CN211449508U - Dynamic damper - Google Patents

Abstract

The utility model provides a dynamic damper can obtain stable frequency characteristic via the settlement of spring, and then improves space efficiency. The dynamic damper includes: a cylindrical portion for mounting on an outer periphery of the rotating shaft; a weight portion disposed coaxially with the cylindrical portion and spaced apart from a radially outer side of the cylindrical portion; and a coupling portion that couples the cylindrical portion and the weight portion in a radial direction, wherein the coupling portion includes a plurality of springs that extend in the radial direction, respectively, and the springs are disposed between the weight portion and an outer periphery of the cylindrical portion, respectively.

Description

Dynamic damper

Technical Field

The present invention relates to a dynamic damper (dynamic damper), and more particularly to a dynamic damper for a rotating shaft of a vehicle.

Background

As is well known, a vibration damping device such as a dynamic damper for suppressing vibration is generally mounted on a rotating shaft such as a drive shaft (drive shaft) of a vehicle. For example, the dynamic damper is constructed in the following manner: on the radial outside of a boss (boss) which is a cylindrical portion attached to the outer periphery of the rotating shaft, a weight portion for holding a weight (weight) coaxially via a rubber elastic body which is a coupling portion in the radial direction is provided, and the cylindrical portion and members such as the weight portion are integrally vulcanization molded via the rubber elastic body. In this way, when a rotary shaft such as a drive shaft of a vehicle transmits or receives vibration, impact, or the like generated by an engine (engine), the dynamic damper is attached to the rotary shaft, and the vibration is absorbed and reduced in the rotary shaft, whereby transmission of vibration and noise of the rotary shaft is prevented, and the stress amplitude of the rotary shaft is suppressed, and fatigue breakage is prevented.

In order to adjust the damping effect of a vibration damping device such as a dynamic damper, the hardness or the sectional shape of the rubber elastic body may be adjusted. However, if the hardness or the cross-sectional shape of the rubber elastic body is adjusted to obtain a specific frequency, a specific mold must be used for each hardness or cross-sectional shape of the rubber elastic body, and the versatility is low. Also, the change in frequency characteristics is large due to aging and deterioration in durability of the rubber elastic body. Further, when there are a plurality of frequencies according to the number of rotations, it is necessary to provide a plurality of dynamic dampers corresponding to the respective frequencies, resulting in poor space efficiency.

[ Prior art documents ]

[ patent document ]

[ patent document 1] Japanese Utility model publication No. JP S59-22362

[ patent document 2] Japanese patent publication No. JP H02-31928

[ patent document 3] Japanese Utility model publication No. JP H04-84845

[ patent document 4] Japanese patent publication No. JP H11-192848

SUMMERY OF THE UTILITY MODEL

The utility model provides a dynamic damper can obtain stable frequency characteristic via the settlement of spring, and then improves space efficiency.

The utility model provides a dynamic damper, dynamic damper includes: a cylindrical portion for mounting on an outer periphery of the rotating shaft; a weight portion disposed coaxially with the cylindrical portion and spaced apart from a radially outer side of the cylindrical portion; and a coupling portion that couples the cylindrical portion and the weight portion in a radial direction, wherein the coupling portion includes a plurality of springs that extend in the radial direction, respectively, and the springs are disposed between the weight portion and an outer periphery of the cylindrical portion, respectively.

In an embodiment of the present invention, the inner surface of the weight portion is provided with a plurality of grooves recessed in the radial direction, and the springs are respectively provided in the corresponding grooves and abut against the outer periphery of the cylindrical portion.

In an embodiment of the present invention, the connection portion further includes a cover and a retaining ring disposed in the groove, the retaining ring is disposed in the groove, the cover is disposed radially inward of the retaining ring, and the spring is disposed between the cover and the outer periphery of the cylindrical portion.

In an embodiment of the present invention, a spring is further disposed between the cover and the retainer ring, and the connection portion constitutes a double-layer spring structure.

