JP2014024602A - Freight transportation pallet device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To greatly reduce necessary transportation costs of a freight transportation pallet device by exhibiting a stable anti-vibration function irrespective of a difference in weight or size of loaded cargoes.SOLUTION: An anti-vibration pallet P includes joint means J for making the side faces of a lower frame 11 and an upper frame 12 butt on each other and connecting them on the same plane. According to the size of an air cargo D to be loaded, the joint means adds lower frames and upper frames in units of one each of them to thereby construct a pallet assembly of a corresponding size. Anti-vibration means V includes a nonlinear compression coil spring 35 having nonlinear spring characteristics. A spring constant of the compression coil spring 35 is set so that a unique frequency can be constant even if the loaded weight of the air cargo varies within a predetermined weight range.

Description

  The present invention mounts cargo such as air cargo, sea cargo, railway cargo, and road cargo and loads them in the cargo compartment of transportation means such as aircraft, ships, trains, and trucks, and buffers vibrations and shocks received during transportation. The present invention relates to a cargo transportation pallet apparatus having a vibration isolation function.

  Among various types of cargo, for example, air cargo, when turbulent airflow occurs during air transportation and the aircraft shakes, it vibrates severely, or it is carried on a pallet dolly at the airport before departure or after arrival. The conventional pallet equipment for transporting air freight is made of rubber or coil, because it may vibrate severely due to the severe shaking that occurs and may break depending on air freight such as precision equipment sensitive to vibration and shock. It is equipped with anti-vibration means consisting of an elastic body such as a spring, and air cargo is mounted via the anti-vibration means, and the whole is covered with a lashing material such as a tie-down rope. Is loaded.

  However, in this type of pallet transport type, even if it is equipped with anti-vibration means, if the entire pallet device is strongly tightened and lashed together with the anti-vibration means, the anti-vibration means will not work and the anti-vibration function at the corner will work. There was a problem of disappearing.

  Therefore, the conventional cargo transportation pallet apparatus has a wooden box, etc. of a certain size on the anti-vibration pallet that carries air cargo so that the tightening load due to lashing does not reach the anti-vibration means when tightening with lashing material. The lashing box is covered and protected, and a tie-down rope or the like is hung around the lashing box for lashing (see Patent Document 1).

JP 2007-297056 A

  However, in a conventional cargo transportation pallet apparatus, for example, when a compression coil spring is used as an elastic body used for the vibration isolating means, the compression coil spring cushions (anti-vibration) when the air cargo to be mounted has a substantially constant weight. Because it is a linear coil spring, such as an equi-pitch coil spring, that exerts its effect, if the weight of the loaded air cargo is lighter than the specified weight, the anti-vibration function will not work. If the weight is not the prescribed weight, it is necessary to replace the anti-vibration means that has a constant spring compression coil spring with a spring constant that exhibits the anti-vibration effect according to the weight of the air cargo to be loaded. There is a problem that it is necessary to prepare a lot of anti-vibration means corresponding to the weight of air cargo.

  In addition, in the conventional cargo transportation pallet apparatus, the lashing box that covers the loaded air cargo is used in a large size with a fixed volume so that the loaded cargo of different sizes can be stored, while the airfare is In addition to the actual weight of the loaded cargo including packaging materials, the total volume is also taken into account. Based on the regulations of IATA (International Air Transport Association), the unit weight of Kg is calculated to calculate the actual weight. The higher rate of volumetric weight is applied. Therefore, in the past, even when transporting a relatively light and small air cargo with a weight of 500 kg, the lashing box has a relatively large common size box with a capacity weight of 2,000 kg with a margin. Therefore, there is a problem that the air fare rate is applied based on the heavier volumetric weight and that much air fare is wasted.

  Furthermore, with conventional pallet equipment for freight transportation, the size of air freight carried on anti-vibration pallets varies widely depending on the shipper requesting air freight transportation. Usually, it is necessary to prepare anti-vibration pallets of different sizes according to the size of the air freight that is requested for transportation. As a result, the number of anti-vibration pallets according to the size of the loaded cargo is enormous. There was also a problem that it was expensive.

  Therefore, in order to solve the above-described problem, the invention described in claim 1 is configured such that an aircraft such as an air cargo D is mounted as shown in an embodiment described below with reference to the drawings. In a cargo transportation pallet apparatus A having a vibration isolating function for loading vibrations and shocks received during transportation in a cargo compartment of a transportation means, a rectangular base plate B fixed to the floor surface of the cargo compartment, and the base A plurality of anti-vibration means V are erected as leg portions between a rectangular frame-like undercarriage 11 placed on the plate B and a rectangular frame-like upper carriage 12 on which cargo is placed. And a lashing material R for securing cargo loaded on the anti-vibration pallet P to the base plate B. The vibration means V has a non-linear spring characteristic. The compression coil spring 35 is provided, and the spring constant of the compression coil spring 35 is set so that the natural frequency is constant even when the cargo loading weight is displaced within a predetermined weight range. Is characterized in that the anti-vibration pallet P is hung directly around the loaded cargo and secured to the pedestal plate B.

