular portion.

  The annular flat surface portion 25 is provided with a number of stress relaxation holes 27a that are through holes penetrating in the plate thickness direction over the entire circumferential direction. Similarly, the outer edge annular portion 23 is provided with a number of stress relaxation holes 27b. By devising the shape, size, number, etc. of these stress relaxation holes 27a, 27b, the ease of bending of the first plate 13 is arbitrarily adjusted, and the stress acting on the first plate 13 is relaxed.

  The mounting disc portion 21 is provided with an inner bolt insertion hole 28, and the outer edge annular portion 23 is provided with an outer bolt insertion hole 29. A plurality of these bolt insertion holes 28 and 29 are provided (eight in FIG. 3), and they are annularly arranged at equal intervals.

  As shown in FIG. 2A and FIG. 3, the second plate 14 has a mounting disc portion 31, an annular bulging portion 32, and an outer edge annular portion 33. The attachment disc portion 31 is formed in a flat disc shape, has a diameter larger than the tip attachment surface of the crankshaft S, and has the same diameter as the attachment disc portion 21 of the first plate 13. A circular central hole 31 a is formed at the central portion of the mounting disc portion 31 and constitutes the positioning hole 11 a of the flexible plate 11 together with the central hole 21 a of the first plate 13.

  The annular bulging portion 32 is in a state of bulging when viewed from the back side (in contrast, in a state of being depressed in the illustration of FIG. 3). The annular bulging portion 32 is provided so as to form an annular shape around the attachment disc portion 31, and has a curved portion 34, an annular flat surface portion 35, and an outer peripheral bulging portion 36.

  The curved portion 34 extends from the outer peripheral portion of the attachment disc portion 31 to the front side of the attachment disc portion 31 and then curves while reaching the back side of the attachment disc portion 31. The annular flat surface portion 35 extends from the outer peripheral portion of the curved portion 34 and is parallel to the mounting disk portion 31. The outer peripheral side bulging portion 36 extends from the outer peripheral portion of the annular flat surface portion 35 and is formed in an annular shape so as to bulge toward the back side. The outer peripheral side bulging portion 36 is provided on the outer peripheral side of the second plate 14.

  The outer edge annular portion 33 is an outer edge portion of the second plate 14 formed so as to extend from the outer peripheral side of the outer peripheral side bulged portion 36, and is parallel to the attachment disc portion 31. The outer edge annular portion 33 has the same width as the outer edge annular portion 23 of the first plate 13, and when the mounting disk portions 21, 31 of both plates 13, 14 are overlapped, as shown in FIG. The outer peripheral annular portions 23 and 33 are also formed so as to overlap each other.

  Returning to FIG. 2A and FIG. 3, a large number of stress relaxation holes 37 a that are through holes penetrating in the plate thickness direction are provided throughout the circumferential direction in the portion from the curved portion 34 to the annular flat surface portion 35. . Similarly, a large number of stress relaxation holes 37b and 37c are provided in the outer edge annular portion 33 and the outer peripheral side bulging portion 36 as well. By devising the shape, size, number, etc. of the stress relaxation holes 37a, 37b, 37c, the ease of bending of the second plate 14 is arbitrarily adjusted, and the stress acting on the second plate 14 is relaxed.

  The mounting disc portion 31 is provided with an inner bolt insertion hole 38, and the outer edge annular portion 33 is provided with an outer bolt insertion hole 39. These bolt insertion holes 38 and 39 are both provided in a plural number or a large number (eight in FIG. 3), and are arranged annularly at equal intervals.

  Next, the inertia ring 12 is made of cast iron, and is formed in an annular shape as shown in FIG. The annular portion of the inertia ring 12 is a mass portion 41, and when the flexible flywheel 10 rotates, a relatively large moment of inertia force can be obtained by the weight of the mass portion 41.

