JP2008240884A - Vibration control supporting member and automobile component unit supporting device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a vibration control supporting member capable of obtaining improved vibration controlling performance without increasing the size of the member, and an automobile component unit supporting device provided with the vibration control supporting part. <P>SOLUTION: The vibration control supporting member 100 is interposed between a supporting body and a supported body, and suppresses transmission of vibration from the supporting body to the supported body, or from the supported body to the supporting body. The vibration control supporting member 100 is equipped with a cylinder part 101 having an insertion hole 104 in which a bolt 5 for connecting the supporting body to the supported body is inserted, and annular projection parts 102, 103 extendingly formed in an annular shape on an outer peripheral face in the radial direction of the cylinder part 101. Portions of the cylinder part 101 between the annular projection parts 102, 103 are alternately disposed as an outer curved part 101a curved to the outside in the radial direction, and an inner curved part 101b curved toward the inside in the radial direction, connected to each other. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to an anti-vibration support member that is interposed between a support and a supported body and suppresses vibration transmission from the support to the supported body or from the supported body to the support, and the anti-vibration support member It is related with the components unit support apparatus for motor vehicles provided with.

  As such an anti-vibration support member, for example, there is a member that supports an automotive component unit (hereinafter referred to as a component unit) such as a motor of various drive units such as a wiper unit, an air cleaner, a water pump, and a compressor. The component unit is supported by the vehicle body via an anti-vibration support member.

  The purpose of using the anti-vibration support member is to prevent the vibration generated from the component unit from being transmitted to the vehicle body side and to generate noise, and the vibration from the vehicle body side is transmitted to the component unit, causing problems in the operation of the component unit. It is to prevent it from occurring.

  FIG. 10 shows a support structure of an automotive component unit support device 9 provided with a conventional vibration-proof support member. As shown in FIG. 10, the automotive component unit support device 9 includes a vibration isolation support member 900. The anti-vibration support member 900 includes a cylindrical portion 901 having an insertion hole 904 through which the spacer 4 is inserted at the center thereof, and two annular convex portions 902 that are annularly formed on the outer peripheral surface in the radial direction of the cylindrical portion 901. 903. The annular convex portions 902 and 903 are provided apart from each other in the axial direction of the cylindrical portion 901, and a receiving concave portion 905 is formed between the annular convex portions 902 and 903.

  The anti-vibration support member 900 is fitted into a through hole formed in the component unit mounting portion 21. The peripheral edge portion of the through hole of the component unit mounting portion 21 is fitted into the receiving recess 905, the peripheral surface of the through hole is in contact with the outer peripheral surface of the cylindrical portion 901, and the component unit mounting portion 21 is sandwiched between the annular convex portions 902 and 903. In this state, the component unit 2 is mounted. The component unit 2 is supported by the vehicle body 3 via the anti-vibration support member 900 by inserting the bolt 5 into the insertion hole 904 of the anti-vibration support member 900.

  The anti-vibration support member 900 is used to obtain sufficient anti-vibration performance against vibration in the axial direction (vertical direction in FIG. 10) and horizontal direction (direction perpendicular to the axial direction) of the anti-vibration support member 900. A design that reduces the spring constant with respect to vibration from the direction as much as possible is required.

  Of these, vibrations in the axial direction are mainly subjected to vibration isolation by the annular convex portions 902 and 903. In order to reduce the spring constant for vibrations from the axial direction, for example, the cross section is substantially omitted. A floating support member having an arch-shaped flange has been proposed (see, for example, Patent Document 1).

On the other hand, for vibration in the horizontal direction, vibration is mainly prevented by the cylindrical portion 901 between the annular convex portions 902 and 903. In order to reduce the horizontal spring constant, for example, a component is used. There has been proposed a configuration in which an annular protrusion is provided on the outer peripheral surface of the cylindrical portion with which the unit mounting portion abuts, and a circumferential groove is provided on the inner peripheral surface (see, for example, Patent Document 2).
JP 2001-90779 A Japanese Utility Model Publication No. 6-60765

  In the conventional example, with respect to the vibration in the axial direction, there is a certain amount of space in the horizontal direction in the region A where the annular protrusions 902 and 903 extend as shown in FIG. Therefore, the degree of freedom of design is relatively high, and various shapes that reduce the spring constant with respect to vibration from the axial direction can be employed for the annular protrusions 902 and 903. As a result, relatively sufficient vibration isolation performance can be obtained.