  The invention according to claim 2 is the freight transportation pallet apparatus A according to claim 1, for example, as shown in the embodiment described below with reference to the drawings, the anti-vibration pallet P includes the undercarriage 11 And a joint means J for connecting the upper frame 12 on the same plane with their side surfaces abutted on each other, and the joint according to the size of the cargo mounted on the lower frame 11 and the upper frame 12 as a unit. The pallet assembly C having a corresponding size is assembled by adding the means J.

  According to a third aspect of the present invention, in the freight transport pallet apparatus A according to the first or second aspect, for example, as shown in an embodiment described below with reference to the drawings, the vibration isolation means V includes the nonlinear The viscoelastic sheet 40 is bonded to the outer periphery or inner periphery of the compression coil spring 35.

  In the freight transportation pallet apparatus according to claim 1 as well, the vibration-proof pallet and the lashing material are hung around the cargo and firmly lashed (clamped). Because it is a non-linear compression coil spring with a non-linear spring characteristic that can obtain a constant natural frequency regardless of the size of the loaded load, the magnitude of the tightening load can be maintained even when a load of about the tightening force of the lashing material is applied. The number of effective turns is reduced in response to the bending, and the coil portion of the low-weight belt with a large coil-to-coil pitch and a smaller spring constant can be bent to buffer the tightening load caused by lashing. . As a result, according to the first aspect of the present invention, since the lashing tightening force does not reach the vibration isolating means as in the prior art, the spring property is not lost. There is no need to cover a dedicated lashing box to protect the lashing's tightening force from reaching the anti-vibration means. As a result, a large amount of lashing boxes required for each lashing are not required, and the transportation cost can be significantly reduced.

  Moreover, according to the freight transportation pallet apparatus according to claim 1, it is not necessary to cover the cargo with a lashing box for lashing, and the lashing material is directly applied to the loaded cargo together with the anti-vibration pallet to the pedestal plate. Even if it is a relatively light and small cargo as in the past, lashing with a common size lashing box will unnecessarily increase the volume of the entire cargo and increase the fare. In this respect, the transportation cost can be drastically reduced.

  By the way, since the weight of the cargo loaded on the vibration isolating pallet is not constant, the load applied to the vibration isolating means also changes according to the weight of the cargo. However, in the freight transport pallet apparatus according to claim 1, even if the load applied to the vibration isolating means changes according to the load weight of the cargo, the compression coil spring of the vibration isolating means does not load the cargo within a predetermined weight range. Because it is a non-linear compression coil spring with non-linear spring characteristics that can obtain a constant natural frequency regardless of the magnitude of the load, the effective number of turns increases and decreases according to the size of the different mounting load, and the mounting load becomes heavy As a result, the spring constant is increased by reducing the effective number of windings due to adhesion between the coil wires, and the natural frequency does not change and remains constant. Accordingly, it is possible to exert a stable anti-vibration (buffer) effect by utilizing a spring. As a result, according to the first aspect of the present invention, even when the load applied to the vibration isolating means changes in accordance with the load weight of the cargo, the anti-vibration performance is adjusted according to the different load weight each time as in the prior art. Therefore, there is no need to replace the anti-vibration means such as an equi-pitch coil spring with a constant spring constant.Therefore, it is not necessary to prepare many anti-vibration means corresponding to the mounted weight, which greatly reduces the cost required for transportation equipment. You can also

  Conventionally, for example, when an extremely large impact is applied to the vibration isolating means due to the turbulent air flow and the aircraft shook violently during air transportation, if the vibration isolating means is, for example, a linear equal pitch coil spring, the large The lashing material may bend greatly according to the load and loosen the lashing material, and the loosening of the lashing may cause the cargo to swing and be damaged. However, in the pallet device for freight transportation according to claim 1, the compression coil spring of the vibration isolating means has a non-linear spring characteristic even if an extremely large load is applied to the vibration isolating means due to a severe impact during the transportation. Since it is a non-linear compression coil spring, the effective number of turns decreases corresponding to such a large load, but the coil portion of the heavy weight zone with a narrow pitch between the coil strands and a large spring constant has a small deflection, so By using a spring to cushion strong impact, loosening of lashing can be suppressed. Moreover, even if an extremely large load is applied to the anti-vibration means due to a severe impact during transportation as described above, the strong load does not prevent the coil elements from adhering to each other, and the spring does not work. By bending the coil part of the heavy weight zone with a narrow gap and a large spring constant, the spring can be used to buffer a strong impact. As a result, according to the first aspect of the present invention, it is necessary to take troublesome measures in the spring design so as not to cause a problem that the coil wires are all bonded to each other by a heavy load and the spring is not used. Can be eliminated.