In an embodiment of the present invention, a sleeve is disposed on an outer periphery of the cylindrical portion, and the spring is disposed radially outside the sleeve.

In an embodiment of the present invention, the counterweight portion is formed with a drainage hole penetrating in a radial direction.

In an embodiment of the present invention, the outer periphery of the cylindrical portion is provided with a spring bearing seat having a curved surface, and the spring bearing seat constitutes a structure capable of rotating at the center of the dynamic damper.

In view of the above, in the dynamic damper of the present invention, the weight portion is disposed separately from the radial outside of the cylindrical portion, and the coupling portion radially couples the cylindrical portion and the weight portion, wherein the coupling portion includes a plurality of springs respectively extending in the radial direction, and the springs are respectively provided between the outer peripheries of the weight portion and the cylindrical portion. Thus, compared with the prior art that the cylindrical part and the counterweight part are vulcanized and molded together through the rubber elastic body, the dynamic damper of the utility model separately manufactures the cylindrical part and the counterweight part and uses the spring to replace the rubber elastic body as the connecting part, thereby obtaining the required frequency through adjusting the parameters, the quantity and the position of the spring, having higher universality without using a special die to manufacture the rubber elastic body, and the frequency characteristic of the spring caused by aging and durability reduction is less than that of the rubber elastic body, therefore, the frequency characteristic is more stable. Accordingly, the dynamic damper of the present invention can obtain stable frequency characteristics by setting the spring, thereby improving space efficiency.

In order to make the aforementioned and other features and advantages of the present invention comprehensible, embodiments accompanied with figures are described in detail below.

Drawings

Fig. 1 is a schematic side view of a dynamic damper according to a first embodiment of the present invention mounted on a rotating shaft;

FIG. 2 is a side schematic view of the dynamic damper of the first embodiment shown in FIG. 1;

FIG. 3 is a schematic front view of the dynamic damper of the first embodiment shown in FIG. 1;

fig. 4 is a schematic side view of a dynamic damper according to a second embodiment of the present invention mounted on a rotating shaft;

FIG. 5 is a side schematic view of the second embodiment of the dynamic damper shown in FIG. 4;

FIG. 6 is a schematic front view of the dynamic damper of the second embodiment shown in FIG. 4;

fig. 7 is a schematic side view of a dynamic damper according to a third embodiment of the present invention mounted on a rotating shaft;

FIG. 8 is a side schematic view of the dynamic damper of the third embodiment shown in FIG. 7;

FIG. 9 is a schematic front view of the dynamic damper of the third embodiment shown in FIG. 7;

FIG. 10 is a schematic side view of a dynamic damper of a fourth embodiment having a spring bearing seat with a curved surface added to the outer periphery of the cylindrical portion of FIG. 1, mounted on a rotating shaft;

FIG. 11 is a schematic side view of a fifth embodiment of the dynamic damper mounted on a rotating shaft, in which a spring bearing seat having a curved surface is added to the outer periphery of the cylindrical portion as compared to FIG. 4;

fig. 12 is a schematic side view of the dynamic damper of the sixth embodiment in which a spring bearing seat having a curved surface is added to the outer periphery of the cylindrical portion in fig. 7, the dynamic damper being attached to the rotating shaft.

Description of reference numerals:

50: a rotating shaft;

100. 100A, 100B, 100C, 100D, 100E: a dynamic damper;

110: a cylindrical portion;

120. 120B: a counterweight portion;

122. 124: a groove;

130. 130A, 130B: a connecting portion;

132. 138: a spring;

134: a cover;

136: a retainer ring;

140. 140A: a sleeve;

150: a spring bearing seat;

160: a drain hole;

l: axial direction;

r: and radial direction.