  However, with respect to the vibration in the horizontal direction, since the region B between the spacer 4 and the peripheral surface of the through hole is narrow, in this slight space, the cylindrical portion 901 between the annular protrusions 902 and 903 has a horizontal direction. It is difficult to provide a structure that sufficiently reduces the spring constant against vibration from Therefore, there has been a problem that sufficient vibration-proof performance cannot be obtained. Further, when the area B is increased, there is a problem that the vibration-proof support member 900 and the component unit mounting portion 21 are increased accordingly.

  The present invention has been made under such circumstances, and an anti-vibration support member capable of obtaining higher anti-vibration performance without increasing the size of the member itself, and an automotive part provided with the anti-vibration support member It is an object to provide a unit support device.

  The present invention has been made to solve the above-described problems, and includes the following configuration.

  (1) An anti-vibration support member that is interposed between the support and the support and suppresses vibration transmission from the support to the support or from the support to the support, A cylindrical portion having an insertion hole through which a connecting member for connecting to a supported body is inserted, and at least two annular protrusions formed annularly on the radially outer peripheral surface of the cylindrical portion; The at least two portions between the two annular convex portions are alternately arranged with a plurality of outward curved portions that are curved radially outward and a plurality of inwardly curved portions that are curved radially inward, and are connected to each other. An anti-vibration support member comprising:

  (2) In the anti-vibration support member according to (1), the cylindrical portion includes four each of the outer curved portion and the inner curved portion that are alternately arranged and connected to each other. The anti-vibration support member according to claim 1, wherein each of the radial cross sections has a deformed quadrangular shape with curved sides.

  (3) An automotive component unit support device for supporting an automotive component unit on a vehicle body, wherein the vibration isolating support member according to (1) or (2) and the automotive component unit are coupled to the vehicle body. The anti-vibration support member, wherein the outer curved portion of the cylindrical portion abuts on a peripheral surface of a through hole formed in the attachment portion of the automotive component unit, and the attachment portion is the anti-vibration member. The vibration support member is mounted on the automobile component unit in a state of being sandwiched by two annular convex portions, and the connecting member is inserted into the insertion hole of the vibration isolation support member, and the peripheral surface thereof is the vibration isolation member. An automotive component, wherein the automotive component unit is in contact with an inwardly curved portion of a cylindrical portion of a support member, a tip end thereof engages with the vehicle body, and the automotive component unit is supported by the vehicle body via the vibration-proof support member. Unit support device.

  According to the present invention, it is possible to provide an anti-vibration support member that can obtain higher anti-vibration performance without increasing the size of the member itself, and an automotive component unit support device provided with the anti-vibration support member. it can.

  The best mode for carrying out the present invention will be described based on the following examples.

  However, the dimensions, materials, shapes, relative arrangements, and the like of the components described in this embodiment are not intended to limit the scope of the present invention only to those unless otherwise specified. .

  Hereinafter, the anti-vibration support member according to the present embodiment will be described with reference to the drawings. In the present embodiment, an automotive component unit support apparatus including the vibration isolating support apparatus according to the present embodiment will be described as an example.

  1A and 1B are diagrams showing a vibration isolating support member according to the present embodiment, in which FIG. 1A is a plan view of the vibration isolating support member, and FIG. 1B is a cross-sectional view taken along line BB in FIG. An end view, FIG.1 (c) is the sectional view on the AA line in FIG.1 (b). FIG. 2 is a schematic cross-sectional view of the automotive component unit support device provided with the vibration isolating support member according to this embodiment, and FIG. 3 is an exploded view illustrating the automotive component unit support device. Note that the cross-sectional view shown in FIG. 1B is used for the anti-vibration support member shown in FIGS. 2 and 3 in order to facilitate understanding of the present invention.

  As shown in the figure, the automotive component unit support device 1 includes an anti-vibration support member 100, a spacer 4 (connection member) inserted through the anti-vibration support member 100, and a bolt 5 (connection member) inserted through the spacer 4. A washer 6 interposed between the spacer 4 and the bolt 5 is provided, and the component unit 2 is supported on the vehicle body 3 by the automotive component unit support device 1. In addition, the automotive component unit support device 1 may not include the spacer 4 and the washer 6.

