JP2016080166A - Long member for high damping assembly frame, and high damping assembly frame - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a long member for high damping frame assembly having a high vibration-proof effect.SOLUTION: A long member 100 for high damping frame assembly includes a long frame body 10 including one or plural open holes 12 extending in a longitudinal direction, and a vibration-proof member 20 inserted into at least one open hole 12 of the open holes 12. The vibration-proof member 20 has a rod-like mass member 21, and a buffer material 22 inserted between the mass member 22 and the inner wall of the open hole 12 and supporting the mass member 21. It is preferable that a plurality of buffer materials 22 is provided for intermittently supporting a plurality of places in the longitudinal direction of the mas member 21.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a long member for a high-damping assembly frame provided with a vibration damping function on a long member constituting a support column or a cross beam of an assembly-type frame that supports a precision device or the like, and a high height assembled using the long member. The present invention relates to a damping assembly frame.

Conventionally, a so-called aluminum frame made of an extruded product of aluminum is widely used for components of precision devices, pedestals, frames and the like because it is lightweight and has high rigidity.
However, the aluminum frame generally has low vibration damping performance, and there are problems of waiting time until the vibration generated from inside and outside the apparatus is sufficiently converged, and adverse effects on the apparatus accuracy due to vibration.

  Therefore, the present inventors pay attention to a through hole penetrating in the longitudinal direction of such an aluminum frame, and insert a member for suppressing vibration of the aluminum frame into the through hole to obtain the vibration damping effect of the assembly type frame. Come up with the idea.

On the other hand, as a member for inserting into a through hole of a structure having a through hole such as an aluminum frame and suppressing vibration of the structure, for example, in Patent Document 1, foamed rubber, clay, sand, etc. And granular materials such as beads are described.
Patent Document 2 describes a foam made of a rubber system, a thermoplastic resin system, or a thermosetting resin system.

JP-A-8-4364 JP-A-9-189340

However, the present inventors described the above-mentioned Patent Document 1 or 2 by devising the configuration of the damping member as a result of repeating earnest research on the damping member inserted into the through hole of the aluminum frame. It was found that the aluminum frame can be damped more effectively than the vibration damping member.
The present invention has been made on the basis of such examination results, and uses a long member for assembling a high-damping assembly frame having a sufficient damping effect to be used for a frame of a precision device, and the long member. An object is to provide a high damping assembly frame.

  The invention made in order to solve the above-described problems includes an elongated frame body having one or more through holes extending in the longitudinal direction, and a vibration damping member inserted into at least one of the through holes. The damping member includes a rod-shaped mass member, and a long member for a high-damping assembly frame that is inserted between the mass member and an inner wall of the through hole and supports the mass member. It is.

  In this way, the damping member is configured by the rod-shaped mass member and the cushioning material that is inserted between the mass member and the inner wall of the through hole and supports the mass member. The vibration of the frame main body can be damped more effectively compared to the case in which the holes are filled with granular materials or the case in which only the foam material is filled as in Patent Document 2.

It is preferable that a plurality of the buffer materials are provided so as to intermittently support a plurality of locations in the longitudinal direction of the mass member.
As described above, by providing a plurality of buffer materials intermittently supporting the rod-shaped mass member, an extremely large vibration damping effect can be obtained as compared with the case where the entire mass member is wrapped with one buffer material.

The one or more through holes have at least one eccentric through hole provided at a position eccentric from a central axis of the frame body, and the damping member is inserted into the eccentric through hole. preferable. By doing so, the vibration of the frame body can be attenuated more effectively.
Here, the “center axis” refers to an imaginary straight line that passes through the center of gravity in a cross section (or end face) perpendicular to the longitudinal direction of the frame body and extends in the longitudinal direction of the frame body.

  It is preferable that the frame main body includes a plurality of eccentric through holes having different distances from the central axis, and the damping member is inserted into the eccentric through hole farthest from the central axis. By doing so, the vibration of the frame body can be attenuated more effectively.

