JP2007145345A - Packaging system, packaging box, and packaging method - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a packaging system, a packaging box and a packaging method that show a high vibration isolation and that can be utilized for precision machines. <P>SOLUTION: Resonance generated with a resonance frequency of a vibration system constituted of a box 10, a casing 2 and a vibration isolation member 3 is eliminated by a dynamic vibration reducer constituted of a weight 11 and a dynamic vibration reducer shock absorbing material 12, and then vibration applied to the casing 2 is restricted as small as possible. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a precision instrument packaging system, a packaging box, and a packaging method.

Electronic cases used in medical equipment such as MR include precision equipment and are often tall.
When packing these precision devices, it is necessary to reduce the load on the devices during transportation, such as vibration and impact.

As a packing method for reducing the load, for example, there is a method of putting a vibration proof / buffer material in the lower part of the packing box.
Hereinafter, the anti-vibration effect in such a general anti-vibration system will be briefly described.

The anti-vibration effect is explained by the relationship between vibration transmissibility and frequency.
FIG. 3 shows the relationship between the vibration transmissibility Tr and the frequency f when there is general attenuation.
FIG. 3 is a diagram showing the relationship between the vibration transmissibility Tr and the frequency f.
The vibration transmissibility Tr is the ratio of the vibration of the vibration isolation system and the vibration of the foundation (floor etc.), that is, when it is smaller than 1, the vibration isolation effect appears.
When the frequency f of the vibration-proof object is the same as the natural frequency when the vibration is prevented (P1 in FIG. 3), the vibration is amplified. This phenomenon is called a resonance phenomenon, and the frequency at this time is called a resonance frequency (≈natural frequency).
In the portion where the vibration transmissibility Tr is smaller than 1, as described above, the anti-vibration effect is exhibited. In other words, the lower the resonance frequency is, the wider the range having an anti-vibration effect is.

However, in the general vibration isolation system described above, there is a disadvantage that there is a frequency band that cannot be fully vibration-proofed as indicated by a range in which the vibration transmissibility Tr in FIG.
In order to increase vibration resistance and impact resistance, it is desirable to support the device softly. However, when packing medical devices with a tall casing, weakening the support may cause instability. There was a disadvantage that it was difficult to form a vibration system.

  In order to eliminate the disadvantages described above, an object of the present invention is to provide a packing system, a packing box, and a packing method that have high vibration isolation and can be used for precision equipment.

  In order to eliminate the disadvantages described above, the packaging system of the first aspect of the invention is a packaging system for packaging a packaged body, and a first support for supporting a weight, the packaged body, and the weight. A body, a body to be packed, the weight, and a packaging box for packing the first support, and the first support includes a first spring element, and the weight The first spring element constitutes a dynamic vibration absorber.

  Preferably, the apparatus further includes a second support for supporting the packaging box, and the second support includes a second spring element, and the weight and the first spring element constitute the movement. The vibration absorber is designed on the basis of the resonance frequency of the vibration isolation system constituted by the packing box and the second spring element.

  More preferably, the weight of the weight is calculated based on an equivalent mass of the vibration isolation system formed by the packaging box and the second spring element.

  More preferably, the first spring element has a spring constant and a damping constant, and the spring constant and the damping constant of the first spring element are the weight of the weight and the equivalent mass of the vibration isolation system. And the resonance frequency of the vibration isolation system constituted by the packing box and the second spring element.

  More preferably, the packaged body includes a housing of a medical device.

  More preferably, the weight includes a package of the medical device.

  A packaging box according to a second aspect of the present invention is a packaging box for packing a packaged body and a packaged product of the packaged body, and supports the packaged body and the packaged product of the packaged body. The package includes a support, and the package of the packaged object constitutes a dynamic vibration absorber together with the first support as a weight.

  The packing method of the invention of the third aspect is a packing method for packing a packaged body, a weight, and the packaged body and a first support body supporting the weight in a packaging box, the weight and A dynamic vibration absorber is constituted by the first support.

  According to the present invention, it is possible to provide a packing system, a packing box, and a packing method that are highly vibration-proof and can be used for precision equipment.

Hereinafter, embodiments of the present invention will be described.
FIG. 1 is a block diagram of the packaging box 1 of the present embodiment.
As shown in FIG. 1, the packaging box 1 includes a box 10, a weight 11, a dynamic vibration damper cushioning material 12, and a housing 2, and is supported on a vibration isolation material 3 and a base 4 to constitute a vibration isolation system. ing.