  Specifically, the vibration-proof support member 100 is made of, for example, butyl rubber such as NR (natural rubber), IIR (isobutylene-isoprene rubber), SBR (styrene butadiene rubber), NBR (acrylonitrile-butadiene rubber), EPDM (ethylene propylene diene). A cylindrical portion 101 having an insertion hole 104 through which the spacer 4 is inserted at the center, and an outer circumferential surface of the cylindrical portion 101 in the radial direction. And two annular convex portions 102 and 103 that are annularly formed. The annular convex portions 102 and 103 are provided apart from each other in the axial direction of the cylindrical portion 101, and a receiving concave portion 105 is formed between the annular convex portions 102 and 103.

  The anti-vibration support member 100 is fitted into a through hole 21 a formed in the component unit mounting portion 21 of the component unit 2. And the through-hole 21a peripheral part of the component unit attaching part 21 fits in the receiving recessed part 105, the peripheral surface of the through-hole 21a contact | abuts the outer peripheral surface of the cylindrical part 101, and the component unit attaching part 21 is the cyclic | annular convex parts 102 and 103. Is mounted on the component unit 2 in a state of being sandwiched between the two.

  Then, the spacer 4 is inserted into the insertion hole 104 of the anti-vibration support member 100, and the bolt 5 is further inserted, and the tip of the bolt 5 is screwed into the recess 31 provided with a thread groove on the peripheral surface provided on the vehicle body 3. . Thereby, the component unit 2 is supported by the vehicle body 3.

  Next, the configuration of the vibration isolating support member 100 will be described in detail.

  4A and 4B are diagrams for explaining a mounting state of the vibration isolating support member 100. FIG. 4A is a diagram illustrating an arrangement configuration of the vibration isolating support member 100 and the spacer 4, and FIG. It is a figure which shows the arrangement configuration of the member 100, the spacer 4, and the component unit attaching part 21. FIG.

  As shown in FIGS. 3 and 4, the cylindrical portion 101 includes a plurality of outward curved portions 101 a that are curved radially outward and a plurality of inward curved portions that are curved radially inward. Part 101b. And the outward bending part 101a and the inward bending part 101b are arrange | positioned alternately, and they are connected smoothly. In this embodiment, the cylindrical portion 101 is composed of four each of an outward bending portion 101a and an inward bending portion 101b, and the radial cross section of the cylindrical portion 101 has a deformed quadrangular shape with curved sides.

  In the outwardly curved portion 101a, the radially outer surface of the outwardly curved portion 101a contacts the peripheral surface of the through hole 21a of the component unit mounting portion 21, and a gap SPa is formed between the radially inner side surface and the spacer 4. Is done. On the other hand, in the inwardly curved portion 101b, a gap SPb is formed between the radially outer surface of the inwardly curved portion 101b and the peripheral surface of the through hole 21a of the component unit mounting portion 21. Abut. Therefore, the anti-vibration support member 100 is in contact with the component unit 2 at the four outward curved portions 101a and is in contact with the spacer 4 at the four inward curved portions 101b.

  As shown in FIGS. 1 and 2, the annular convex portion 102 has locking convex portions 102 c and 102 d that protrude in both the axial direction of the cylindrical portion 101, that is, the direction toward the component unit mounting portion 21 and the direction toward the washer 6, respectively. Is formed. Similarly, locking projections 103e and 103f projecting in the direction toward the component unit mounting portion 21 and in the direction toward the vehicle body 3, respectively, are formed on the annular projection 103.

  When the vibration isolating support member 100 is mounted on the component unit mounting portion 21, the locking projections 102 c and 103 e abut against the component unit mounting portion 21, and the component unit mounting portion 21 is sandwiched between the annular projections 102 and 103. Is done.

  Next, a description will be given of the vibration isolation effect of the vibration isolation support member 100 according to the present embodiment.

  The anti-vibration effect in the case of using such an anti-vibration support member that is an elastic body is generally represented by a transmissibility curve as shown in FIG. In the transmissibility curve, the frequency Fn of the peak portion of the resonance region having one or more vibration transmissibility having no vibration isolation effect is expressed by the following equation.