  It is preferable that the eccentric through hole includes at least one pair of eccentric through holes symmetrical with respect to the central axis, and the vibration damping member is inserted into both of the pair of eccentric through holes. By doing so, the vibration of the frame body can be attenuated more effectively.

  It is preferable that a natural frequency related to at least one vibration mode among vibration modes in which the frame body is deformed is 1000 Hz or less. When the natural frequency related to all vibration modes among the vibration modes accompanied by deformation of the frame main body exceeds 1000 Hz, there is a possibility that a substantial effect by inserting the damping member into the frame main body may not be obtained.

  The present invention includes a high attenuation assembly frame using the long member for a high attenuation assembly frame described above.

  As described above, according to the long member for frame assembly of the present invention, it is possible to obtain a vibration damping effect sufficient to be used for a frame of a precision device.

It is a perspective view of the elongate member for high attenuation | damping assembly frames which concerns on 1st Embodiment of this invention. It is a typical perspective view of the damping member used for the elongate member for a frame assembly of FIG. It is a fragmentary perspective view of the high attenuation | damping assembly frame which concerns on 1st Embodiment of this invention. It is a perspective view of the elongate member for high attenuation | damping assembly frames which concerns on 2nd Embodiment of this invention. It is (a) front view of the elongate member shown in FIG. 4, (b) It is a side view. It is a perspective view of the elongate member for high attenuation | damping assembly frames which concerns on 3rd Embodiment of this invention. It is a perspective view of the elongate member for high attenuation | damping assembly frames which concerns on 4th Embodiment of this invention. It is a perspective view of the elongate member for high attenuation | damping assembly frames which concerns on 5th Embodiment of this invention. It is the (a) front view and (b) side view which showed using the 3rd-5th embodiment typically the mode of the vibration test. It is the graph which showed the relationship between the natural frequency of only the frame main body in each Example of 3rd-5th Embodiment, and the damping ratio magnification of a long member.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings as appropriate. However, the present invention is not limited to the following embodiments.
(First embodiment)
FIG. 1 shows a long member (hereinafter also simply referred to as “long member”) 100 for a high attenuation assembly frame according to a first embodiment of the present invention. The long member 100 includes a frame main body 10 and a vibration damping member 20, and the vibration damping member 20 includes a mass member 21 and a buffer material 22 as illustrated in FIG. 2.

The frame body 10 is made of an aluminum alloy extruded material, and has a prismatic shape with a substantially square cross section. The frame body 10 includes a central through hole 11 located at the center of the cross section and corner through holes (eccentric through holes) 12 located at the four corners of the square of the cross section. The side surface 13 of the frame main body 10 is provided with a slit 14 having a substantially T-shaped cross section extending in the longitudinal direction at the center thereof.
As shown in FIG. 3, the long member 100 is assembled to the high attenuation assembly frame 1000 using the connecting bracket 3, the bolt 4, and the nut 5.

The damping member 20 is inserted into at least one through hole among the center through hole 11 and the four corner through holes 12 of the frame body 10. The mass member 21 of the damping member 20 is made of a rod or tube material, and the buffer material 22 is made of an elastic material such as a resin foam sheet or rubber, and is wound around the outer circumference of the mass member 21. The mass member 21 is interposed between the inner walls of the through holes 11 and 12 so as to be positioned substantially at the center of the cross section of the through hole 11. The buffer material 22 may be provided so as to cover the entire length of the mass member, may be provided so as to cover a part thereof, or a plurality of the buffer materials 22 may be provided intermittently in the longitudinal direction.
As the mass member 21, a metal such as iron or stainless steel is preferably used, and various kinds of resins, known materials such as composite materials can be used as appropriate, and the inside of the hollow cylindrical member is filled with a solid or liquid. Such members can also be used.