  As shown in FIG. 1, a mounting groove 42 is formed on the flexible plate 11 side of the mass portion 41. The mounting groove 42 is formed according to the size of each of the plates 13 and 14 so that the first plate 13 and the second plate 14 can be accommodated in the mounting groove 42. Further, a bolt hole 43 in which a female screw is formed is provided on the bottom surface portion of the mounting groove 42. The same number of the bolt holes 43 as the outer bolt insertion holes 29 and 39 of the outer edge annular portions 23 and 33 in the plates 13 and 14 are provided, and they are arranged at equal intervals.

  The first plate 13 is first fitted in the mounting groove 42 of the inertia ring 12, and then the second plate 14 is fitted in order. In a state where both the plates 13 and 14 are fitted, the outer edge annular portion 23 of the first plate 13 and the outer edge annular portion 33 of the second plate 14 are in surface contact. After that, the positions of the outer bolt insertion holes 29 and 39 and the bolt holes 43 are aligned, and the first plate 13 and the second plate 14 and the inertia ring 12 are connected by the fastening bolt B2. Thereby, the flexible flywheel 10 by which both plates 13 and 14 and the inertia ring 12 are integrated is obtained.

  In such a flexible flywheel 10, the mounting disc portion 21 of the first plate 13 and the mounting disc portion 31 of the second plate 14 are in surface contact with the same center position, and the plates 13 and 14 are integrated. Thus, one flexible plate 11 is formed. The positions of the inner bolt insertion holes 28 and 38 provided in the mounting disk portions 21 and 31 are also in a combined state. The back surface of the flexible plate 11, that is, the back surface of the second plate 14 (the left surface in FIG. 1) serves as a mounting surface to the crankshaft S.

  Further, in a state where the plates 13 and 14 are overlapped and integrated with the inertia ring 12, the plates are surrounded by both the annular bulging portion 22 of the first plate 13 and the annular bulging portion 32 of the second plate 14. An annular space portion 15 is formed. The annular space 15 corresponds to an eigenvalue adjustment space. The annular bulging portion 22 and the annular bulging portion 32 are provided in annular regions between the attachment disc portions 21 and 31 and the outer edge annular portions 23 and 33, respectively, and the annular space portion 15 is close to the rotation center of the flexible plate 11. From the position to the fixed portion with the mass portion 41.

  The flexible flywheel 10 thus configured is fixed to the crankshaft S as follows.

  That is, as shown in FIG. 1, the rear surface of the attachment disc portion 31 of the second plate 14 is inserted into the end surface of the crankshaft S while the front end protrusion Sa of the crankshaft S is inserted into the positioning hole 11 a of the flexible plate 11. Make contact. Thereafter, the fastening bolt B1 is inserted into the inner bolt insertion holes 28, 38 of the mounting disk portions 21, 31, and the flexible plate 11 is bolted. Thereby, the flexible flywheel 10 is fixed to the crankshaft S. In the fixing to the crankshaft S, the bolt is tightened from the front side of the flexible plate 11 by the fastening bolt B1. This bolting direction is opposite to the bolting direction when the first plate 13 and the second plate 14 are connected to the inertia ring 12 on the outer peripheral side thereof.

  In a state where the flexible flywheel 10 is fixed to the crankshaft S, a space region A is formed on the back side of the second plate 14 as shown in FIG. This is because the annular bulging portion 32 of the second plate 14 is provided with an outer peripheral bulging portion 36 that bulges further from the annular flat surface portion 35 toward the shaft side. On the outer peripheral side of the flexible flywheel 10, the presence of the outer peripheral bulging portion 36 forms a space between the crankshaft S and the space region A on the rotational center side. Yes.

  If this space area A is used, it is possible to install a sensor plate (not shown) for detecting the rotational speed of the crankshaft S. The sensor plate corresponds to a detection object for detecting the number of rotations, and the space area A corresponds to a detection object installation space.

