CN210259241U

CN210259241U - Vibration-proof pallet and glass bundle package

Info

Publication number: CN210259241U
Application number: CN201790001358.3U
Authority: CN
Inventors: 野田隆行
Original assignee: Nippon Electric Glass Co Ltd
Current assignee: Nippon Electric Glass Co Ltd
Priority date: 2016-12-09
Filing date: 2017-12-05
Publication date: 2020-04-07
Anticipated expiration: 2027-12-05
Also published as: JP7022391B2; WO2018105615A1; CN210364828U; JPWO2018105615A1; TW201834938A; JPWO2018105612A1; TW201834937A; WO2018105612A1

Abstract

An anti-vibration pallet (1) for conveying a load (5) comprising an inorganic brittle material is provided with a pallet section (2) for storing the load (5), a vibration isolator (3) arranged on the lower surface of the pallet section (2), and a base section (4) for holding the pallet section (2) via the vibration isolator (3). The vibration isolator (3) has a helical elastic body (31) disposed so that the central axis (X) is oriented in the lateral direction, and holding devices (32, 33) for holding the helical elastic body (31) in a state of being wound in a helical shape.

Description

Vibration-proof pallet and glass bundle package

Technical Field

The utility model relates to a antivibration tray and glass bundle inclusion.

Background

As an anti-vibration tray used for conveying a load such as a precision instrument, there is an anti-vibration tray including a table portion for storing the load, a vibration isolator disposed on a lower surface of the table portion, and a base portion for holding the table portion via the vibration isolator.

As a vibration isolator for a vibration-proof tray, for example, as shown in patent document 1, a vibration isolator having a coil spring arranged such that a center axis thereof is oriented in a vertical direction is widely used. Such a vibration isolator (hereinafter, also referred to as an inverted spring (longitudinal spring) type vibration isolator) absorbs an impact in a longitudinal direction (for example, in a vertical direction) by longitudinal deflection of a coil spring, and absorbs an impact in a lateral direction (for example, in a horizontal direction) by lateral deflection of the coil spring.

Documents of the prior art

Patent document

Patent document 1: japanese patent laid-open publication No. 2016-8664

SUMMERY OF THE UTILITY MODEL

Problem to be solved by utility model

However, when a load made of an inorganic brittle material such as a glass plate is transported, a vibration-proof tray provided with an inverted spring type vibration damper may be used, but the following problems occur.

That is, the coil spring is configured to be relatively smoothly deformed by expansion and contraction accompanying longitudinal deflection. Therefore, when a longitudinal impact is input, the impact can be effectively absorbed by the longitudinal deflection of the coil spring. On the other hand, when a lateral impact is input, the impact is absorbed by lateral deflection of the coil spring, but the lateral deflection has a deformation element such as shear deformation while bending deformation of the coil spring dominates. The above-described lateral deformation can be generated in the range of the expansion/contraction margin of the coil spring. However, when the coil spring is compressed by a vertical load generated by a load or the like during conveyance, the margin of the expansion/contraction margin is reduced, and the lateral deformation is hindered. Therefore, it is difficult to exhibit a sufficient impact absorption effect with respect to an impact input simultaneously generated from any direction during conveyance, and there is a possibility that the inorganic brittle material included in the load is broken. Examples of the breakage of the inorganic brittle material include fracture, defect, and scratch.

Further, since the bending deformation mainly caused by the lateral deflection causes the platform portion to be inclined, the load is likely to swing when absorbing the lateral impact. This swing is a lateral swing accompanying a pendulum-like motion, and is particularly large above the load. Further, since the lateral swing is accompanied by a continuous change in the position of the center of gravity of the load being conveyed, there is a possibility that continuous vibration of the load is induced. Therefore, the inorganic brittle material included in the load may be broken by such continuous vibration of the load.

The technical problem of the utility model is to provide a vibration-proof tray that can reliably prevent the damage of inorganic brittle material when carrying.

Means for solving the problems

The present invention has been made to solve the above-mentioned problems, and an object of the present invention is to provide an anti-vibration pallet for conveying a load including an inorganic brittle material, the anti-vibration pallet including a deck portion for storing the load, a vibration isolator disposed on a lower surface of the deck portion, and a base portion for holding the deck portion via the vibration isolator, the vibration isolator including a spiral elastic body disposed so that a central axis thereof is oriented in a lateral direction, and a holding device for holding the spiral elastic body.