Detailed Description

Fig. 1 is a schematic side view of a dynamic damper 100 according to a first embodiment of the present invention mounted on a rotating shaft 50, fig. 2 is a schematic side view of the dynamic damper 100 of the first embodiment shown in fig. 1, and fig. 3 is a schematic front view of the dynamic damper 100 of the first embodiment shown in fig. 1. In the present embodiment, the dynamic damper 100 is annular and is suitable for mounting on the radially R outer side of the rotating shaft 50 such as a drive shaft of a vehicle. However, the present invention does not limit the installation position of the dynamic damper 100, that is, the dynamic damper 100 can be provided on other types of shafts. The overall configuration of the dynamic damper 100 of the present embodiment will be described below with reference to fig. 1 to 3, in which an axial direction L refers to an extending direction of the rotating shaft 50 and the dynamic damper 100, a radial direction R refers to a direction of a diameter of the rotating shaft 50 and is perpendicular to the axial direction L, and a circumferential direction (not shown) refers to a direction along a circumference of the rotating shaft 50.

Referring to fig. 1 to 3, in the present embodiment, the dynamic damper 100 includes a cylindrical portion 110, a weight portion 120, and a connecting portion 130. The cylindrical portion 110 is, for example, a boss, has a cylindrical shape, and is attached to the outer periphery of the rotating shaft 50, and the axial center of the cylindrical portion 110 coincides with the axial direction L of the rotating shaft 50. The weight portion 120 is, for example, an annular mass and includes a metal weight. The weight portion 120 is disposed coaxially with the cylindrical portion 110 and spaced apart from the outside of the cylindrical portion 110 in the radial direction R. That is, the center of the weight 120 coincides with the axial direction L of the rotary shaft 50. The coupling portion 130 couples the cylindrical portion 110 and the weight portion 120 in the radial direction R. In this way, the dynamic damper 100 can displace the weight portion 120 relative to the cylindrical portion 110 through the coupling of the coupling portion 130, thereby reducing the vibration of the rotary shaft 50.

In the present embodiment, the coupling portion 130 includes a plurality of springs 132 each extending in the radial direction R, and five springs 132 are illustrated as an example in fig. 3. The springs 132 are arranged at equal intervals in the circumferential direction, that is, the springs 132 are arranged in parallel between the outer periphery of the cylindrical portion 110 and the inner surface of the weight portion 120. However, the present invention is not limited to the parameters (such as size, elastic modulus, etc.), the number, the position and the arrangement of the springs 132, and the number, the position and the arrangement can be adjusted according to the requirement.

Further, in the present embodiment, the sleeve 140 is provided on the outer periphery of the cylindrical portion 110. The sleeve 140 is annular and is fitted around the outer circumference of the cylindrical portion 110. Therefore, the dynamic damper 100 can omit the provision of a band (band) for preventing the expansion of the cylindrical portion 110 in the related art. The spring 132 is disposed radially outward of the sleeve 140. That is, the springs 132 are respectively provided between the weight portion 120 and the sleeve 140 provided on the outer periphery of the cylindrical portion 110. The sleeve 140 and the cylindrical portion 110 may be integrally formed, but may be separately provided, and the present invention is not limited thereto.

Further, in the present embodiment, the inner surface of the weight portion 120 is provided with a plurality of grooves 122 recessed in the radial direction R, and as shown in fig. 3, five grooves 122 are taken as an example, and the grooves 122 are arranged in a dispersed manner at equal intervals in the circumferential direction. However, the present invention is not limited to the parameters (such as size), number, position and arrangement of the grooves 122, and the number, position and arrangement can be adjusted according to the requirement.

By the arrangement of the grooves 122, the springs 132 are respectively disposed in the corresponding grooves 122 and abut against the sleeve 140 disposed on the outer periphery of the cylindrical portion 110. That is, the groove 122 is a recessed structure disposed on the inner surface of the weight 120 but does not penetrate through the weight 120, most of the spring 132 is embedded in the corresponding groove 122, and one end of the spring 132 extends out of the groove 122 to connect the sleeve 140, so that the spring 132 serves as a connecting portion to connect the weight 120 and the sleeve 140. However, the present invention is not limited to disposing the spring 132 in the groove 122, and the installation structure of the spring 132 on the inner surface of the weight portion 120 may be adjusted as required.