  By the way, when fixing to such a crankshaft S, as shown in FIG. 1, the center plate 51 is provided in the front side of the flexible plate 11, ie, the front side of the 1st plate 13. As shown in FIG. That is, the flexible plate 11 has the center plate 51 superimposed on the mounting disc portion 21 of the first plate 13 and its peripheral portion, and is fixed to the end of the crankshaft S by the fastening bolt B1 in that state.

  As shown in FIGS. 2C and 3, the center plate 51 is made of a metal material such as iron and has a disk shape as a whole. The center plate 51 corresponds to a disk member. The diameter of the center plate 51 is larger than the combined diameter of the mounting disc portion 21 and the inner tapered portion 24 of the first plate 13. Further, the center plate 51 has a shape that follows the attachment disc portion 21 and the inner taper portion 24, and is thereby divided into a center disc portion 52, a first outer peripheral portion 53, and a second outer peripheral portion 54. The In this embodiment, the central disk portion 52 corresponds to the contact disk portion, and the first outer peripheral portion 53 and the second outer peripheral portion 54 constitute the outer peripheral portion.

  The central disc portion 52 has the same diameter as the attachment disc portion 21 of the first plate 13 and has a flat disc shape. A central circular hole 52 a having the same diameter as the central holes 21 a and 31 a of the plates 13 and 14 is formed in the central portion of the central disk portion 52. The center circular hole 52a is a hole for positioning the center plate 51, and the front end protrusion Sa of the crankshaft S is inserted therein. Further, the central disc portion 52 is provided with the same number (8 in FIG. 3) of bolt insertion holes 55 as the inner bolt insertion holes 28 of the attachment disc portion 21.

  The first outer peripheral portion 53 extends from the outer peripheral portion of the central disk portion 52 and is formed in an annular shape with the same width and the same inclination angle as the inner tapered portion 24.

  The second outer peripheral portion 54 is an outer peripheral edge portion of the center plate 51, and is provided in an annular shape on the outer peripheral side of the first outer peripheral portion 53. The second outer peripheral portion 54 is formed in a state parallel to the central disc portion 52. For this reason, when the center plate 51 is superimposed on the first plate 13, the second outer peripheral portion 54 comes into contact with the annular flat portion 25 of the first plate 13 as shown in FIG. 1. Therefore, in the overlapped state, the outer peripheral edge of the center plate 51 extends from the inner taper portion 24 of the first plate 13 to a portion closer to the inner periphery of the annular flat surface portion 25 due to the presence of the second outer peripheral portion 54. It has been installed.

  When the flexible flywheel 10 is fixed to the crankshaft S, the back surface of the center plate 51 is brought into contact with the surface of the first plate 13 and overlapped. As a result, the center plate 51 overlaps the inner disk portions 21 of the first plate 13, the inner tapered portion 24, and the annular flat surface portion 25, and the portions are in surface contact with each other. . In this state, the fastening bolt B1 is inserted into the bolt insertion hole 55 of the center plate 51 and the inner bolt insertion holes 28 and 38 of the plates 13 and 14, and the flexible plate 11 is bolted by the fastening bolt B1.

  Next, the operation of the flexible flywheel 10 having the above configuration will be described.

  Since the flexible flywheel 10 is provided at the end of the crankshaft S, an inertia moment is generated by the mass portion 41 of the inertia ring 12, whereby a stable rotating operation of the crankshaft S is obtained. When bending vibration or the like acts on the crankshaft S due to the driving of the engine, the flexible plate 11 composed of the two plates 13 and 14 is elastically deformed and absorbs and attenuates the bending vibration and the like. Thereby, vibration etc. are suppressed, obtaining the stable rotation operation of the crankshaft S.

  Here, in the flexible flywheel 10, an annular space portion 15 is provided between the first plate 13 and the second plate 14. In this case, with respect to the natural value (natural frequency) of the flexible plate 11 composed of both the plates 13 and 14, the section modulus of the flexible plate 11 is determined as having a plate thickness including the annular space portion 15. The eigenvalue is determined by the value of the section modulus. In the flexible flywheel 10 of this embodiment, a single plate is used, or a flexible plate in which two flat disk-shaped plates are overlapped is used. The eigenvalue is shifted to the higher frequency side than the case.