  In the pallet device for freight transportation according to claim 2, the anti-vibration pallet is provided with joint means for connecting the lower base and the upper base on the same plane with the side surfaces abutted on each other, and each of the lower base and the upper base is used as a unit. Since the pallet assembly of the size corresponding to the loaded cargo is assembled by adding joint means according to the size of the loaded cargo, the size of the cargo loaded on the anti-vibration pallet varies depending on the shipper However, it is not necessary to prepare anti-vibration pallets of different sizes depending on the size of the loaded cargo. As a result, according to the second aspect of the present invention, the transportation equipment cost can be greatly reduced by the amount that it is not necessary to prepare a large number of size-specific anti-vibration pallets.

  In addition, according to the second aspect of the present invention, when a pallet assembly having a size corresponding to the loaded cargo is used by assembling with a joint means according to the size of the loaded cargo, When cargoes with different weights are loaded, tower loads distributed in different weights are applied to the vibration isolation pallets, that is, the vibration isolation means of each unit, but the compression coil springs of the vibration isolation means have nonlinear spring characteristics. Since it is a non-linear compression coil spring, even if the loading load applied to each anti-vibration means varies depending on the installation position, the elastic displacement amount of each non-linear compression coil spring can be made the same and the anti-vibration (buffer) action can be exhibited uniformly. it can.

  According to the third aspect of the present invention, since the vibration isolating means is formed of a damping coil spring in which a viscoelastic sheet is bonded to the compression coil spring, when the vibration is transmitted and the compression coil spring expands and contracts, the viscoelasticity is accordingly increased. The sheet bends and deforms between the individual coil wires, and the bending motion of this viscoelastic sheet suppresses the amplitude of the compression coil spring and attenuates free vibration (extension and contraction) quickly, thereby buffering the impact with as little displacement as possible. Accordingly, the vibration can be damped quickly and effectively to prevent the cargo from being damaged due to the vibration.

It is an assembly sectional view showing the pallet device for cargo transportation which is an example of the present invention in the lashing state. It is an assembly top view which shows a vibration proof pallet. (A) Assembling front view of anti-vibration pallet, (B) Assembling side view of anti-vibration pallet. It is a top view which shows the mount frame of a vibration proof pallet. (A) It is a front view of a base, (B) It is a side view of a base. It is a top view which shows the mount stand of a vibration proof pallet. (A) The front view of an upper stand, (B) It is a side view of an upper stand. (A) The top view which shows the 1st coupling of a joint means, (B) The front view of a 1st coupling. (A) Structure explanatory drawing which shows the 2nd joint of a joint means seeing from a plane, a front, and a side surface, (B) It is structure explanatory drawing which shows a 3rd joint seeing from a plane, a front surface, and a side surface. (A) The longitudinal cross-sectional view which shows a vibration isolating means, (B) The top view of a vibration isolating means. It is operation | movement explanatory drawing of a damping coil spring. (A) It is a graph which shows the spring load characteristic of an equal pitch compression coil spring, (B) It is a graph which shows the spring load characteristic of the unequal pitch compression coil spring of this invention. It is a characteristic explanatory view showing a spring state when different mounting loads are sequentially applied to the unequal pitch compression coil spring of the present invention. It is a fragmentary top view which shows the connection structure of the undercarriage of a pallet assembly. It is a partial front view which shows the connection structure of the mount stand of a pallet assembly. (A) The partial front view which shows the connection structure of a pallet assembly, (B) It is a partial side view. (A) A schematic plan view of a pallet assembly assembled by adding four anti-vibration pallets, and (B) a schematic front view. (A) It is a schematic plan view of the pallet assembly assembled by adding two anti-vibration pallets sideways, (B) It is a schematic front view. (A) It is a schematic plan view of a pallet assembly assembled by adding two anti-vibration pallets vertically, (B) a schematic front view, and (C) a schematic side view. In the cargo transportation pallet apparatus which is another example of this invention, it is a partial top view which shows the connection structure of a pallet assembly. It is a partial front view which shows the connection structure of the pallet assembly of another example. It is a top view which shows the mount frame of the vibration proof pallet of another example. (A) FIG. 22 is a sectional view taken along line XX in FIG. 22, (B) is a side view showing a mounting hole of the first connector, and (C) is a sectional view taken along line YY in FIG. It is a top view which shows the mount stand of a vibration proof pallet. (A) The top view which shows the 1st coupling tool of the joint means of another example, (B) The front view which shows the clamping member of a 1st coupling tool. (A) The top view which shows the 2nd coupling tool of a joint means, (B) The front view which shows the insertion member of a 2nd coupling tool. It is an assembly top view which shows another anti-vibration pallet. It is an assembly front view of the vibration isolating pallet. It is a schematic top view explaining the connection position of the undercarriage which adjoins an anti-vibration pallet. It is a schematic plan view explaining the connection position of the upper stand which adjoins a vibration proof pallet. It is a partial enlarged plan view which shows the structure of the connection position of the undercarriage which adjoins a vibration proof pallet. It is a partial enlarged plan view which shows the structure of the connection position of the upper stand which adjoins a vibration proof pallet.