Next, examples according to the first embodiment will be described in detail. However, the present invention is not limited to the following examples.
Example 1
As the frame body 10, the aluminum frame made of A6063S shown in FIG. 1, 50 mm × 50 mm × 1500 mm, weight 4.3 kg is used, and the damping member 20 is a round member (SS400) of φ6 mm × 1500 mm as the mass member 21. Was used as the cushioning material 22 by cutting a sheet-like polyethylene foam material having a thickness of 3 mm provided with an adhesive layer on one side into a width of 15 mm and a length of 18 mm. The cushioning material 22 has the adhesive layer on the surface of the round steel that is the mass member 21, the length direction of the cushioning material 22 is set to the circumferential direction of the mass member 21, and the transverse width of the cushioning material 22 is set to the longitudinal direction of the mass member 21. Was attached to 5 places in total, ie, both ends of the mass member 21 and 3 intermediate portions at a pitch of 375.0 mm. The vibration damping member 20 thus formed was inserted into one of the corner through holes 12 of the frame body 10.

  After that, the long member 100 for testing is watered at two places of 340 mm from both ends so that the corner through hole 12 provided with the damping member is located on the upper side and the upper and lower side surfaces 13 are horizontal. Hanging down with thread, PCB PIEZOTRONICS INC. Company-made 3-axis accelerometer (model 356A17) was set at a pitch of 375 mm at a total of 5 locations on both ends in the longitudinal direction and 3 in the middle, with the impact hammer (model 086D20) at the center in the longitudinal direction. I beat it and shaken it. The natural frequency of the bending primary mode and the damping ratio are calculated from the data thus obtained with the accelerometer using an FFT analyzer (model OR35-4) manufactured by OROS, and the damping ratio comparison example 1 in each example is calculated. The magnification (hereinafter referred to as “attenuation ratio magnification”) with respect to the attenuation ratio (only the frame body) was obtained.

(Example 2 to Example 9)
Except for changing the pitch of the buffer material 22 as shown in Table 1, the natural frequency, damping ratio, and damping ratio magnification of the bending primary mode were obtained for Examples 2 to 9 in the same manner as in Example 1. .

(Example 10)
The test was conducted in the same manner as in Example 1 except that the damping member was configured by covering the entire length of the same round steel as in Example 1 with a single cushioning material made of the same cushioning material as in Example 1. The natural frequency, damping ratio, and damping ratio magnification of the primary mode were determined.

(Comparative Example 1)
Only the frame main body of Example 1 without using a damping member was tested in the same manner as in Example 1 to obtain the natural frequency and damping ratio of the bending first mode.

Table 1 shows the test results of Examples 1 to 10 and Comparative Example 1.

From the results shown in Table 1, it can be seen that the damping ratio and damping ratio magnification of the long member for the assembly frame are greatly improved when the damping member is provided than when the damping member is not provided. It was.
In addition, the damping ratio and the damping ratio magnification are greatly improved by winding a plurality of cushioning materials intermittently in the longitudinal direction of the mass member, rather than winding the cushioning material over the entire length of the mass member. I understood.

(Second Embodiment)
FIG. 4 shows a long member 200 for a high attenuation assembly frame according to the second embodiment of the present invention. The long member 200 includes a frame main body 210 and a vibration damping member 20, and the vibration damping member 20 includes a mass member 21 and a buffer material 22 as illustrated in FIG. 2.

  As shown in FIG. 5, the frame main body 210 has a long rectangular plate shape in which both end faces 214 in the longitudinal direction are flat rectangles, and penetrates in the longitudinal direction and is provided with six eccentricities provided at equal intervals in the width direction. The through hole 212 (212a, 212b, 212c, 212d, 212e, 212f) is provided. Each of the six through holes 212 is provided at a position eccentric from a central axis X extending in the longitudinal direction of the panel body 210 through the center of gravity O of the end surface 214. The outer two eccentric through holes 212a and 212f, the second eccentric through holes 212b and 212e from the outer side, and the innermost eccentric through holes 212c and 212d are provided symmetrically about the central axis X.

  In the second embodiment, the damping member 20 is provided so as to be inserted into any one of the eccentric through holes 212. The damping member 20 is preferably provided in the outermost eccentric through-hole 212a or 212f in the width direction of the frame body 210, and a pair of eccentric through-holes (for example, 212a and 212f axisymmetric about the central axis X). , 212b and 212e, and 212c and 212d).