  In addition, the flexible plate 11 is fixed to the crankshaft S in a state where the center plate 51 is superimposed on the first plate 13 at a portion near the inner periphery of the flexible plate 11. For this reason, if a stress acts on a portion near the inner periphery of the flexible plate 11 due to bending vibration of the crankshaft S and the flexible plate 11 tries to deform toward the front side in the axial direction, the deformation is caused by the center plate 51. Received by. For this reason, the rigidity of the portion near the inner periphery of the flexible plate 11 is increased.

  According to the flexible flywheel 10 of the present embodiment described in detail above, the following excellent effects can be obtained.

  As described above, the value of the section coefficient as the flexible plate 11 is increased by the annular space 15 provided between the first plate 13 and the second plate 14, and the eigenvalue is shifted to the high frequency side. ing. Thereby, dispersion | distribution with the eigenvalue of the motive power generation part of an engine can be aimed at, and the vibration amplification by resonance can be suppressed.

  In the configuration having the annular space 15 as described above, the numerical value of the section modulus as the flexible plate 11 is changed depending on the shape and size of the annular space 15 (the length in the rotation center axis direction and the length in the radial direction). . Therefore, if the shape and size of the annular space portion 15 are arbitrarily changed, the numerical value of the section modulus of the flexible plate 11 can be arbitrarily set and set to a desired eigenvalue. Therefore, it is possible to widen the adjustment range of the eigenvalue compared to a configuration in which the plate thickness of one plate is increased or the plate thickness is increased by overlapping two plates.

  In addition, since the eigenvalue can be changed by changing the size of the annular space 15, it is necessary to unnecessarily increase the thickness of the first plate 13 and the second plate 14 in order to raise the eigenvalue to a high frequency range. There is no. That is, it is sufficient to set the thicknesses of the first plate 13 and the second plate 14 to such a thickness that an elastic force that does not hinder the absorption of vibrations acting on the crankshaft S can be obtained.

  Accordingly, the flexible plate 11 is constituted by the first plate 13 and the second plate 14 and the annular space portion 15 is formed therebetween, so that the adjustment range of the eigenvalue is widened while maintaining the elastic force of the flexible plate 11. Can do. Moreover, since the rigidity as the flexible plate 11 is increased by combining the first plate 13 and the second plate 14, the durability can be improved.

  The annular space portion 15 is provided so as to form an annular shape in a region excluding the portion close to the crankshaft S (close to the rotation center). For this reason, the area part where the 1st plate 13 and the 2nd plate 14 overlap becomes the attachment disc parts 21 and 31 of a center part, and such an overlap area decreases. As a result, even when the rigidity is improved by overlapping the first plate 13 and the second plate 14, it is possible to suppress the elastic force of the flexible plate 11 from being reduced more than necessary only by improving the rigidity appropriately.

  The outer peripheral side bulging portion 36 of the second plate 14 is formed to bulge further outward than the annular flat surface portion 35. Thus, when the flexible flywheel 10 is fixed to the crankshaft S, a space region A in which a sensor plate (not shown) can be installed is formed on the inner peripheral side of the outer peripheral side bulging portion 36. Is done. Thereby, space can be used effectively.

  The flexible plate 11 is fixed to the crankshaft S in a state where the center plate 51 is superimposed on a portion of the first plate 13 closer to the inner periphery. Thereby, if the portion near the inner periphery of the crankshaft S is deformed to the front side in the axial direction due to bending vibration of the crankshaft S, the deformation is received by the center plate 51. Thereby, the rigidity in the site | part near the inner periphery with a large stress load can be improved, and durability as the flexible plate 11 can be improved.