In addition, in the present embodiment, the inner surface of the weight portion 120 is provided with a plurality of grooves 124 recessed in the radial direction R, and five grooves 124 are illustrated as an example in fig. 3. The concave grooves 124 are arranged in a dispersed manner at equal intervals in the circumferential direction and penetrate the weight portion 120. More specifically, the grooves 122 and the grooves 124 are arranged in a staggered manner at equal intervals in the circumferential direction. However, the present invention is not limited to the parameters (such as size), number, position and arrangement of the grooves 124, and the number, position and arrangement can be adjusted according to the requirement.

By providing the groove 124, although not shown in the drawings, a connection portion such as another spring may be disposed in the groove 124 according to the requirement. Alternatively, in the case where no additional spring is provided, the groove 124 may be omitted, and the present invention does not limit whether the groove 124 is provided or not.

In the present embodiment, the dynamic damper 100 may further include a water drain hole 160 formed in the weight 120 to penetrate in the radial direction R as needed. Preferably, five drainage holes 160 are formed through the weight 120 at positions corresponding to the grooves 122, so that the drainage holes 160 communicate the inner surface and the outer surface of the weight 120 in the radial direction R through the grooves 122. In this way, even if muddy water or the like enters the rotary shaft 50 from the outside of the vehicle and then enters the dynamic damper 100, it can be discharged through the water discharge hole 160. Thus, the drain hole 160 can prevent accumulation of muddy water or the like. However, the present invention does not limit the number, position and arrangement of the water discharge holes 160, and it can be adjusted according to the requirement.

Accordingly, compared to the prior art in which the cylindrical portion and the weight portion are vulcanized and molded together through the rubber elastic body, the dynamic damper 100 of the present embodiment has the cylindrical portion 110 and the weight portion 120 separately manufactured, and the springs 132 are used as the connection portion 130 instead of the rubber elastic body, so that the desired frequency can be obtained by adjusting the parameters, the number, and the positions of the springs 132 (in the present embodiment, the five springs 132 are arranged at equal intervals in the circumferential direction in a distributed manner), and the rubber elastic body can be manufactured without using a specific mold, so that the versatility is high, and the frequency characteristics of the springs 132 are changed less due to aging and deterioration in durability than those of the rubber elastic body, so that the frequency characteristics are stable. Accordingly, the dynamic damper 100 of the present embodiment can obtain stable frequency characteristics through the setting of the spring 132, thereby improving space efficiency.

Fig. 4 is a schematic side view of a dynamic damper 100A according to a second embodiment of the present invention mounted on a rotary shaft 50, fig. 5 is a schematic side view of the dynamic damper 100A of the second embodiment shown in fig. 4, and fig. 6 is a schematic front view of the dynamic damper 100A of the second embodiment shown in fig. 4. In the present embodiment, the dynamic damper 100A has a similar structure to the aforementioned dynamic damper 100, and the overall configuration of the dynamic damper 100A of the present embodiment will be described below with reference to fig. 4 to 6, but descriptions of parts similar to the aforementioned dynamic damper 100 will be omitted.

Referring to fig. 4 to 6, in the present embodiment, the dynamic damper 100A includes a cylindrical portion 110, a weight portion 120, and connecting portions 130 and 130A. That is, the structure of the cylindrical portion 110, the weight portion 120, and the coupling portion 130 is similar to that of the first embodiment, and the main difference is that the dynamic damper 100A is further provided with the coupling portion 130A.

As described above, in the dynamic damper 100, the coupling portion 130 includes the plurality of springs 132 each extending in the radial direction R, and is disposed in the recess 122 of the weight portion 120 in a dispersed manner at equal intervals in the circumferential direction, thereby coupling the cylindrical portion 110 and the weight portion 120. Moreover, by the arrangement of the groove 124, the connecting portion can be disposed in the groove 124 according to the requirement. Therefore, in the dynamic damper 100A of the present embodiment, the coupling portion 130A is further disposed in the recess 124 in addition to the structure of the dynamic damper 100 described above.