  Next, an example according to the second embodiment will be described in detail. However, the present invention is not limited to the following examples.

(Example 11)
As the frame main body 210, six aluminum plates (A5052P) cut into a width of 410 mm, a length of 780 mm, and a thickness of 35 mm so that the dimensions shown in FIG. 5B are g = 60 and h = 58. A φ9 mm eccentric through hole 212 with a drill was used.
The damping member 20 is made of a round steel (SS400) of φ6 mm × 720 mm as the mass member 21 and made of a sheet-like soft CR (chloroprene rubber) having a thickness of 1 mm with an adhesive layer provided on one side as the buffer material 22. A sponge cut into a width of 15 mm and a length of 30 mm was used. The cushioning material 22 has the adhesive layer on the surface of the round steel that is the mass member 21, the length direction of the cushioning material 22 is the circumferential direction of the mass member 21, and the width direction of the cushioning material 22 is the longitudinal direction of the mass member 21 1 piece or more, and attached at a pitch of 141 mm to a total of 6 locations, both ends of the mass member 21 and 4 intermediate portions. The damping member 20 thus formed was inserted into the eccentric through hole 212c so as to be positioned at the center in the longitudinal direction of the eccentric through hole 212c.

  Thereafter, the long member 200 for testing is connected to a pair of φ9 mm through holes 210 a provided in positions where the dimensions in FIG. 5A are e = 30 mm, c = 171.6 mm, and d = 436.8. , So that the eccentric through-hole 212a is positioned above the central axis X and the both end faces 213 in the width direction are horizontal, and the PCB PIEZOTRONICS INC. A 3-axis accelerometer (model 356A03) manufactured by the company is set at 10 measurement points P1 to P10 where the dimensions in FIG. 5A are a = 20 mm and b = 185 mm, and in the vicinity of the measurement point P1 Was shaken with a PCB impact hammer 086C03. The natural frequency and damping ratio of the torsional primary mode are calculated from the data thus obtained with the accelerometer using an FFT analyzer (model OR35-4) manufactured by OROS, and Comparative Example 2 (only the frame main body 210). The attenuation ratio magnification with respect to the attenuation ratio was obtained.

(Example 12 to Example 13)
Except that one damping member 20 was inserted into the eccentric through hole indicated by ● in Table 2, the test was conducted in the same manner as in Example 11 to perform the natural frequency, damping ratio and damping ratio of the torsional primary mode. The magnification was determined.

(Example 14)
Except for inserting the two damping members 20 one by one into the two central eccentric through holes 212c and 212d that are symmetric about the central axis X, the test was conducted in the same manner as in Example 11 to perform the natural vibration of the torsional primary mode. The number, damping ratio and damping ratio magnification were determined.

(Example 15, Example 16)
Except that the two damping members 20 were inserted into the eccentric through holes indicated by ● in Table 2, the test was conducted in the same manner as in Example 14 to determine the natural frequency, damping ratio, and damping ratio magnification of the torsional primary mode. Asked.

(Comparative Example 2)
Except that the damping member 20 was omitted, a test was performed in the same manner as in Example 11 to obtain the natural frequency, damping ratio, and damping ratio magnification of the torsional primary mode.

Table 2 shows the test results of Examples 11 to 16 and Comparative Example 2.

From the results in Table 2, the damping ratio and the damping ratio magnification of the long member for the assembly frame are improved when the damping member is inserted into the through hole located away from the center in the width direction of the frame body. I understood.
It was also found that the damping ratio and the damping ratio magnification are improved by providing two damping members symmetrically with respect to the central axis X, rather than providing only one damping member at a position eccentric from the central axis X.

(Third embodiment)
FIG. 6 shows a long member 300 for a high attenuation assembly frame according to a third embodiment of the present invention. The long member 300 includes a frame main body 310 and a vibration damping member 20.