  As apparent from the above equation, the smaller the spring constant K and the greater the weight M of the component unit, the smaller the frequency Fn of the peak portion, that is, the resonance region moves to the lower frequency side. In addition, it is known that the vibration-proof region moves to the lower frequency side. Therefore, if the spring constant K of the vibration isolating support member is low, a vibration isolating effect can be obtained even for vibrations at lower frequencies, and a desired vibration isolating effect can be obtained even for lighter component units. It becomes like this.

  Therefore, predetermined vibration is applied to the vibration isolating support member 100 according to the present embodiment and the vibration isolating support member having another shape, and the displacement (mm) and reaction force (N) of each vibration isolating support member at that time are applied. ) And the spring constants of the anti-vibration support members were compared.

  FIG. 6 is a diagram for explaining a comparison of spring constants between the anti-vibration support member 100 according to this embodiment and the conventional anti-vibration support member, and FIG. 7 is a displacement when vibration is applied to each anti-vibration support member shown in FIG. It is a graph which shows the relationship between (mm) and reaction force (N). Of the cross-section of the anti-vibration support member illustrated in FIG. 6, the anti-vibration support member 100 according to the present embodiment is illustrated in FIG. 1B in order to facilitate understanding of the present invention. A cross section was used.

  As shown in FIG. 6A, the conventional example A is provided with an annular protrusion having a substantially trapezoidal cross section on the outer peripheral surface of the cylindrical portion. The peripheral surface of the through hole 21 a of the portion 21 and the spacer 4 are in surface contact. In the conventional example B, an annular protrusion having a substantially trapezoidal cross section is provided on the outer peripheral surface of the cylindrical portion, and a circumferential groove is provided on the inner peripheral surface. The outer peripheral surface of the cylindrical portion faces the peripheral surface of the through hole 21a. The inner circumferential surface of the cylindrical portion is separated from the spacer 4 in the circumferential groove portion. In the conventional example C, two annular protrusions are provided on the outer peripheral surface of the cylindrical portion so as to be separated from each other in the axial direction. The outer peripheral surface of the cylindrical portion is in line contact with the peripheral surface of the through hole 21a, and the inner peripheral surface of the cylindrical portion is a spacer. 4 is in surface contact.

  When applying vibration to each anti-vibration support member, vibration was applied to the anti-vibration support member 100 according to this example from directions indicated by arrows 1 and 2 in FIG. As for the conventional examples A to C, there is no difference regardless of which direction the vibration is applied in the structure, so the vibration is determined from only one direction.

  The result is shown in FIG. As is clear from FIG. 7, it can be seen that the anti-vibration support member 100 according to the present example has a lower reaction force than the conventional examples A to C, that is, has a lower spring constant. Therefore, compared with the conventional example, a more excellent anti-vibration effect can be obtained against horizontal vibration.

  Subsequently, regarding the vibration-proof support member 100 according to the present embodiment, the modified example of the vibration-proof support member according to the present embodiment, and the change when a predetermined vibration is applied to the vibration-proof support member of the conventional example, the computer Analysis by simulation was performed.

  FIG. 8 is a diagram showing a state of deformation of each anti-vibration support member due to vibration, and FIG. 9 is a graph showing displacement (mm) and reaction force (N) when vibration is applied to each anti-vibration support member shown in FIG. It is a graph which shows a relationship.

  As shown in FIG. 8, Conventional Example D has six protrusions provided at equal intervals on the outer peripheral surface of the cylindrical portion. In the modified example of the anti-vibration support member according to this embodiment, the cylindrical portion is composed of six outward curved portions and inward curved portions, and the radial cross section of the cylindrical portion has a deformed hexagonal shape with curved sides. It is. The direction in which the vibration is applied is indicated by an arrow in the figure, but the vibration isolating support member 100 and the modification according to the present embodiment are applied with vibrations from directions different from those of the patterns 1 and 2. Regarding Conventional Example D, there is almost no difference even if vibration is applied from either direction of pattern 1 or pattern 2, so that only pattern 1 is used.

  The result is shown in FIG. As is clear from FIG. 9, it can be seen that the anti-vibration support member 100 and the modification according to the present embodiment have a lower reaction force than the conventional example D, that is, have a lower spring constant.