According to such a configuration, first, the spiral elastic body of the vibration damper is flexibly deformed against an external impact input, and therefore, the impact input generated simultaneously from any direction can be sufficiently absorbed. Specifically, the helical elastic body has deformation (compression deformation) that is different in element from deformation (shear or rotational deformation) that is caused by absorbing a longitudinal impact. That is, since the deformation for absorbing the longitudinal impact and the deformation for absorbing the lateral impact can be generated independently of each other, even if the deformations are generated simultaneously, the deformations do not interfere with each other. Therefore, the impact input generated simultaneously from any direction can be sufficiently absorbed as described above. Second, when lateral impact is absorbed, lateral oscillation such as a pendulum is less likely to occur, and therefore the deck portion is less likely to tilt. Therefore, the cargo is less likely to generate an inappropriate vibration accompanying the swinging. Therefore, the damage of the inorganic brittle material during conveyance can be reliably prevented by the above-described impact absorption effect and vibration prevention effect.

In the above-described configuration, the spiral elastic body is preferably a metal cable. In this way, when the spiral elastic body is deformed, resistance against deformation is generated due to friction between the wires constituting the metal cable and the course of the weave. As a result, it is possible to appropriately attenuate the continuous change in the deformed state of the spiral elastic body. The vibration generation due to the impact input can be converged promptly by this damping effect.

In the above-described structure, the spiral elastic body may be embedded in the rubber material. In this way, when the helical elastic body is deformed, the continuous change in the deformed state of the helical elastic body can be appropriately attenuated so as not to largely inhibit the deformation of the helical elastic body. The vibration generation due to the impact input can be converged promptly by this damping effect. Further, since the spiral elastic body is protected by the rubber material, for example, even when the spiral elastic body comes into contact with a claw of a forklift, damage to the spiral elastic body can be prevented.

In the above-described configuration, it is preferable that the platform portion has a rectangular shape in plan view, the vibration isolators be disposed at least at four corners of the platform portion, and center axes of the spiral elastic bodies of the vibration isolators disposed at the four corners be inclined with respect to adjacent sides of the platform portion constituting the corners at which the vibration isolators are disposed. In this way, the degree of freedom of shock absorption can be improved at the four corners of the platform portion where displacement in any direction is likely to concentrate.

In the above-described configuration, it is preferable that the central axes of the spiral elastic bodies of the vibration isolators disposed at the four corners are inclined with respect to the adjacent both sides of the cargo bed portion constituting the corners at which the vibration isolators are disposed.

In the above-described configuration, it is preferable that the center axis of the spiral elastic body of the vibration isolator disposed at each of the four corners is along a line orthogonal to a bisector of an angle formed by two adjacent sides of the shelf portion constituting the corner portion at which the vibration isolator is disposed.

In the above structure, the inorganic brittle material may be a glass material or a ceramic material.

A stacked body in which a plurality of glass plates are stacked in the vertical posture may be placed as a package on the vibration-proof tray, thereby forming a glass plate package.

Effect of the utility model

As described above, according to the present invention, the breakage of the inorganic brittle material during conveyance can be reliably prevented.

Drawings

Fig. 1A is a side view showing the vibration-proof tray.

Fig. 1B is a plan view showing the vibration-proof tray.

Fig. 2 is a perspective view showing a vibration isolator of the vibration isolation tray.

Fig. 3A is a view for explaining compression deformation of the vibration isolator.

Fig. 3B is a diagram for explaining shear deformation of the vibration isolator.

Fig. 3C is a view for explaining rotational deformation of the vibration isolator.

Fig. 4 is a side view showing an example of a bundle (glass bundle) in which goods are accommodated in an anti-vibration tray.

Fig. 5 is a side view showing another example of a bundle (glass bundle) with goods accommodated in an anti-vibration tray.

Fig. 6 is a schematic plan view showing the vibration-proof tray of example 1.

Fig. 7 is a schematic plan view showing the vibration-proof tray of example 2.

Fig. 8 is a schematic plan view showing the vibration-proof tray of example 3.

Fig. 9A is a graph showing the entire waveform of the input shock in the comparative example, and is a graph showing the measurement result in the front-rear direction.

Fig. 9B is a graph showing the entire waveform of the input shock in the comparative example, and is a graph showing the measurement result in the left-right direction.

Fig. 9C is a graph showing the entire waveform of the input shock in the comparative example, and is a graph showing the measurement result in the vertical direction.

Fig. 10A is a graph showing the entire waveform of the vibration-proof result of the lower part of the load of the comparative example, and is a graph showing the measurement result in the front-rear direction.

Fig. 10B is a graph showing the entire waveform of the vibration-proof result of the lower part of the load in the comparative example, and is a graph showing the measurement result in the left-right direction.