  The frame body 310 is made of an extruded material of aluminum alloy and has a prismatic shape with a substantially square cross section. The frame main body 310 includes a central through hole 311 located at the center of the cross section and four corner through holes (eccentric through holes) 312 located at the four corners of the square of the cross section. The side surface 313 of the frame main body 310 is provided with a slit 314 extending in the longitudinal direction at the center.

  As shown in FIG. 2, the damping member 20 includes a mass member 21 and a buffer material 22, and the mass member 21 is provided in the same length as the frame body 310, and the buffer material 22 is as shown in FIG. 2. A plurality of them are provided at equal intervals. The damping member 20 is inserted into one of the corner through holes 312.

Next, vibration tests performed using the examples according to the third embodiment and comparative examples will be described in detail.
(Example 17a)
In Example 17a, an aluminum frame (model AFS-4545L-8), 45 mm square × 2000 mm length, manufactured by Nichi Autotech Co., Ltd., was used as the frame body 310.
The damping member 20 is made of a round steel (SS400) of φ6 mm × 2000 mm as the mass member 21 and made of a sheet-like soft CR (chloroprene rubber) having a thickness of 3 mm with an adhesive layer provided on one side as the buffer material 22. A sponge cut into a width of 15 mm and a length of 24 mm was used. The cushioning material 22 has the adhesive layer on the surface of the round steel that is the mass member 21, the length direction of the cushioning material 22 is the circumferential direction of the mass member 21, and the width direction of the cushioning material 22 is the longitudinal direction of the mass member 21 1 round or more, so that both ends and the middle part were attached at equal intervals.

  Thereafter, the test elongate member 300 is placed at two locations where the dimensions shown in FIG. 9 are t = 0.22 × L (L is the length of the frame body 310) and u = 0.56L. Hang a water string and hang it horizontally, PCB PIEZOTRONICS INC. As shown in FIG. 9 (a), a 3-axis accelerometer made by the company (model 356A03) is set at five measurement points P11 to P15 arranged at equal intervals in the longitudinal direction, and the longitudinal center The vicinity (position 50 mm from the center in the longitudinal direction) was vibrated by hitting it with a PCB impact hammer 086C03. The attenuation ratio of the bending first mode is calculated from the data thus obtained with the accelerometer using an FFT analyzer (model OR35-4) manufactured by OROS, and the attenuation ratio relative to the attenuation ratio of Comparative Example 3 (frame body 310 only). The magnification was determined.

(Example 17b to Example 17h)
Except that the number of the buffer materials 22 is 4, 5, 6, 7, 9, 11, 17 in the order of Example 17b to Example 17h, the test is performed in the same manner as in Example 17a to determine the damping ratio. The attenuation ratio magnification with respect to the attenuation ratio of Comparative Example 3 (only the frame main body 310) was calculated.

(Example 19a to Example 19h)
In Examples 19a to 19h, tests were performed in the same manner as in Examples 17a to 17h, except that the lengths of the frame main body 310 and the mass member 20 were both 1000 mm. The attenuation ratio magnification with respect to the attenuation ratio of Example 5 (only the frame main body 310) was obtained.

(Example 20a to Example 20h)
In Example 20a to Example 20h, tests were performed in the same manner as in Example 17a to Example 17h, except that the lengths of the frame main body 310 and the mass member 20 were both 700 mm, and the attenuation ratio was calculated. The attenuation ratio magnification with respect to the attenuation ratio of Example 6 (only the frame main body 310) was obtained.

(Comparative Examples 3, 5, 6)
Except for omitting the damping member 20, tests were performed in the same manner as in Example 17a, Example 19a, and Example 20a to obtain the natural frequency and damping ratio.

(Fourth embodiment)
FIG. 7 shows a long member 400 for a high attenuation assembly frame according to a fourth embodiment of the present invention. The long member 400 includes a frame body 410 and the vibration damping member 20.