  In comparison with the above-described conventional example, it was shown that the vibration isolating support member 100 according to this example has a lower spring constant. Also, in the analysis by the computer simulation described above, it has been shown that the vibration-proof support member 100 according to the present embodiment and its modification have a lower spring constant. This is because the vibration isolation support member is smoothly deformed by the gap SPa formed between the vibration isolation support member and the spacer 4 and the gap SPb formed between the vibration isolation support member and the peripheral surface of the through hole 21a. Further, it is considered that the spacer 4 can move smoothly along the peripheral surface of the vibration-proof support member because the peripheral surface of the cylindrical portion has a smooth curved shape. Therefore, compared with the conventional example, a more excellent anti-vibration effect can be obtained against horizontal vibration.

  Further, when comparing the vibration isolating support member 100 according to the present example and the modification, it can be seen that the vibration isolating support member 100 according to the present example has a lower spring constant. This is because there is almost no anisotropy when the cylindrical portion is composed of four outward curved portions and four inwardly curved portions, compared to the case where the cylindrical portion is composed of a larger number of outward curved portions and inward curved portions, This is probably because the spacer can be effectively slid along the peripheral surface of the cylindrical portion. Also, in the case of a deformed triangular shape comprising three each of the outward bending portion and the inward bending portion, the balance between the outward bending portion and the inward bending portion is poor and a force is applied to the outward bending portion. The reaction force may be increased. Therefore, a deformed square shape is more preferable.

  In the present embodiment, the vibration-proof support member is applied to the automobile component unit support device, but is not particularly limited to this, and may be a vehicle other than an automobile, and further, for example, a refrigerator compressor, a CD driver, etc. The present invention can be applied to a device that needs to suppress the vibration of the body or the support from being transmitted to the other.

(A), (b), (a) is a figure which shows the vibration isolating support member which concerns on Example 1. FIG. Schematic cross-sectional view of automotive component unit support device Exploded view for explaining an automotive component unit support device (A), (b) is a figure explaining the mounting state of an anti-vibration support member Diagram showing transmission curve (A), (b) is a figure explaining the spring constant comparison of the vibration proof support member of a present Example, and the conventional vibration proof support member. A graph showing the relationship between displacement and reaction force when vibration is applied to an anti-vibration support member The figure which shows the mode of deformation of the vibration-proof support member A graph showing the relationship between displacement and reaction force when vibration is applied to an anti-vibration support member The figure which shows the support structure of the conventional automotive component unit support apparatus

Explanation of symbols

SPa, SPb Gap 1 Automotive component unit support device 2 Component unit 3 Car body 4 Spacer (corresponding to connecting member)
5 bolts (corresponding to connecting members)
21 Component unit mounting portion 21a Through hole 100 Anti-vibration support member 101 Cylindrical portion 101a Outer bending portion 101b Inner bending portion 102, 103 Annular convex portion 104 Insertion hole

Claims (3)

An anti-vibration support member that is interposed between the support and the supported body and suppresses vibration transmission from the support to the supported body or from the supported body to the support,
A cylindrical portion having an insertion hole through which a connecting member for connecting the support and the supported body is inserted;
And at least two annular projections formed annularly on the radially outer peripheral surface of the cylindrical portion,
In the cylindrical portion, at least a portion between the two annular convex portions is alternately arranged with a plurality of outward curved portions that are curved radially outward and a plurality of inwardly curved portions that are curved radially inward. An anti-vibration support member characterized by being connected. The vibration-proof support member according to claim 1,
The cylindrical portion is formed by alternately arranging four each of the outward bending portion and the inward bending portion and connecting them, and the radial cross section of the cylindrical portion has a deformed quadrangular shape with curved sides. An anti-vibration support member. An automotive component unit support device for supporting an automotive component unit on a vehicle body,
An anti-vibration support member according to claim 1 or 2,
A connecting member for connecting the automobile part unit to the vehicle body,
The vibration isolating support member has an outer curved portion of the cylindrical portion that abuts on a peripheral surface of a through hole formed in the attachment portion of the automotive component unit, and the attachment portion has two annular protrusions of the vibration isolation support member. In a state of being sandwiched by the parts, it is mounted on the automobile component unit,
The connecting member is inserted into the insertion hole of the vibration isolating support member, a peripheral surface thereof abuts on an inwardly curved portion of the cylindrical portion of the vibration isolating support member, a tip end thereof engages with the vehicle body, and the automobile An automotive component unit support device, wherein a vehicle component unit is supported by a vehicle body via the vibration-proof support member.

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