Specifically, in the present embodiment, the coupling portion 130A includes a cover (cap)134 and a retainer ring (circlip)136 provided in the groove 124, in addition to the plurality of springs 132 each extending in the radial direction R. The retainer ring 136 is disposed in the corresponding groove 124, the cover 134 is disposed radially R inside the retainer ring 136, and the spring 132 is disposed between the cover 134 and a sleeve 140 provided on the outer periphery of the cylindrical portion 110. In this way, the coupling portions 130 and the coupling portions 130A are arranged alternately at equal intervals in the circumferential direction. However, the present invention does not limit the parameters (such as size), number, position and arrangement of the spring 132, the cover 134 and the retainer ring 136, i.e., the present invention does not limit the composition of the connection portion 130A, which can be adjusted according to the requirement.

Accordingly, compared to the prior art in which the cylindrical portion and the weight portion are vulcanized and molded together through the rubber elastic body, the dynamic damper 100A of the present embodiment separately manufactures the cylindrical portion 110 and the weight portion 120, and uses the springs 132 as the connecting portions 130 and 130A instead of the rubber elastic body, so that the desired frequency can be obtained by adjusting the parameters, the number and the positions of the springs 132 (in the present embodiment, ten springs 132 are distributed at equal intervals in the circumferential direction, and the connecting portions 130 and 130A at different positions have different compositions), and the rubber elastic body is manufactured without using a specific mold, so that the versatility is high, and the frequency characteristics of the springs 132 are changed less due to aging and reduced durability than those of the rubber elastic body, so that the frequency characteristics are stable. Accordingly, the dynamic damper 100A of the present embodiment can obtain stable frequency characteristics through the setting of the spring 132, thereby improving space efficiency.

Fig. 7 is a schematic side view of a dynamic damper 100B according to a third embodiment of the present invention mounted on a rotary shaft 50, fig. 8 is a schematic side view of the dynamic damper 100B of the third embodiment shown in fig. 7, and fig. 9 is a schematic front view of the dynamic damper 100B of the third embodiment shown in fig. 7. In the present embodiment, the dynamic damper 100B has a similar structure to the dynamic dampers 100 and 100A described above, and the overall structure of the dynamic damper 100B of the present embodiment will be described below with reference to fig. 7 to 9, but descriptions of the parts similar to the dynamic dampers 100 and 100A described above will be omitted.

Referring to fig. 7 to 9, in the present embodiment, the dynamic damper 100B includes a cylindrical portion 110, a weight portion 120B and a connecting portion 130B. That is, the structure of the cylindrical portion 110 is similar to that of the first and second embodiments, and the main difference is the weight portion 120B and the connecting portion 130B.

As described above, in the dynamic dampers 100 and 100A, the weight 120 is provided with the grooves 122 and 124, and the coupling portion 130 is provided or further includes the coupling portion 130A. However, in the dynamic damper 100B of the present embodiment, the disposition of the recess 122 is omitted from the weight 120B, only five recesses 124 penetrating the weight 120B are disposed in a dispersed manner at equal intervals in the circumferential direction, the disposition of the coupling portions 130 and 130A is omitted from the dynamic damper 100B, and the coupling portion 130B is disposed only in the recess 124.

Specifically, the coupling portion 130B includes a plurality of springs 132 extending in the radial direction R, a cover 134 and a retainer 136 provided in the groove 124, and a spring 138 is provided between the cover 134 and the retainer 136, and the coupling portion 130B has a double-layer spring structure. In other words, the coupling portions 130 and 130A are provided so that the plurality of springs 132 are arranged in parallel, but in the present embodiment, the coupling portion 130B is provided so that the plurality of springs 132 are arranged in parallel, and further, the springs 132 and the springs 138 are arranged in series in the radial direction R. However, the present invention does not limit the parameters (such as size), number, position and arrangement of the spring 132, the cover 134, the retainer ring 136 and the spring 138, i.e., the present invention does not limit the composition of the connection portion 130B, which can be adjusted according to the requirement.