  The frame main body 410 is made of an extruded material of an aluminum alloy, and has a long plate shape with a substantially rectangular cross-sectional shape. The frame body 410 is provided with a central through hole 411 located at the center in the width direction and three types of eccentric through holes 412a, 412b, and 412c shifted in the width direction. There are two eccentric through holes 412a across the center through hole 411, four eccentric through holes 412b in the width direction of the frame body 410, and one eccentric through hole 412c at four corners of the cross section of the frame body 410. A total of four are provided. A total of ten slits 415 extending in the longitudinal direction are provided on the side surfaces 413 and 414 of the frame body 410.

  As shown in FIG. 2, the damping member 20 includes a mass member 21 and a buffer material 22, and the mass member 21 is provided in the same length as the frame body 410, and the buffer material 22 is as shown in FIG. 2. A plurality of them are provided at equal intervals. The damping member 20 is inserted into one of the corner through holes 412.

Next, examples according to the fourth embodiment and comparative examples will be described in detail.
(Example 18a to Example 18h)
In Example 18a to Example 18h, the aluminum body (model AFS-45180B-8) manufactured by NF Autotech Co., Ltd., height 45 mm × width 180 mm × length 1500 mm is used as the frame body 410, and the length of the mass member 20 The thickness was set to 1500 mm, and the test was performed in the same manner as in Example 17a to Example 17h except that the width direction was horizontal, and the attenuation ratio of the bending primary mode in the weak axis direction was calculated. The attenuation ratio magnification with respect to the attenuation ratio of the frame body 410 only) was determined.

(Comparative Example 4)
Except that the damping member 20 was omitted, tests were performed in the same manner as in Example 18a to determine the natural frequency and damping ratio.

(Fifth embodiment)
FIG. 8 shows a long member 500 for a high attenuation assembly frame according to the fourth embodiment of the present invention. The long member 500 includes a frame main body 510 and the vibration damping member 20.

  The frame body 510 is made of an extruded material of aluminum alloy, and has a long plate shape with a substantially rectangular cross-sectional shape. The frame main body 510 is provided with a central through hole 511 located at the center in the width direction and two types of eccentric through holes 512a and 512b shifted in the width direction. Two eccentric through-holes 512a are provided across the center through-hole 511, and four eccentric through-holes 512b are provided, one at each of the four corners of the cross section of the frame body 510. A total of six slits 415 extending in the longitudinal direction are provided on side surfaces 513 and 514 of the frame main body 510.

  As shown in FIG. 2, the damping member 20 includes a mass member 21 and a buffer material 22, and the mass member 21 is provided in the same length as the frame body 510, and the buffer material 22 is as shown in FIG. 2. A plurality of them are provided at equal intervals. The damping member 20 is inserted into the central through hole 511.

Next, examples and comparative examples according to the fifth embodiment will be described in detail.
(Example 21a to Example 21h)
In Example 21a to Example 21h, an aluminum frame (model SFF-334) manufactured by SUS Co., Ltd., having a height of 30 mm, a width of 60 mm, and a length of 465 mm was used as the frame body 510.
The damping member 20 was the same as that of Example 17a except that the mass member 21 had a length of 465 mm and the cushioning material had a length of 95 mm, and was inserted into the central through hole 511 of the frame body 510.
In addition, when measuring the bending mode of the frame main body 510 in the weak axis direction, the width direction is horizontal, and when measuring the bending mode in the strong axis direction, the frame body 510 is suspended with the width direction vertical. The test was performed in the same manner as in Example 17h, and the attenuation ratio and attenuation ratio of the bending primary mode in the weak axis direction and the bending primary mode in the strong axis direction were obtained.

(Example 22a to Example 22f)
In Example 22a to Example 22f, the length of the frame main body 510 is 220 mm, the length of the mass member is 220 mm, and the number of cushioning materials is 3, 4, 5, 6, 7, and 9. The tests were performed in the same manner as in Example 21a to Example 22h, and the attenuation ratio and attenuation ratio of the bending primary mode in the weak axis direction and the bending primary mode in the strong axis direction were obtained.

(Comparative Examples 7 and 8)
Except that the damping member 20 was omitted, the test was performed in the same manner as in Example 21a and Example 22a, and the natural frequency and attenuation of the bending primary mode in the weak axis direction and the bending primary mode in the strong axis direction were tested. The ratio was determined.