Fig. 10C is a graph showing the entire waveform of the vibration-proof result of the lower part of the load of the comparative example, and is a graph showing the measurement result in the vertical direction.

Fig. 11A is a graph showing the entire waveform of the vibration-proof result of the upper part of the load of the comparative example, and is a graph showing the measurement result in the front-rear direction.

Fig. 11B is a graph showing the entire waveform of the vibration-proof result of the upper part of the load of the comparative example, and is a graph showing the measurement result in the left-right direction.

Fig. 11C is a graph showing the entire waveform of the vibration-proof result of the upper part of the load of the comparative example, and is a graph showing the measurement result in the vertical direction.

Fig. 12A is a graph showing the entire waveform of the input shock in example 3, and is a graph showing the measurement result in the front-rear direction.

Fig. 12B is a graph showing the entire waveform of the input shock in example 3, and is a graph showing the measurement result in the left-right direction.

Fig. 12C is a graph showing the entire waveform of the input shock in example 3, and is a graph showing the measurement result in the vertical direction.

Fig. 13A is a graph showing the entire waveform of the vibration-proof result of the lower part of the load in example 3, and is a graph showing the measurement result in the front-rear direction.

Fig. 13B is a graph showing the entire waveform of the vibration-proof result of the bottom of the load in example 3, and is a graph showing the measurement result in the left-right direction.

Fig. 13C is a graph showing the entire waveform of the vibration-proof result of the lower part of the load in example 3, and is a graph showing the measurement result in the vertical direction.

Fig. 14A is a graph showing the entire waveform of the vibration-proof result of the upper part of the cargo in example 3, and is a graph showing the measurement result in the front-rear direction.

Fig. 14B is a graph showing the entire waveform of the vibration-proof result of the upper part of the load in example 3, and is a graph showing the measurement result in the left-right direction.

Fig. 14C is a graph showing the entire waveform of the vibration-proof result of the upper part of the load in example 3, and is a graph showing the measurement result in the vertical direction.

Fig. 15A is a graph showing a 1 second enlarged waveform of an input impact in the comparative example, and is a graph showing a measurement result in the front-rear direction.

Fig. 15B is a graph showing a 1-second enlarged waveform of an input impact in the comparative example, and is a graph showing a measurement result in the left-right direction.

Fig. 15C is a graph showing a 1-second enlarged waveform of the input shock in the comparative example, and is a graph showing the measurement results in the vertical direction.

Fig. 16A is a graph showing an enlarged waveform of 1 second showing the vibration-proof result of the lower part of the load of the comparative example, and is a graph showing the measurement result in the front-rear direction.

Fig. 16B is a graph showing an enlarged waveform of 1 second showing the vibration-proof result of the lower portion of the load of the comparative example, and is a graph showing the measurement result in the left-right direction.

Fig. 16C is a graph showing an enlarged waveform of 1 second showing the vibration-proof result of the lower portion of the load of the comparative example, and is a graph showing the measurement result in the vertical direction.

Fig. 17A is a graph showing an enlarged waveform of 1 second showing the vibration-proof result of the upper part of the load of the comparative example, and is a graph showing the measurement result in the front-rear direction.

Fig. 17B is a graph showing an enlarged waveform of 1 second showing the vibration-proof result of the upper portion of the load of the comparative example, and is a graph showing the measurement result in the left-right direction.

Fig. 17C is a graph showing an enlarged waveform of 1 second showing the vibration-proof result of the upper portion of the load of the comparative example, and is a graph showing the measurement result in the vertical direction.

Fig. 18A is a graph showing a 1 second enlarged waveform of an input impact in example 3, and is a graph showing a measurement result in the front-rear direction.

Fig. 18B is a graph showing a 1-second enlarged waveform of the input impact in example 3, and is a graph showing the measurement result in the left-right direction.

Fig. 18C is a graph showing a 1 second enlarged waveform of the input shock in example 3, and is a graph showing the measurement results in the vertical direction.

Fig. 19A is a graph showing a 1 second enlarged waveform of the vibration-proof result of the lower part of the load in example 3, and is a graph showing the measurement result in the front-rear direction.

Fig. 19B is a graph showing a 1-second enlarged waveform of the vibration-proof result of the lower portion of the load in example 3, and is a graph showing the measurement result in the left-right direction.

Fig. 19C is a graph showing a 1-second enlarged waveform of the vibration-proof result of the lower portion of the load in example 3, and is a graph showing the measurement result in the vertical direction.