  The first plate 13 has two inclined portions, that is, an inner tapered portion 24 and an outer tapered portion 26, but the center plate 51 is not provided in the outer tapered portion 26. The outer taper portion 26 is on the outer peripheral side of the inner taper portion 24, and the magnitude of stress applied thereto is not as great as that of the inner taper portion 24. Conversely, if the center plate 51 is expanded to reach the outer tapered portion 26, the elastic force of the first plate 13 is reduced. In that respect, since the center plate 51 is provided only in the inner tapered portion 24 near the rotation center where the stress load is large, the elastic force can be maintained while increasing the rigidity.

  Since the center plate 51 has the second outer peripheral portion 54, the boundary portion between the inner tapered portion 24 and the annular flat portion 25 of the first plate 13 is also a receiving region by the center plate 51. Since the stress load is relatively large at such a boundary portion, the deformation of the portion is received by the center plate 51, whereby the rigidity of the flexible plate 11 can be increased and the durability can be further improved.

  Further, in the portion near the rotation center of the flexible plate 11, the plate thickness increases due to the overlap of the center plate 51, the value of the section modulus increases accordingly, and the eigenvalue is shifted to the higher frequency side accordingly. Thereby, by providing the center plate 51, the adjustment range of the eigenvalue can be further expanded.

[Other Embodiments]
(1) In the above embodiment, the annular space portion 15 is provided over almost the entire region except the portion near the crankshaft S (close to the rotation center). It is not limited and is arbitrary. FIG. 4 shows an example of a flexible flywheel 10 having an annular space of another form.

  As shown in FIG. 4, in the flexible plate 61 of the flexible flywheel 10, the annular bulge portion 72 of the first plate 63 has a smaller degree of bulge than the annular bulge portion 22 of the above embodiment. The second plate 64 has an inner tapered portion 84 that is inclined from the outer peripheral portion of the attachment disc portion 81 toward the front side and has a shape along the inner tapered portion 74 of the first plate 63. Further, the annular flat surface portion 85 of the second plate 64 is in contact with the annular flat surface portion 75 of the first plate 63, and an outer peripheral side expansion portion 86 extending from the outer peripheral portion is provided. In this alternative embodiment, the center plate 51 is not provided.

  Unlike the annular space portion 15 of the above-described embodiment, the annular space portion 65 in such a configuration is provided only in a portion near the outer periphery, and the cross-sectional shape and the cross-sectional area thereof are smaller than those of the above-described embodiment. Even in the configuration having the annular space 65 of this different form, the eigenvalue of the flexible plate 61 can be raised to a high frequency range. And the flexible plate 11 of the said embodiment and the flexible plate 61 of this another form differ in the magnitude | size and installation location of the annular space parts 15 and 65, Therefore It has a different eigenvalue with the difference in the value of a section modulus. Thus, if the magnitude | size and installation location of the cyclic | annular space parts 15 and 65 are changed, it can adjust by changing a characteristic value.

  Further, in the flexible plate 61 of this different form, the annular flat portions 75 and 85 of both plates 63 and 64 are in contact with each other, so that the space area A is wider than that of the above embodiment. Can be secured and the space can be used effectively. Although the space area A has an annular shape, FIG. 4 shows only the space area A at the bottom of the drawing, and omits the space area A at the top of the drawing.

  Further, in the flexible plate 61 of this different form, the stress adjusting holes 77a and 87a are formed in the portions where the annular flat portions 75 and 85 of the plates 63 and 64 overlap with each other at the same position. That is, the flexible plate 61 is penetrated in the thickness direction by the stress adjusting holes 77a and 87a. Thereby, not the ease of bending as the individual plates 63 and 64 but the ease of bending as the single flexible plate 61 in which both are overlapped can be provided.