Accordingly, compared to the prior art in which the cylindrical portion and the weight portion are vulcanized and molded together through the rubber elastic body, the dynamic damper 100B of the present embodiment separately manufactures the cylindrical portion 110 and the weight portion 120B, and uses the springs 132 and 138 instead of the rubber elastic body as the connection portion 130B, so that the required frequency can be obtained by adjusting the parameters, the number and the positions of the springs 132 and 138 (in the present embodiment, five springs 132 and five springs 138 are disposed at equal intervals in the circumferential direction, and the springs 132 and the springs 138 are connected in the radial direction R one-to-one), the rubber elastic body is manufactured without using a specific mold, and the versatility is high, and the frequency characteristics of the springs 132 and 138 are changed less due to aging and reduced durability than the rubber elastic body, so that the frequency characteristics are stable. Accordingly, the dynamic damper 100B of the present embodiment can obtain stable frequency characteristics through the setting of the springs 132 and 138, thereby improving space efficiency.

More specifically, when the dynamic damper 100B is provided with two or more layers of springs (e.g., the springs 132 and 138 of the present embodiment) as the connection portion in the radial direction R, the two or more layers of springs 132 and 138 may have different elastic coefficients to obtain a desired frequency. In the case of multiple frequencies according to the rotation number, it is not necessary to provide multiple dynamic dampers for each frequency, but only a single dynamic damper 100B is used and the required springs 132 and 138 are selected according to the requirement. In other words, by arranging a plurality of springs (e.g., the springs 132 and 138) in series, the elastic coefficients of the springs 132 and 138 are changed according to the number of rotations, so that two or more frequencies can be accommodated, and space efficiency can be improved.

Fig. 10 is a schematic side view of a dynamic damper 100C according to a fourth embodiment of the present invention mounted on a rotary shaft 50, fig. 11 is a schematic side view of a dynamic damper 100D according to a fifth embodiment of the present invention mounted on the rotary shaft 50, and fig. 12 is a schematic side view of a dynamic damper 100E according to a sixth embodiment of the present invention mounted on the rotary shaft 50. In the fourth to sixth embodiments, the dynamic dampers 110C, 100D, 100E have similar structures to the aforementioned dynamic dampers 100, 100A, 110B, respectively, and the overall configurations of the dynamic dampers 110C, 100D, 100E of the fourth to sixth embodiments will be described below with reference to fig. 10 to 12, but descriptions of parts similar to the aforementioned dynamic dampers 100, 100A, 110B will be omitted.

Referring to fig. 10 to 12, in the fourth to sixth embodiments, the dynamic dampers 110C, 100D, 100E include a cylindrical portion 110, weight portions 120, 120B, and coupling portions 130, 130A, 130B. That is, the structures of the cylindrical portion 110, the weight portions 120, 120B, and the coupling portions 130, 130A, 130B are similar to those of the first to third embodiments, and the main difference is the sleeve 140A.

As described above, in the dynamic dampers 100, 100A, and 110B, the weight portions 120 and 120B are provided with the grooves 122 and 124, and the coupling portion 130 is provided, or the coupling portion 130A is further provided, or the coupling portion 130B is further included. However, in the dynamic dampers 110C, 100D, 100E of the fourth to sixth embodiments, the spring bearing seat 150 having a curved surface is provided on the outer periphery of the sleeve 140A provided on the outer periphery of the cylindrical portion 110.

Specifically, the sleeve 140A provided on the outer periphery of the cylindrical portion 110 is provided with a spring receiving seat 150 having a curved surface on the outer periphery, and the spring receiving seat 150 is configured to be rotatable around the center of the dynamic damper.