Fig. 20A is a graph showing a 1 second enlarged waveform of the vibration-proof result of the upper part of the cargo of example 3, and is a graph showing the measurement result in the front-rear direction.

Fig. 20B is a graph showing a 1-second enlarged waveform of the vibration-proof result of the upper portion of the load in example 3, and is a graph showing the measurement result in the left-right direction.

Fig. 20C is a graph showing the vibration-proof result of the upper part of the load of example 3, which is a waveform enlarged for 1 second, and is a graph showing the measurement result in the vertical direction.

Fig. 21 is a front view showing a first modification of the vibration isolator.

Fig. 22 is a plan view showing a second modification of the vibration isolator.

Detailed Description

Hereinafter, embodiments of the present invention will be described with reference to the drawings.

As shown in fig. 1A and 1B, the vibration-proof tray 1 according to the present embodiment includes a cargo bed portion 2, a vibration isolator 3 disposed on a lower surface of the cargo bed portion 2, and a base portion 4 that holds the cargo bed portion 2 via the vibration isolator 3.

A load 5 made of an inorganic brittle material is accommodated on the upper surface of the platform portion 2. The cargo bed portion 2 includes frames 21 and support bars 22 vertically and horizontally arranged between the frames 21. The frame 21 and the support bars 22 are made of metal (preferably, stainless steel).

The lower surface of the base portion 4 is placed on the floor surface, a cargo bed of a truck, or the like. The base portion 4 includes a metal frame and support bars, as in the case of the cargo portion 2.

As shown in fig. 2, the vibration isolator 3 includes a spiral elastic body 31 disposed so that the central axis X is oriented in the lateral direction (preferably, the horizontal direction), and a pair of holding

members

32 and 33 for holding the spiral elastic body 31, and the vibration isolator 3 is generally cylindrical as a whole. The vibration isolators 3 are disposed at positions corresponding to the frames and support bars of the cargo bed 2 and the base 4.

The spiral elastic body 31 may be a resin material containing a rubber material, or the like, but in the present embodiment is a metal cable (metal material) formed by twisting and/or weaving a thin metal wire (for example, iron, stainless steel, or the like). In particular, from the viewpoint of durability and environmental resistance, the metal material is preferably a stainless steel material.

Specifically, the spiral elastic body 31 is formed by winding a metal cable having a bent portion 31a folded in two at an intermediate portion thereof around end portions different from each other so as to draw opposite spirals on the same central axis. That is, the spiral elastic body 31 has a right wound portion 31b and a left wound portion 31c with the bent portion 31a as a boundary. Each of the

holders

32 and 33 is a long plate material, and has a plurality of through

holes

32a and 33a for passing the spiral elastic body 31 therethrough at intervals in the longitudinal direction thereof. The spiral elastic body 31 alternately penetrates through the through

holes

32a and 33a of the holding tool 32 and the holding tool 33, and is maintained in a state of being wound in a spiral shape. The

holders

32 and 33 are disposed parallel to the central axis X of the spiral elastic body 31 and vertically face each other with the central axis X therebetween. That is, in the present embodiment, the longitudinal direction of the vibration isolator 3 coincides with the direction of the central axis X of the spiral elastic body 31.

The

holders

32 and 33 have mounting

holes

32b and 33b, and fixing members such as screws are inserted into the mounting

holes

32b and 33 b. Thus, the vibration damper 3 is detachably attached to the platform portion 2 and the base portion 4. By configuring the vibration isolators 3 to be detachable in this manner, the number and mounting positions of the vibration isolators 3 can be easily adjusted in accordance with the weight of the cargo 5 and the like. The vibration isolator 3 may be configured to be fixed by welding or the like and not to be attached and detached.

In the vibration isolator 3 configured as described above, deformation that absorbs a longitudinal impact (for example, compression deformation as shown in fig. 3A) and deformation that absorbs a lateral impact (for example, shear deformation as shown in fig. 3B or rotational deformation as shown in fig. 3C) are different elements. Therefore, even if the deformation for absorbing the lateral impact and the deformation for absorbing the longitudinal impact occur simultaneously, the respective deformations do not interfere with each other, and there is an advantage that the impact input generated simultaneously from any direction can be sufficiently absorbed. Further, when lateral impact is absorbed, lateral oscillation such as a pendulum is less likely to occur, and the upper surface of the cargo bed portion 2 is less likely to tilt.