The box 10 is a box for packing the casing 2 and is selected in consideration of packing an electronic device. For example, corrugated board etc. are mentioned.
The weight 11 and the dynamic vibration absorber cushioning material 12 together form a dynamic vibration absorber.
The weight 11 is a weight of the dynamic vibration absorber, and uses a packaged electronic device in the housing 2, that is, a cable, a manual, or the like.
As will be described later, in order to maximize the effect of the dynamic vibration absorber, the mass of the weight 11 must be set appropriately, but the packaged electronic equipment in the housing 2 is insufficient for the appropriate mass. May be used by adding an appropriate weight.

The dynamic vibration damper cushioning material 12 supports the casing 2 and the weight 11 so that the weight 11 can swing, and is connected to the box 10.
As the dynamic vibration absorber cushioning material 12, for example, a material having a large damping centering on an elastomer such as urethane elastomer is used, and a high effect as a dynamic vibration absorber is obtained. A method for setting a spring constant and a damping constant necessary for determining the material will be described later.

The housing 2 is a housing that encloses precision equipment, and is an object to be packaged and vibration-proof in the present invention. In the present embodiment, the housing 2 is assumed to be a housing containing precision equipment such as a control device of an MR apparatus (magnetic resonance diagnostic apparatus) and other medical equipment.
The anti-vibration material 3 is an anti-vibration cushioning material that supports the packaging box 1. For example, anti-vibration rubber or the like is used.
The base 4 is a base on which the packaging box 1 supported by the vibration isolator 3 is placed.

Next, the function of the dynamic vibration absorber will be briefly described.
FIG. 2 is a diagram illustrating an example of a dynamic vibration absorber.
As shown in FIG. 2, the dynamic vibration absorber 100 is formed of a weight 101, a spring member 102, and a damping member 103, and is attached to a structure 200 that is an object of vibration isolation. The structure 200 is supported by the spring element 300 and connected to the floor 400.

The spring element 300 and the structure 200 supported by the spring element 300 have a resonance frequency specific to the vibration isolation system formed by them. In addition, it is assumed that vibration corresponding to the force acting on the structure 200 is generated.
The dynamic vibration absorber 100 appropriately adjusts the overall resonance frequency by selecting a weight 101 having an appropriate mass, a spring member 102 having an appropriate spring constant, and a damping member 103 having an appropriate damping constant. In particular, a force that cancels resonance can be applied to the structure 200.

As described above, in order for the dynamic vibration absorber 100 to achieve a high effect, it is necessary to appropriately set the mass of the weight 101, the spring constant of the spring member 102, and the damping constant of the damping member 103.
Hereinafter, an optimal value setting method will be described.

  Each of the weight 101, the spring member 102, and the damping member 103 includes a mass m2, a spring constant corresponding to the resonance frequency of the structure 200, as shown in the following formulas (1), (2), and (3). k2 and attenuation constant c2.

  In Equations (1), (2), and (3), μ is a mass ratio, ω1 is a natural frequency of the structure 200, and m1 is a structure corresponding to the natural frequency ω1. This is the equivalent mass of the body 200. Here, the mass ratio μ is expressed by Equation (4). In addition, the natural frequency ω1 of the structure 200 is expressed by Equation (5) by the equivalent mass m1 and the elastic coefficient k1 of the vibration isolation system constituted by the structure 200 and the spring element 300.

  In Equations (1), (2), and (3), ω2 is the natural frequency of the dynamic vibration absorber 100, γopt is the optimum natural frequency ratio, and ζ2opt is the optimum damping ratio. is there. Here, the natural frequency ω <b> 2 of the dynamic vibration absorber 100 is expressed by Equation (6) by the equivalent mass m <b> 2 and the elastic coefficient k <b> 2 of the dynamic vibration absorber 100. Then, the optimum natural frequency ratio γopt is expressed as in Expression (8) by the damping ratio ζ1 of the gradient coil section 13 expressed in Expression (7). Then, the optimum damping ratio ζ2opt is expressed as Equation (9).

When setting the mass m2, the spring constant k2, and the damping constant c2 in the dynamic vibration absorber 100, first, an equivalent for the natural vibration mode in which vibration is reduced in the vibration isolation system constituted by the structure 200 and the spring element 300. The mass m1 is obtained. Here, modal analysis is used, which is identified from the change in the natural frequency when a weight is loaded. Next, for the mass m2 of the dynamic vibration absorber 100, a large value is set with the mass ratio μ set to 0.1. Next, the optimum natural frequency ratio γopt determined from the mass ratio μ is determined for the spring constant k2 of the dynamic vibration absorber 100 and determined. Next, the optimum damping ratio ζ2opt determined from the mass ratio μ is determined for the damping constant c2 of the dynamic vibration absorber 100. Further, based on the mass m2, the spring constant k2, and the damping constant c2 determined as described above, the values are optimized within a designable range.
Based on the optimum conditions thus obtained, the mass of the weight 101, the spring constant of the spring member 102, and the damping constant of the damping member 103 are determined.