Table 3 shows the test conditions of Examples 17a to 22f according to the third to fifth embodiments and the natural frequencies of Comparative Examples 3 to 8 (only the frame body). FIG. 10 shows the relationship with the natural frequency of only the frame body.

From FIG. 10, it was found that when the natural frequency of the frame main body exceeds 1000 Hz, the damping ratio magnification is as low as less than 10 times, and the effect of providing the damping member cannot be sufficiently obtained.
Note that the natural frequencies and damping ratios obtained in the above-described examples and comparative examples are all obtained for vibration modes accompanied by deformation of the frame body.

(Other embodiments)
The long member for assembling a frame of the present invention is not limited to the above-described embodiment. For example, the number of through holes of the frame body is not limited to the number of the above-described embodiments, and may be provided by an arbitrary number of one or more. The vibration damping member may be provided in only one through hole, in a plurality of through holes, in some through holes, or in all through holes. The frame body is not limited to a square or rectangular cross-sectional shape, but is known in the art such as a polygon surrounded by a curve such as a circle or a circle, an ellipse, or a curve or a curve surrounded by a straight line. A cross-sectional shape can be appropriately employed. The material of the frame body is not limited to an aluminum alloy, and known materials such as wood, concrete, resin, and various composite materials can be used as appropriate in addition to metals such as iron and stainless steel.
Similarly, the mass member is not limited to a metal, and a known material can be appropriately used in addition to a resin and various composite materials.
Further, when a plurality of buffer materials are provided intermittently, the buffer materials can be provided at non-equal intervals in the longitudinal direction of the mass member. The cushioning material may be wound for a length of less than one turn of the mass member, or may be wound for a length of one turn or more.
Furthermore, the through hole may be provided by forming the frame body with two or more parts, providing a groove in one of the two or more parts, and closing the groove with another part.

1000 High attenuation assembly frame 100 Long member 10 for high attenuation assembly frame Frame body 11 Center part through hole (through hole)
12 corner through hole (eccentric through hole)
20 Damping member 21 Mass member 22 Buffer member 200 Long member 210 for high attenuation assembly frame Frame body 212 Eccentric through hole 300 Long member 310 for high attenuation assembly frame Frame body 311 Center through hole (through hole)
312 Eccentric through hole 400 Long member 410 for high attenuation assembly frame Frame body 411 Center through hole (through hole)
412a, 412b, 412c Eccentric through-hole 500 Long member 510 for high-damping assembly frame Frame body 511 Center through-hole (through-hole)
512a, 512b Eccentric through hole

Claims (7)

An elongated frame body having one or more through holes extending in the longitudinal direction;
A damping member inserted into at least one of the through holes,
The damping member is a long member for a high-damping assembly frame that includes a rod-shaped mass member and a cushioning material that is inserted between the mass member and an inner wall of the through-hole to support the mass member.   The long member for a high attenuation assembly frame according to claim 1, wherein a plurality of the cushioning materials are provided so as to intermittently support a plurality of locations in the longitudinal direction of the mass member. The one or more through holes have at least one eccentric through hole provided at a position eccentric from the central axis of the frame body,
The long member for a high damping assembly frame according to claim 1, wherein the damping member is inserted into the eccentric through hole. The frame body includes a plurality of eccentric through holes with different distances from the central axis,
The long member for a high attenuation assembly frame according to claim 3, wherein the vibration damping member is inserted into an eccentric through hole farthest from the central axis. The eccentric through-hole includes at least one pair of eccentric through-holes symmetrical about the central axis,
The long member for a high-damping assembly frame according to claim 3 or 4, wherein the damping member is inserted into at least both of the pair of eccentric through holes.   The long member for a high-damping assembly frame according to any one of claims 1 to 5, wherein a natural frequency related to at least one vibration mode among vibration modes in which the frame main body is deformed is 1000 Hz or less.   A high attenuation assembly frame using the long member for a high attenuation assembly frame according to any one of claims 1 to 6.

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