Returning again to fig. 1B, it is preferable that four or more vibration isolators 3 be disposed at positions corresponding to the frames and support bars of the cargo bed portion 2 and the base portion 4. In this case, the vibration isolators 3 are preferably disposed at the four corners of the platform 2. The center axis X of the spiral elastic body 31 of the vibration isolator 3 disposed at each of the four corners is preferably inclined with respect to the adjacent two sides of the platform 2 constituting the corner where the vibration isolator 3 is disposed. In this case, for example, the vibration isolators 3 arranged at the four corners are arranged radially or concentrically with respect to the center of the table portion 2. Here, in the vibration-proof tray according to the present embodiment, for example, the cargo 5 is housed so that the four corners of the cargo bed 2 match the four corners of the cargo 5.

In fig. 1B, the central axis X of the spiral elastic body 31 of the vibration isolator 3 disposed at the corner portion is along a line orthogonal to the bisector of the angle formed by the adjacent two sides of the platform portion 2 constituting the corner portion. Here, "along a line orthogonal to the bisector" means a concept that can be regarded as a case where the line is substantially parallel to the line orthogonal to the bisector, in addition to a case where the line is completely coincident with the line orthogonal to the bisector. In this case, the inclination angle θ of the central axis X of the spiral elastic body 31 is preferably 125 to 145 °, and particularly preferably 135 °.

The center axis X of the spiral elastic body 31 of the vibration isolator 3 disposed at the corner portion may be along a bisector of an angle formed by two adjacent sides of the platform portion 2 constituting the corner portion. Here, "along the bisector" means a concept that can be considered to be substantially parallel to the bisector, in addition to a case where the "along the bisector" completely coincides with the bisector. In this case, the inclination angle θ of the central axis X of the spiral elastic body 31 is preferably 35 to 55 °, and particularly preferably 45 °.

As shown in fig. 4 and 5, for example, the vibration-proof tray 1 configured as described above contains a load 5. This forms a bundle provided with the vibration-proof tray 1 and the package 5.

In the package of fig. 4, as the package 5, a stacked body in which glass plates 52 as glass materials are stacked in a vertical posture (preferably, an inclined posture of 45 ° to 80 ° with respect to the horizontal direction, and more preferably, 60 ° to 75 °) is held and fixed on a vertical direction holding base 51. The holding base 51 includes a bottom surface support portion 51a that supports the bottom surface of the stacked body of the glass plates 52 in the vertical posture, and a back surface support portion 51b that supports the back surface of the stacked body. Further, although not shown in the drawings, for example, a pressing plate is disposed at the foremost surface of the laminated body, pressing rods extending to both sides in the width direction (for example, the horizontal direction) of the laminated body are disposed on the pressing plate, and both end portions of the pressing rods are fastened by fastening members so as to be pulled toward the back surface support portion 51b side, whereby the laminated body may be fixed to the holding base 51. In order to restrict the movement of the stacked body in the width direction, a pressing member that presses the side surface of the stacked body may be disposed. Examples of a method for fixing the vibration-proof tray 1 to the holding base 51 include the following: convex portions are provided at four corners of the upper surface of the platform portion 2 of the vibration-proof tray 1, concave portions are provided at four corners of the bottom surface supporting portion 51a of the holding base 51, and the fixing is performed by the fitting of the concave and convex portions. Of course, when the uneven portions are fitted, a concave portion may be provided in the cargo bed portion 2 of the vibration-proof tray 1, and a convex portion may be provided in the bottom surface support portion 51a of the holding bed 51. In this way, the fixing method by fitting the uneven portions facilitates attachment and detachment of the holding base 51 to and from the vibration-proof tray 1. The method of fixing the laminated body to the holding base 51 and the method of fixing the vibration-proof tray 1 to the holding base 51 are not particularly limited, and any fixing method can be employed.

In the package of fig. 5, as the package 5, a laminate in which glass plates 54 as glass materials are laminated in a horizontal posture (preferably 0 ° (horizontal posture) to 30 °, more preferably 0 ° to 15 °) is held and fixed on a horizontal holding base 53. The holding table 53 includes a bottom surface support portion 53a that supports the bottom surface of the stacked body of the glass plates 54 in the horizontal posture. Further, although not shown in the drawings, for example, a pressing plate is disposed on the foremost surface (uppermost surface) of the laminated body, pressing rods extending to both sides of the laminated body are disposed above the pressing plate, and both end portions of the pressing rods are fastened by fastening members so as to be pulled toward the bottom surface support portion 53a side, whereby the laminated body may be fixed to the holding base 53. In order to restrict the lateral displacement of the laminated body, a pressing member that presses the side surface of the laminated body may be disposed. The plurality of pressing members are arranged in a dispersed manner so as to surround, for example, four corners of the laminate. As a method of fixing the vibration-proof tray 1 and the holding base 53, for example, a method of fixing by fitting the uneven portions exemplified in the above-described vertically-placed holding base 51 can be similarly applied. The method of fixing the laminated body to the holding base 53 and the method of fixing the vibration-proof tray 1 to the holding base 53 are not particularly limited, and any fixing method can be employed.