  (2) In the above embodiment, the configuration in which one annular space portion 15 is formed in the flexible plate 11 is adopted. However, a configuration in which a plurality of annular space portions 15 having an annular shape is formed may be employed. . For example, the shape of the annular bulging portion 22 and the annular bulging portion 32 is changed, and between the attachment disc portions 21 and 31 and the outer edge annular portions 23 and 33, two of the intermediate portion and the portion near the outer periphery are provided. An annular space 15 may be formed.

  (3) In the above embodiment, the configuration in which the center plate 51 is provided is adopted, but a configuration in which the center plate 51 is omitted may be adopted. The presence of the center plate 51 provides rigidity at a portion near the rotation center. However, the overlapping of the mounting disk portions 21 and 31 of both plates 13 and 14 increases the rigidity as compared with the case of one sheet. Yes.

  (4) Although the center plate 51 has the second outer peripheral portion 54 on the outer peripheral side of the first outer peripheral portion 53 in the above embodiment, a configuration in which the second outer peripheral portion 54 is omitted may be adopted. Good. Even with such a configuration, the deformation of the inner tapered portion 24 where stress tends to concentrate can be received by the center plate 51, so that the rigidity of the flexible plate 11 can be increased. However, in terms of improving rigidity, a configuration having the second outer peripheral portion 54 as in the present embodiment is preferable.

  (5) In the above-described embodiment, the flexible plate 11 and the center plate 51 are configured to directly contact and overlap each other, but a buffer member such as a vibration-proof rubber may be interposed therebetween. Thereby, the friction between the flexible plate 11 and the center plate 51 is suppressed by the buffer member interposed therebetween, and the damage to the flexible plate 11 can be further suppressed.

  (6) In the above embodiment, the configuration of the end edge portion of the second outer peripheral portion 54 of the center plate 51 is not particularly described, but the side (back side) that contacts the first plate 13 is the first plate 13. You may form so that it may gradually move away from. Thereby, these edge parts become round in the circumferential direction whole region, and it can suppress that the 1st plate 13 is damaged by the collision with the 1st plate 13.

  (7) In the above embodiment, the flexible plate 11 is constituted by the first plate 13 and the second plate 14, but a configuration in which the number of plates is increased to three or more may be adopted. In this case, you may form another annular space part using the increased plate.

  (8) In the above embodiment, the first plate 13 has the inner tapered portion 24 as the intermediate annular portion and the outer tapered portion 26 as the second outer annular portion. The annular portion may not be inclined linearly but may be curved in the axial direction of the crankshaft S.

  (9) In the above embodiment, the space area A formed on the back side of the second plate 14 is used as a space for installing a sensor plate (not shown) for detecting (detecting) the number of rotations of the crankshaft S. used. Instead of this, the space area A may be used as a concave space for avoiding interference with a member (for example, a cylinder block that is a member constituting the engine) disposed in the vicinity of the flexible plate 11. . In other words, a concave space for avoiding interference with a member provided on the back side of the second plate 14 may be formed on the rotation center side of the outer peripheral side bulging portion 36 of the second plate 14. . Even if the space area A is used as such a space, the space can be used effectively.

  (10) In the above embodiment, the internal combustion engine (engine) of the vehicle is assumed as the rotating machine. However, the application of the present invention is not limited to this, and the stabilization of rotation and the rotational energy using the moment of inertia. As long as it is used for the purpose of preserving the storage, for example, its application target is arbitrary such as a press machine.

  DESCRIPTION OF SYMBOLS 10 ... Flexible flywheel, 11 ... Flexible plate (elastic disk), 13 ... 1st plate (1st elastic disk), 14 ... 2nd plate (2nd elastic disk), 15 ... Annular space part (Eigen value adjustment) Space), 21 ... mounting disk part, 22 ... annular ridge part (outer annular part), 23 ... outer edge annular part (outer annular part, third outer annular part), 24 ... inner taper part (intermediate annular part), 25 ... annular flat surface part (second outer annular part), 26 ... outer taper part (outer annular part, second outer annular part), 36 ... outer peripheral side bulging part, 41 ... mass part, 51 ... center plate (disc member) ), 52... Central disc portion (contact disc portion). 53 ... 1st outer peripheral part (outer peripheral part), 54 ... 2nd outer peripheral part (outer peripheral part), A ... Space area (detected body installation space), S ... Crankshaft (shaft).