Accordingly, compared to the prior art in which the cylindrical portion and the weight portion are vulcanized and molded together through the rubber elastic body, the dynamic dampers 110C, 100D, and 100E of the fourth to sixth embodiments separately manufacture the cylindrical portion 110 and the weight portions 120 and 120B, and use the springs 132 and 138 instead of the rubber elastic body as the connection portions 130, 130A, and 130B, so that it is possible to obtain a desired frequency by adjusting the parameters, the number, and the positions of the springs 132 and 138, and it is not necessary to use a specific mold to manufacture the rubber elastic body, which is high in versatility, and the frequency characteristics of the springs 132 and 138 are less changed due to aging and deterioration in durability than the rubber elastic body, which is stable in frequency characteristics. Accordingly, the dynamic dampers 110C, 100D, 100E of the fourth to sixth embodiments can obtain stable frequency characteristics through the setting of the springs 132, 138, thereby improving space efficiency.

Further, when the dynamic dampers 110C, 100D, and 100E are further provided with the spring bearing seat 150 having a curved surface on the outer periphery of the sleeve 140A provided on the outer periphery of the cylindrical portion 110, the dynamic dampers 110C, 100D, and 100E can rotate about the dynamic damper center, and the spring stroke direction (spring stroke direction) can be aligned in the vibration direction. This can improve the effect of reducing vibration.

In summary, in the dynamic damper of the present invention, the weight portion is disposed apart from the radial outside of the cylindrical portion, and the coupling portion couples the cylindrical portion and the weight portion in the radial direction, wherein the coupling portion includes a plurality of springs extending in the radial direction, respectively, and the springs are disposed between the outer peripheries of the weight portion and the cylindrical portion, respectively. Furthermore, the dynamic damper of the utility model can be set into a double-layer spring structure. Thus, compared with the prior art that the cylindrical part and the counterweight part are vulcanized and molded together through the rubber elastic body, the dynamic damper of the utility model separately manufactures the cylindrical part and the counterweight part and uses the spring to replace the rubber elastic body as the connecting part, thereby obtaining the required frequency through adjusting the parameters, the quantity and the position of the spring, having higher universality without using a special die to manufacture the rubber elastic body, and the frequency characteristic of the spring caused by aging and durability reduction is less than that of the rubber elastic body, therefore, the frequency characteristic is more stable. Accordingly, the dynamic damper of the present invention can obtain stable frequency characteristics by setting the spring, thereby improving space efficiency.

Finally, it should be noted that: the above embodiments are only used to illustrate the technical solution of the present invention, and not to limit it; although the present invention has been described in detail with reference to the foregoing embodiments, it should be understood by those skilled in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some or all of the technical features may be equivalently replaced; such modifications or substitutions do not depart from the scope of the embodiments of the present invention, and the essence of the corresponding technical solutions is not disclosed.

Claims (7)

1. A dynamic damper, comprising:

a cylindrical portion for mounting on an outer periphery of the rotating shaft;

a weight portion disposed coaxially with the cylindrical portion and spaced apart from a radially outer side of the cylindrical portion; and

a coupling portion that couples the cylindrical portion and the weight portion in a radial direction, wherein

The coupling portion includes a plurality of springs respectively extending in the radial direction, and

the springs are respectively provided between the weight portions and the outer periphery of the cylindrical portion.

2. The dynamic damper according to claim 1, wherein an inner face of the weight portion is provided with a plurality of grooves recessed in the radial direction, and the springs are respectively provided in the corresponding grooves and bear against an outer periphery of the cylindrical portion.

3. The dynamic damper according to claim 2, wherein the coupling portion further includes a cap and a retainer ring provided in the groove, the retainer ring being provided in the corresponding groove, the cap being provided radially inward of the retainer ring, and the spring being provided between the cap and an outer periphery of the cylindrical portion.

4. The dynamic damper of claim 3, wherein a spring is further provided between the cover and the retainer ring, and the coupling portion constitutes a double-layer spring structure.

5. The dynamic damper according to claim 1, wherein an outer periphery of the cylindrical portion is provided with a sleeve, and the spring is provided radially outside the sleeve.

6. The dynamic damper according to claim 1, wherein the weight portion is formed with a water discharge hole penetrating in a radial direction.

7. The dynamic damper as claimed in claim 1, wherein the cylindrical portion is provided at an outer periphery thereof with a spring bearing seat having a curved surface, the spring bearing seat constituting a structure rotatable at a center of the dynamic damper.

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