  Hereinafter, embodiments for carrying out the present invention will be described in detail with reference to the drawings.

  FIG. 1 shows a cargo transportation pallet apparatus as an example of the present invention in a rushing state. The cargo transportation pallet apparatus A in the illustrated example is a suitable means for securing the air cargo D as cargo loaded with different weight and volume, and loading and transporting it in the cargo compartment of the aircraft as the transportation means, Pedestal plate B fixed to the floor of the cargo compartment, anti-vibration pallet P mounted on pedestal plate B and carrying air cargo, and air cargo D on anti-vibration pallet P lashing to pedestal plate B A lashing material R is provided.

  The pedestal plate B is a rectangular flat pallet of a predetermined size, for example, 96 inches, which is determined according to the cargo compartment of the aircraft, and is made of an aluminum plate and an aluminum frame material that borders it. A plurality of hooking rings 10 to be hung are erected and a number of hooking grooves for hooking hooks for hooking provided on a net (not shown) are cut.

  As shown in FIGS. 2 and 3, the anti-vibration pallet P includes a lower base 11 that is placed on and connected to the base plate B, an upper base 12 that carries the air cargo D, and the lower base 11 and the upper base 12. And a vibration isolation means V that elastically supports the upper frame 12 as legs, and joint means J for connecting on the same plane in units of the lower frame 11 and the upper frame 12 as a unit.

  The undercarriage 11 is an outside of a horizontally long rectangular shape composed of parallel vertical frame members 14 and 15 opposed in the left and right length direction in FIG. 4 and parallel horizontal frame members 19 and 20 opposed in the upper and lower short width directions. The frame part a and the reinforcing frame part b formed by crossing the two vertical and horizontal reinforcing frame members 16 and 17 in a cross shape in the outer frame part a are assembled in a lattice shape as a whole. The vertical frame members 14 and 15 and the horizontal frame members 19 and 20 are provided with a groove-shaped frame obtained by bending an aluminum plate into a substantially U-shaped cross section. Use. In the outer frame portion a, the vertical frame members 14 and 15 are assembled with the flange portions 14a and 15a facing each other and the web portions 14b and 15b standing up and bolted to the web portions 14b and 15b, as shown in FIG. The horizontal frame members 19 and 20 are provided with the web portions 19b and 20b with the flange portions 19a and 20a facing upward, as shown in FIGS. 4 and 5B. A plurality of connection holes n... For passing bolts are provided on the outer sides in the width direction of the flange portions 19a and 20a. As such, the lower base 11 has connection holes m in the web portions 14b and 15b of the vertical frame members 14 and 15 forming the side surfaces of the outer frame portion a and the flange portions 19a and 20a of the horizontal frame members 19 and 20, respectively. -N is provided as the joint means J.

  The upper base 12 is formed by a horizontally long rectangular outside made up of parallel vertical frame members 24 and 25 opposed to the left and right length directions in FIG. 6 and parallel horizontal frame materials 29 and 30 opposed to the upper and lower short width directions. The frame portion x and the reinforcement frame portion y formed by orthogonally reinforcing two reinforcing frame members 26, 26 and 27 in the vertical direction and laterally in the outer frame portion a are assembled in a lattice shape. The vertical frame members 24 and 25, the horizontal frame members 29 and 30 and the reinforcing frame member 27 are made of aluminum square tubes having a flat cross section, and the reinforcing frame members 26 and 26 are made of aluminum corners having a cross sectional mouth shape. Use a tube. In the outer frame portion x, the vertical frame members 24 and 25, the horizontal frame members 29 and 30 and the reinforcing frame member 27 are laid sideways, and the height direction of the wide flat surface portions 24a and 25a, 29a and 30a, 27a facing each other. It is assembled so that the upper surface side is formed on the same plane as the cargo placement surface, and is assembled into a slightly smaller rectangle that is horizontally long and shorter in length and width than the base 11. As shown in FIGS. 6 and 7, the outer frame portion x has narrow side portions 24b and 25b, 29b and 30b facing each other in the width direction of the vertical frame materials 24 and 25 and the horizontal frame materials 29 and 30, respectively. Connection holes p, q, r, and s for passing bolts are provided at both ends on the outside.