In the case of the laminate described above, protective sheets (not shown) such as paper (backing paper) and foamed resin sheets are preferably interposed between the

glass plates

52 and 54. The size of the cargo bed 2 is not particularly limited, but in the present embodiment, it is substantially the same as the size of the bottom surface of the cargo 5. The glass material includes, in addition to the glass plate, a glass roll, a glass tube, and the like, in which a long glass film is wound in a roll shape. Although not shown, the vibration-proof tray 1 may be loaded with any inorganic brittle material as a load, and for example, a refractory constituting a melting facility, a ceramic molded body for molding molten glass, or the like may be housed therein.

Examples

(example 1)

(1) Goods

The load is a laminate in which glass substrates for a liquid crystal display are laminated on a holding table in an inclined posture of 72 degrees with respect to the horizontal (see fig. 4). The cargo has a size of 1050mm in the longitudinal direction, 1950mm in the transverse direction, 1800mm in height and a weight of 2000 kg.

(2) Vibration-proof tray

As shown in fig. 6, a cable damper (manufactured by Enidine corporation) having a spiral-shaped elastic body made of a stainless steel cable is used as the damper 3 of the vibration-proof tray 1. Fig. 6 to 8 show the structures of the cargo bed 2 and the vibration isolators 3 in a simplified manner. Four vibration isolators 3 were used and each set to a load weight of about 500 kg. The vibration isolators 3 are disposed at the four corners of the platform 2 having substantially the same size (1050 mm in the vertical direction and 1950mm in the horizontal direction) as the bottom surface of the cargo. The inclination angle with respect to the long side of the platform part 2 of each vibration isolator 3 is 135 °. The natural frequency of the vibration system including the load and the vibration-proof tray 1 is set to 5Hz, and the vibration system is designed to absorb vibration of 7Hz or more generated by external impact input. In general, since the main vibration frequency of the conveyance shock is 10Hz or more, a design for absorbing vibration of 7Hz or more is adopted, and thus good vibration-proof characteristics can be obtained.

(example 2)

(1) Goods

The load is a laminate in which glass substrates for a liquid crystal display are laminated on a holding table in a horizontal posture (see fig. 5). The cargo has a size of 2300mm in the longitudinal direction, 2900mm in the transverse direction and 700mm in height, and has a weight of 2200 kg.

(2) Vibration-proof tray

As shown in fig. 7, the same type of cable vibration isolator as in example 1 was used as the vibration isolator 3 of the vibration-isolated tray 1. Ten vibration isolators 3 were used and each set to a load weight of about 220 kg. Four of the vibration isolators 3 are disposed at four corners of the platform 2 having substantially the same size (2300 mm in vertical direction and 2900mm in horizontal direction) as the bottom surface of the cargo, so that the inclination angle with respect to the long side of the platform 2 is 135 °. Of the remaining six vibration isolators 3, two are disposed at the center of each long side of the platform 2, and four are disposed symmetrically near the center of the platform 2. The vibration isolators 3 disposed at the centers of the long sides of the platform 2 are parallel to the long sides of the platform 2, and the vibration isolators 3 disposed near the centers of the platform 2 are parallel to the short sides of the platform 2. By disposing the dampers 3 in this manner, sinking due to flexure of the center portion of the load can be prevented, and the sinking amount of all the dampers 3 can be equalized. The vibration isolator group having a uniform amount of sinking functions as a vibration isolator having a single spring constant, and exhibits excellent vibration isolation characteristics. Similarly to example 1, the natural frequency of the vibration system including the load and the vibration-proof tray 1 was set to 5Hz, and the vibration system was designed to absorb vibration of 7Hz or more generated by an external impact input.

(example 3)

(1) Goods

The cargo was the same as in example 1.