Claims (6)

An elastic disc that is fixed to the end of the shaft of the rotating machine and absorbs vibration acting on the shaft;
A mass portion provided on an outer peripheral portion of the elastic disc;
A flywheel with
The elastic disk includes a first elastic disk and a second elastic disk provided closer to the shaft than the first elastic disk, and the first elastic disk includes a first elastic disk on the rotation center side of the first elastic disk. The elastic disc and the second elastic disc are fixed to the end of the shaft in a state of being overlapped with each other, and on the outer peripheral side, the first elastic disc and the second elastic disc are fixed. The part near the outer periphery of the plate is fixed to the mass part in a state where both are overlapped ,
Between the first elastic disk and the second elastic disk, an eigenvalue adjustment space for adjusting the eigenvalue of the elastic disk is provided closer to the center of rotation than the portion fixed to the mass portion. A flywheel characterized by   The eigenvalue adjustment space excludes a portion near the shaft among a portion where the first elastic disc and the second elastic disc are fixed to the mass portion and a portion fixed to the shaft. The flywheel according to claim 1, wherein the flywheel is provided so as to form an annular shape in the region. An elastic disc that is fixed to the end of the shaft of the rotating machine and absorbs vibration acting on the shaft;
A mass portion provided on an outer peripheral portion of the elastic disc;
A flywheel with
The elastic disk is formed by superimposing a first elastic disk and a second elastic disk provided closer to the shaft than the first elastic disk, and in a state in which both are superimposed. The rotation center side is fixed to the end of the shaft, and the outer periphery side is fixed to the mass portion.
Between the first elastic disk and the second elastic disk, an eigenvalue adjustment space for adjusting the eigenvalue of the elastic disk is provided closer to the center of rotation than the portion fixed to the mass portion. ,
The second elastic disk has an outer peripheral side bulging portion that swells in the axial direction of the shaft at a portion near the outer periphery fixed to the mass portion, and the eigenvalue is obtained using the outer peripheral side bulging portion. An adjustment space is formed,
Wherein the rotation center side than the outer peripheral side expansion, flywheel you characterized by sensing object installation space for installing the sensing object for detecting the rotational speed of the shaft is formed. The first elastic disk is formed in a flat disk shape, and is attached to the shaft, extends from an outer periphery of the mounting disk part, and inclines toward the opposite side of the shaft or A curved intermediate annular portion, and an outer annular portion extending from the outer peripheral portion of the intermediate annular portion to the mass portion;
The eigenvalue adjustment space is formed using a bulge caused by the inclination or curvature of the intermediate annular portion,
On the opposite side of the first elastic disk from the second elastic disk, a disk member fixed to the end of the shaft is provided together with the first elastic disk and the second elastic disk. And
The disc member includes a contact disc portion that abuts on the attachment disc portion, and an outer peripheral portion that is provided around the contact disc portion and is formed along the intermediate annular portion. The flywheel according to any one of claims 1 to 3, wherein the flywheel is provided. The outer annular portion includes a first outer annular portion extending from the intermediate annular portion, a second outer annular portion extending from the first outer annular portion and inclined or curved toward the shaft side, and a second outer annular portion thereof. A third outer annular portion extending from the portion and provided with the mass portion on the outer peripheral edge portion;
5. The flywheel according to claim 4, wherein the eigenvalue adjustment space is formed using a bulge caused by an inclination or a curve of the intermediate annular portion and the second outer annular portion.   6. The flywheel according to claim 4, wherein an outer peripheral portion of the disc member extends to reach the outer annular portion of the first elastic disc.

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