  As described above, the upper base 12 includes connection holes p, q, r, and s as joint means J on the side surfaces 24b, 25b, 29b, and 30b of the outer frame portion x. The joint means J is a connecting tool 45 that fills a gap generated between the upper bases 12 when the upper bases 12 that are smaller than the lower base 11 are connected to each other on the assembly of the connected lower bases 11 (FIGS. 8 and 8). 9). The connection tool 45 includes a first joint 50 for connecting four units, a second joint 51 for connecting two vertical units, and a third joint 52 for connecting two horizontal units, both of which are made of an aluminum plate and have the same width. It is assembled using a groove-shaped frame with a short cross-section and a connecting hole t is formed in each of the opposing flange portions f. The first joint 50 is formed by setting a groove-shaped frame in a cross shape. The second joint 51 for connecting two vertical units is formed slightly longer than the third joint 52 for connecting two horizontal units.

  As shown in FIG. 10, each vibration isolation means V included in the vibration isolation pallet P includes a compression coil spring 35 and a pair of upper and lower rectangular fixing steel plates 31 that fix the compression coil spring 35 to the lower frame 11 and the upper frame 12. 32 and a pair of upper and lower spring attachments 33 and 34 for attaching the compression coil spring 35 to the fixing steel plates 31 and 32.

  The compression coil spring 35 is an unequal pitch compression coil spring having non-linear spring characteristics, and is formed by adhering a viscoelastic sheet 40 to the outer periphery. The viscoelastic sheet 40 is formed by forming a viscoelastic body made of, for example, an acrylic resin into a sheet shape having a substantially uniform thickness and longer than the free length of the compression coil spring 35. The viscoelastic sheet 40 is self-adhesive and is pressure-bonded to the compression coil spring 35 so as to form a bent portion 40a that bends into the gap d between adjacent coils. Therefore, according to the vibration isolating means V, for example, when the compression coil spring 35 has a damping ratio of about 0.001, the damping ratio is improved to about 0.3 to 0.4, and the compression coil spring 35 is expanded and contracted by being placed in a vibration system. Then, as shown in FIG. 11, the viscoelastic sheet 40 operates so as to bend and deform between the individual coil wires, and the dynamic spring constant of the viscoelastic sheet 40 can be reduced by this operation. As a result, the vibration isolation by the compression coil spring 35 and the damping force of the viscoelastic sheet 40 quickly attenuate the free vibration (extension / contraction) of the compression coil spring 35, and the natural frequency and resonance magnification of the vibration system can be kept low. It has a structure. The vibration isolation means V can also be formed of an elastic body in which the viscoelastic sheet 40 is bonded to the inner periphery of the compression coil spring 35.

  As shown in FIG. 10, the spring fixtures 33 and 34 are configured to bond a plurality of spring pressing pieces 37 radially on the disc 36, and to connect the distal end portion 37 a of the spring pressing piece 37 in the radial direction from the peripheral edge of the disc 36. It protrudes outward. Therefore, the vibration isolating means V connects the spring mounting members 33 and 34 to the compression coil in a state in which the distal end portion 37a of the spring pressing piece 37 is inserted between the coil portion 35a at both ends of the compression coil spring 35 and the coil portion 35b adjacent thereto. While fitting the both ends of the spring 35 at the both ends, the bolt holes 38 are aligned with the disc 36 and the fixing steel plates 31 and 32 are overlaid, and then tightened with flat head bolts and nuts to fix the coil portions 35a at both ends to the fixing steel plates 31 and 32. 32 and the spring pressing piece 37, and the compression coil spring 35 is fixed to the fixing steel plates 31 and 32 and assembled.

  2 and 3, the anti-vibration pallet P fixes the steel plate 32 for fixing the anti-vibration means V to the both ends of the web portions 19b and 20b of the horizontal frame members 19 and 20 of the undercarriage 11 with bolts. On the other hand, the fixing steel plate 32 is fixed with bolts to both ends of the bottom plane portions 29a and 30a of the horizontal frame members 29 and 30 of the upper frame 12, and the vibration isolation means V is provided at the four corners between the lower frame 11 and the upper frame 12. As a leg part, the both bases 11 and 12 are connected up and down by vibration isolation means V to support the upper base 12 elastically, and movably connected to the lower base 11 in a three-dimensional direction. It becomes.