(2) Vibration-proof tray

As shown in fig. 8, the same cable vibration isolators as those of examples 1 and 2 were used as the vibration isolators 3 of the vibration-proof tray 1. Seven vibration isolators 3 were used and each was set to a load weight of about 290 kg. Four of the vibration isolators 3 are disposed at four corners of the cargo bed 2 having substantially the same size (1050 mm in the vertical direction and 1950mm in the horizontal direction) as the bottom surface of the cargo, so that the inclination angle with respect to the long side of the cargo bed 2 is 135 °. Of the remaining three vibration isolators 3, two are disposed one at the center of each long side of the platform 2, and one is disposed at the center of the support surface of the platform 2. The vibration isolators 3 disposed at the centers of the long sides of the platform 2 are parallel to the long sides of the platform 2, and the vibration isolators 3 disposed at the centers of the supporting surfaces of the platform 2 are parallel to the short sides of the platform 2. By disposing the vibration isolators 3 in this manner, sinking of the center portion of the load due to deflection can be prevented. Similarly to examples 1 and 2, the natural frequency of the vibration system including the load and the vibration-proof tray 1 was set to 5Hz, and the vibration system was designed to absorb vibration of 7Hz or more, which is vibration generated by external impact input.

Comparative example

(1) Goods

The cargo was the same as in examples 1 and 3.

(2) Vibration-proof tray

As the vibration isolator of the vibration isolation tray, an inverted spring type vibration isolator is used. The vibration isolators used seven and were each set to a load weight of about 290 kg. Four of the shock absorbers are disposed at four corners of a shelf portion having substantially the same size (1050 mm in the vertical direction and 1950mm in the horizontal direction) as the bottom surface of the cargo. Of the remaining three vibration isolators, two are disposed one at the center of each long side of the platform portion, and one is disposed at the center of the support surface of the platform portion. In the comparative examples, the orientation of the vibration isolator in a plan view is not specified unlike in examples 1 to 3. In addition, as in examples 1 to 3, the natural frequency of the vibration system including the load and the vibration-proof tray was set to 5Hz, and the vibration system was designed to absorb vibration of 7Hz or more generated by an external impact input.

Next, the input shock and vibration-proof results at the time of conveyance are shown in fig. 9A, 9B, 9C to 14A, 14B, and 14C for the above comparative example and example 3, respectively. In each graph of fig. 9A, 9B, 9C to 14A, 14B, and 14C, the vertical axis represents acceleration, and the horizontal axis represents time. Fig. 9A, 9B, and 9C show input impacts of comparative examples, and fig. 10A, 10B, 10C to 11A, 11B, and 11C show vibration-proof results of comparative examples. Fig. 12A, 12B, and 12C show the input shock of example 3, and fig. 13A, 13B, 13C to 14A, 14B, and 14C show the vibration-proof results of example 3. The above results were obtained by the following tests.

First, in each of the comparative examples and example 3, the conveyance was performed for about one hour by a truck. At this time, the impact acceleration during the transportation is measured by the three-axis accelerometer. Accelerometers are mounted on the bed, lower cargo portion and upper cargo portion of the truck, respectively, in the vicinity of the cargo. Then, the measurement results of the accelerometers attached to the load bed of the truck were used as input impacts, and the measurement results of the accelerometers attached to the lower part and the upper part of the load were used as vibration-proof results. The reason why the accelerometers are installed at the lower part of the cargo and the upper part of the cargo, respectively, is to confirm the difference in vibration conditions between the lower part of the cargo and the upper part of the cargo. In the figure, the front-rear direction, the left-right direction, and the up-down direction are based on the traveling direction of the truck.

As shown in fig. 10A, 10B, 10C to 11A, 11B, 11C, 13A, 13B, 13C to 14A, 14B, and 14C, in both comparative example and example 3, the maximum value of the shock after vibration isolation (the maximum amplitude of the vibration waveform) was reduced to about 0.5G. Therefore, at first glance, both are considered to have good vibration-proof performance. However, since there is substantially a large difference in the vibration-proof performance between the two, the difference will be clear from the following description.

That is, fig. 15A, 15B, 15C to 20A, 20B, and 20C show the input shock and the vibration-proof result at the time of conveyance after enlarging a certain period of time during conveyance for 1 second. Fig. 15A, 15B, and 15C show input impacts of comparative examples, and fig. 16A, 16B, 16C to 17A, 17B, and 17C show vibration-proof results of comparative examples. Fig. 18A, 18B, and 18C show the input shock of example 3, and fig. 19A, 19B, 19C to 20A, 20B, and 20C show the vibration-proof results of example 3.

As shown in the above-described figures, it was confirmed that low-frequency vibration of about 1.5Hz was prominent in the front-rear direction of the upper part of the cargo in the vibration-proof results of the comparative examples. Since the vibration was not observed under the load, it was found that the load was vibrated in the front-rear direction as a result of vibration isolation. Further, it was confirmed that the maximum value of the shock after vibration isolation is larger than the maximum value of the shock of the input shock in the front-rear direction and the left-right direction of either the upper part or the lower part of the load due to the influence of the swing, and the situation is deteriorated.