In this embodiment, the weight 11 corresponds to the weight 101 of the dynamic vibration absorber 100, the dynamic vibration absorber cushioning material 12 corresponds to the spring member 102 and the damping member 103, and the box 10 containing the housing 2 is a structural body. The vibration isolator 3 corresponds to the spring element 300, and the mass of the weight 11 and the spring constant and damping constant of the dynamic vibration damper cushioning material 12 can be determined by the same method as described above.
The dynamic vibration damper cushioning material 12 may be formed of a spring member having a spring constant and a damping member having a damping constant independent of the spring member. You may form only with the material which has both a spring constant and a damping constant.

  As described above, the dynamic vibration absorber constituted by the weight 11 and the dynamic vibration absorber cushioning material 12 cancels the resonance at the resonance frequency of the vibration system constituted by the box 10, the case 2 and the vibration isolation material 3. The vibration applied to can be minimized.

As described above, according to the packaging box 1 of the present embodiment, the dynamic vibration absorber is configured by the weight 11 and the dynamic vibration absorber cushioning material 12, and vibrations cannot be suppressed in the conventional general vibration isolation system. Vibration near the resonance frequency of the vibration isolation system can be suppressed.
Moreover, according to the packaging box 1 of this embodiment, since a housing | casing can be firmly supported by the box 10 and the dynamic vibration damper cushioning material 12, it is statically stable also with respect to the tall housing | casing of medical equipment, such as MR apparatus. Can be kept.
Moreover, since the package of the electronic device in the housing | casing 2 is utilized as a weight of a dynamic vibration absorber, an efficient packing form can be formed.
Further, since the resonance frequency of the vibration isolation system is often single, there is an advantage that the dynamic vibration absorber can be easily designed.

The present invention is not limited to the embodiment described above.
That is, those skilled in the art may make various modifications, combinations, subcombinations, and alternatives regarding the components of the above-described embodiments within the technical scope of the present invention or an equivalent scope thereof.
In the present embodiment, the case 2 is assumed to be a case containing a precision device such as a control device of an MR apparatus (magnetic resonance diagnostic apparatus) or other medical equipment, but the present invention is not limited to this. Instead, in the present invention, it is possible to make all objects to be subjected to vibration resistance / impact measures at the time of packing as targets for packing and vibration isolation.

FIG. 1 is a block diagram of the packaging box 1 of the present embodiment. FIG. 2 is a diagram illustrating an example of a dynamic vibration absorber. FIG. 3 is a diagram showing the relationship between the vibration transmissibility Tr and the frequency f.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Packing box, 10 ... Box, 11 ... Weight, 12 ... Dynamic vibration damper cushioning material, 2 ... Housing, 3 ... Anti-vibration material, 4 ... Base, 100 ... Dynamic vibration absorber, 101 ... Weight, 102 ... Spring member 103 ... Damping member, 200 ... Structure, 300 ... Spring element, 400 ... Floor

Claims (8)

A packing system for packing an object to be packed,
Weight,
A first support for supporting the packaged body and the weight;
A packing box for packing the packaged body, the weight, and the first support;
Have
The first support includes a first spring element;
The weight and the first spring element constitute a dynamic vibration absorber. A second support for supporting the packing box;
The second support includes a second spring element;
The dynamic vibration damper which the said weight and said 1st spring element comprise is designed based on the resonant frequency of the vibration proof system which the said packaging box and said 2nd spring element comprise. Packing system. The packaging system according to claim 2, wherein the weight of the weight is calculated based on an equivalent mass of the vibration isolation system formed by the packaging box and the second spring element. The first spring element has a spring constant and a damping constant;
The spring constant and the damping constant of the first spring element are the mass ratio between the weight of the weight and the equivalent mass of the vibration isolation system, and the vibration isolation system formed by the packing box and the second spring element. The packaging system according to claim 2, wherein the packaging system is calculated based on a resonance frequency. The packaging system according to claim 1, wherein the packaged body includes a housing of a medical device. The packaging system according to any one of claims 1 to 5, wherein the weight includes a package of the medical device. A packing box for packing the packaged body and the packaged package.
A first support body for supporting a packaged body and a packaged object of the packaged body;
The package of the packaged object constitutes a dynamic vibration absorber together with the first support as a weight. A packing method for packing a packaged body, a weight, and a first support body for supporting the packaged body and the weight in a packaging box,
A packaging method in which a dynamic vibration absorber is constituted by the weight and the first support.

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