  FIG. 12 shows a comparison of spring characteristics in relation to the load and deflection amount of compression coil springs of equal pitch and unequal pitch. Here, one of the features of the illustrated pallet apparatus A of the present invention is that the anti-vibration means V of the anti-vibration pallet P has an inequality of non-linear springs having the non-linear spring characteristics shown in FIG. The point is that a pitch compression coil spring is used. As shown in FIG. 12A, when a linear spring having a linear spring characteristic, for example, an equal pitch compression coil spring, is used as a vibration isolating means, the air cargo to be mounted is always specified and the mounting load W is constant. Certainly, it is possible to make the anti-vibration performance work for the fixed load. However, when the weight (mounting load) W of the loaded cargo changes without specifying the linear pitch compression coil of the linear spring, the natural frequency fn fluctuates as calculated from Equation 1 below. When the load is 50% of the predetermined load, the natural frequency is √2 times, and when it is 25%, the natural vibration frequency is doubled and the vibration isolation performance is lowered.

  If it does so, even if the mounting load W displaces, if the natural frequency fn is constant, the vibration isolation performance will not deteriorate. Therefore, the present invention provides a spring in which the spring constant K changes in proportion to the mounting load W in Formula 1 above, that is, when the mounting load is applied, the effective number of turns acting as a spring changes and exhibits non-linear spring characteristics. A non-linear spring is selected as the vibration isolating means, and in the example shown in the figure, an unequal pitch compression coil spring 35 is selected and used as the vibration isolating means V.

  Due to the non-linear spring characteristics possessed by the unequal pitch compression coil spring 35, when the mounting load W becomes heavier, adhesion occurs between the coil wires, and the effective number of turns decreases, thereby increasing the spring constant. Therefore, in the present invention, the spring constant of the non-linear compression coil spring is set so that the natural frequency remains constant even if the loaded weight of the air cargo is displaced within a predetermined weight range. In this case, the pitches of the unequal pitch compression coil springs 35 are determined using the following formula 2 so that K / W in the above formula 1 becomes constant over a considerably wide range of the mounting load W.

  Therefore, in the illustrated example, the unequal pitch compression coil spring 35 is a coil having a free state length (free length) of, for example, 67.1 mm in accordance with the above formula 2, as shown in FIG. Each pitch (interval) d between the coil wires is determined, and the spring constant K is set so that the natural frequency fn is constant even if the loaded weight (load) of the air cargo is displaced within a predetermined weight range. Then, a coil portion of a low weight band in which a coil constant between the coil wires is set to a large value corresponding to the applied mounting weight (load) W and a small spring constant is set, and a coil constant between the coil wires is narrowed. Is formed in the height direction.

  In the illustrated example, the spring state when a load of 58 kg, 87 kg, 116 kg, 174 kg, 348 kg, for example, is applied to each non-uniform pitch compression coil spring 35 is tested, and the results are shown in Table 1 and FIG. 13 (B) to (F). As shown in Table 1 and FIGS. 13 (B) to (F), when the mounting weight (load) W increases to 58 kg, 87 kg, 116 kg, 174 kg, and 348 kg, adhesion occurs between the coil wires, and the effective number of turns n Decreases the spring constant K. Accordingly, the unequal pitch compression coil spring 35 changes the spring constant K according to the mounting weight W, so that the mounting weight W is within a predetermined weight range of 58 kg to 348 kg regardless of the mounting weight W. Both natural frequencies show a constant value of 6.30 Hz, even if the lightest weight is 58 kg, it is still deflected even when the weight is reduced to 7.70 Hz and 1/3 (33%) of the standard (100%) 174 kg. It is elastic enough to exhibit sufficient vibration isolation performance.

  In the illustrated example, an unequal pitch compression coil spring is used as the nonlinear compression coil spring. However, in the present invention, a conical coil spring or a double coil spring can be used as long as the compression coil spring has nonlinear characteristics. .

  Therefore, as shown in FIG. 1, the cargo transport pallet apparatus A composed of the above components is mounted with the vibration proof pallet P on the pedestal plate B, and the air cargo D is mounted on the cargo placement surface of the upper platform 12. Then, hang the lashing belt R1 of the lashing material R together with the gantry 12 and tighten the lashing pallet P with the tie-down rope r2 of the lashing material R around the air cargo D. The hook 19 is hooked on the hook ring 10 and secured to the base plate B. Then, although not shown in the figure, the net is finally hung on the whole, and the hook for hooking the net is hung on the hooking groove of the base plate B, assembled, and hung on the net.