On the other hand, in example 3, no hunting due to low-frequency vibration as in the comparative example was observed, and it was found that the posture of the cargo was stable. In addition, it was confirmed that the maximum shock value was lower than the input shock after vibration isolation in all positions and directions.

While the vibration-proof tray according to the present embodiment has been described above, the embodiment of the present invention is not limited to this, and various modifications can be made without departing from the scope of the present invention.

For example, as shown in fig. 21, the damper 3 may have the spiral elastic body 31 embedded in the rubber material 34. In this case, the rubber material 34 is preferably formed in a substantially cylindrical shape as a whole so as not to hinder the movement of the spiral elastic body 31.

In the above-described embodiment, the case where the right wound portion 31b and the left wound portion 31c are provided as the spiral elastic body 31 of the vibration isolator 3 with the bent portion 31a of the intermediate portion as a boundary has been described, but the spiral elastic body 31 is not limited to the configuration having the bent portion 31 a. For example, as shown in fig. 22, the spiral elastic body 31 of the vibration isolator 3 may have a twisted portion 31d in the middle portion thereof, and a right wound portion 31b and a left wound portion 31c are provided with the twisted portion 31d as a boundary, and the twisted portion 31d may be twisted around the central axis of the wire rope so as to change the winding direction of the metal wire rope. Of course, the spiral elastic body 31 may be formed by only the right winding portion or the left winding portion without reversing the winding direction of the metal rope in the middle. That is, the spiral elastic body 31 may be formed of a cable wound in one direction.

In the above-described embodiment, the case where the holding bases (product trays) 51 and 53 that are separate members from the platform portion 2 are fixed to the platform portion 2 of the vibration-proof tray 1 has been described, but the platform portion of the vibration-proof tray may be integrally provided with a holding base for stacking glass plates. In this case, since the holding base is configured as a vibration-proof tray, only the laminated body portion of the glass plates except for the holding base becomes a load. In the case where the vibration-proof tray and the holding base are configured as separate members that can be separated from each other, one vibration-proof tray can be shared by a plurality of holding bases. Therefore, there is an advantage that the manufacturing cost of the tray becomes lower than the case where the vibration-proof tray and the holding base are integrated and cannot be separated from each other or the case where the separation is not assumed.

Description of the reference numerals

1 vibration-proof tray

2 platform part

3 antivibrator

31 helical elastic body

32. 33 holding device

34 rubber material

4 base part

5 goods

51. 53 holding table

52. 54 glass plate.

Claims

1. A vibration-proof pallet for conveying goods containing inorganic brittle materials, characterized in that,

the vibration-proof tray includes a cargo bed portion for receiving the cargo, a vibration isolator disposed on a lower surface of the cargo bed portion, and a base portion for holding the cargo bed portion via the vibration isolator,

the vibration isolator includes a spiral elastic body arranged such that a central axis thereof is oriented in a lateral direction, and a holder for holding the spiral elastic body.

2. Anti-vibration tray according to claim 1,

the spiral elastic body is a metal cable.

3. Anti-vibration tray according to claim 1,

the spiral elastic body is embedded in the rubber material.

4. Anti-vibration tray according to claim 2,

the spiral elastic body is embedded in the rubber material.

5. Anti-vibration tray according to any of claims 1 to 4,

the cargo bed portion has a rectangular shape in plan view, and the vibration isolators are arranged at least at four corners of the cargo bed portion,

the center axis of the spiral elastic body of the vibration isolator disposed at each of the four corners is inclined with respect to both adjacent sides of the shelf portion constituting the corner portion at which the vibration isolator is disposed.

6. Anti-vibration tray according to claim 5,

the center axis of the spiral elastic body of the vibration isolator disposed at each of the four corners is along a bisector of an angle formed by two adjacent sides of the shelf portion constituting the corner portion at which the vibration isolator is disposed.

7. Anti-vibration tray according to claim 5,

the center axis of the spiral elastic body of the vibration isolator disposed at each of the four corners is along a line orthogonal to a bisector of an angle formed by two adjacent sides of the shelf portion constituting the corner portion at which the vibration isolator is disposed.

8. Anti-vibration tray according to any of claims 1 to 4,

the inorganic brittle material is a glass material or a ceramic material.

9. A glass bundle package, characterized in that,

the glass bundle is obtained by placing, as the load, a laminate in which a plurality of glass plates are stacked in a vertical posture on the vibration-proof tray according to any one of claims 1 to 8.