  Now, for example, in an airport, the cargo pallet apparatus A, for example, secures the air cargo D with the lashing material R and hangs it on the net, and then carries it on the pallet dolly to the side of the aircraft, for example, a cargo loader, etc. Then, the cargo is lifted up to the cargo compartment and carried into a predetermined loading position. The retaining ring 10 of the base plate B is hung on a fastening device provided in the cargo compartment and fixed to the floor surface, and then transported by air.

  Therefore, in the cargo transport pallet apparatus A, the lashing pallet P and the tie-down rope r2 of the lashing material R are hung around the air cargo D together with the anti-vibration pallet P, and the compression coil spring 35 of the anti-vibration means V is predetermined. Since it is a non-uniform pitch compression coil spring with non-linear spring characteristics that can obtain a constant natural frequency regardless of the load of air cargo in the weight range, a load of about the tightening force by the lashing material R is applied. However, the effective number of turns decreases corresponding to the tightening load, and the spring is used by lashing by bending at the coil part of the low weight zone with a large pitch between coil wires and a smaller spring constant. The tightening load can be buffered. As a result, in the pallet apparatus A for cargo transportation, the lashing tightening force does not reach the vibration isolation means V and the spring property is not lost as in the conventional case. There is no need to cover the lashing material R together with the anti-vibration pallet P directly on the base plate B without the need to protect the lashing from reaching the anti-vibration means V. As a result, a large amount of tying boxes required for each lashing are not required, and the transportation cost can be significantly reduced.

  Moreover, in the cargo transport pallet apparatus A, it is not necessary to cover the air cargo with a lashing box and lashing, and the anti-shake pallet P is hung directly on the loaded cargo and secured to the base plate B. Therefore, even if it is a relatively light and small cargo as in the past, lashing with a uniform size lashing box will unnecessarily increase the volume of the entire cargo and increase the air fare. In this respect, the transportation cost can be drastically reduced.

  In the cargo transport pallet apparatus A, the anti-vibration pallet P is connected to the lower base 11 and the upper base 12 up and down by the anti-vibration means V, and the upper base 12 is elastically supported. Because it is assembled in a working state, even if vibration is transmitted due to an impact during transportation, vibration from the aircraft or pallet dolly is attenuated by the vibration isolation function by the vibration isolation means V, The transmission to the air cargo D is suppressed to prevent the air cargo D from being damaged due to vibration. Moreover, in the pallet apparatus A for cargo transportation, since the vibration isolating means V is formed by a damping coil spring in which the viscoelastic sheet 40 is bonded to the compression coil spring 35, as shown in FIG. When 35 expands and contracts, the viscoelastic sheet 40 is bent and deformed between the individual coil wires, and the bending operation of the viscoelastic sheet 40 suppresses the amplitude of the compression coil spring 35 to make free vibration (extension and contraction) faster. Attenuating and shock can be buffered with as little displacement as possible, and the vibration can be quickly and effectively attenuated to prevent the air cargo D from being damaged due to the vibration. .

  By the way, since the weight of the air cargo mounted on the anti-vibration pallet P is not constant, the load applied to the anti-vibration means V also changes according to the weight of the air cargo. However, even if the load applied to the vibration isolating means V changes according to the load weight of the air cargo, the pallet apparatus A for cargo transportation has the compression coil spring 35 of the vibration isolating means V having a load load within a predetermined weight range. Because it is a non-uniform pitch compression coil spring with non-linear spring characteristics that can obtain a constant natural frequency regardless of the size, the effective number of turns increases and decreases according to the size of different loading loads, and the loading load of air cargo When the load becomes heavier, adhesion occurs between the coil wires and the effective number of turns decreases, so the spring constant increases, so the natural frequency does not change and remains constant. However, a stable anti-vibration (buffer) effect can be exerted by utilizing the spring accordingly. As a result, in the pallet apparatus A for cargo transportation, even when the load applied to the vibration isolating means V changes in accordance with the loaded weight of the air cargo, the anti-vibration performance is adjusted according to the different loaded weight each time as before. There is no need to replace the anti-vibration means such as an equi-pitch coil spring with a constant spring constant, so there is no need to prepare a large number of anti-vibration means corresponding to the mounted weight, which can reduce the cost required for transportation equipment. it can.

  Conventionally, during air transportation, for example, when an extremely large impact is applied to the anti-vibration means due to turbulent airflow and the aircraft shaking vigorously, the large anti-vibration means is, for example, a linear equi-pitch coil spring. The lashing material may be bent greatly according to the load to loosen the lashing material, and the air cargo D may swing and be damaged due to the loosening of the lashing. However, the freight transport pallet apparatus A has a non-linear spring characteristic in which the compression coil spring 35 of the vibration isolating means V has a non-linear spring characteristic even if an extremely large load is applied to the vibration isolating means V due to a severe impact during transportation. Since it consists of an equi-pitch coil spring, the effective number of turns decreases corresponding to such a large load, but it is sufficient because the coil portion of the heavy belt with a narrow pitch between the coil wires and a large spring constant has a small deflection. By using a spring to cushion strong impact, loosening of lashing can be suppressed. Moreover, even if an extremely large load is applied to the vibration isolating means V due to a severe impact during transportation, the strong load does not cause the coil wires to adhere to each other and the spring does not work. By bending the coil portion of the heavy weight zone with a narrow line pitch and a large spring constant, the spring can be used to buffer a strong impact. As a result, it is possible to eliminate the need for bothersome troublesome spring design measures so as not to cause a problem that the coil wires are all bonded by a strong load and the springs do not work.

  In the cargo transportation pallet apparatus A in the illustrated example, there is a difference in the size of the air cargo D that is carried on the anti-vibration pallet P depending on the shipper. In that case, FIG. 14, FIG. 15, FIG. As shown in FIG. 4, the pallet assembly C having a size corresponding to the loaded cargo is assembled by adding the joint means J according to the size of the air cargo D to be mounted, with each of the lower rack 11 and the upper rack 12 as a unit. .

  Therefore, when the pallet assembly C is assembled to a size that is placed on one surface of a 96-inch pedestal plate B according to the size of a large air cargo, for example, the lower base 11 and the upper base of the anti-vibration pallet P 12 are added by four joint means J each. As shown in FIG. 14, the lower base 11 is adjacent to the vertical base 11 adjacent to the left and right in the figure, and the side surfaces of the vertical frame members 15 and 14, that is, the web portions 15 b and 14 b are abutted to the connection hole m. The lower base 11 adjacent to the upper and lower sides in the figure is connected to the side holes of the horizontal frame members 20 and 19, that is, the flange portions 20a and 19a, and connected to the connection holes n through the bolts. The four undercarriages 11 are connected in a rectangular shape on the same plane.

  On the other hand, as shown in FIGS. 15 and 16, the upper base 12 is connected to the cross groove-shaped gap 60 formed between the upper bases 12 and 12 on the assembly of the four lower bases 11. The tool 45 is fitted and connected. That is, the upper base 12 is configured such that the first joint 50 of the connector 45 is fitted into the center intersection 60a of the gap 60, and the upper base 12 adjacent to the left and right in the figure and the side surfaces of the vertical frame members 25 and 24, that is, One side of the flange portions 25a, 24a is abutted on both sides of the vertical straight portion 50a of the first joint 50, and is screwed into the connection holes p, q, t through bolts. The upper frame 12 adjacent in the vertical direction in the figure is the connection hole r by abutting the side surfaces of the horizontal frame members 30 and 29, that is, one side of the flange portions 30a and 29a with the horizontal straight portion 50b of the first joint 50 interposed therebetween. Threaded through bolts to s · t, and the second joint 51 is fitted into the left and right end portions 60b of the gap 60 in the drawing, and the side surfaces of the horizontal frame members 30 and 29, that is, the other sides of the flange portions 30a and 29a are second. The joints 51 are put together and screwed into the connection holes r · s · t with bolts, and the third joints 52 are fitted into the upper and lower end portions 60c of the gap 60 in the drawing, that is, the side surfaces of the vertical frame members 25 and 24, that is, The other sides of the flange portions 25a and 24a are brought into contact with each other with the third joint 52 interposed therebetween, and screwed into the connection holes r · s · t through bolts. Accordingly, the four undercarriages 11 are assembled in a rectangular shape on the same plane by the joint means J and connected to each other. The upper platform 12 is assembled in a rectangular shape on the same plane and connected, and four anti-vibration pallets P are added according to the size of a large (96 inch) air cargo to assemble and use a large pallet assembly C. .

  Accordingly, the cargo transport pallet apparatus A has, for example, two anti-vibration pallets P according to the size of the air cargo to be mounted, and the upper base 12 is the second joint 51 of the joint means J as shown in FIG. It is also possible to connect the two anti-vibration pallets P side by side and assemble the medium-sized pallet assembly C for use. Further, for example, as shown in FIG. 19, two vibration isolating pallets P are connected to the upper frame 12 using a third joint 52 of the joint means J, and two anti-vibration pallets P are vertically connected to form a medium size. The pallet assembly C can also be assembled and used.

  As described above, in the cargo transport pallet apparatus A, the anti-vibration pallet P includes the joint means J for connecting the lower base 11 and the upper base 12 on the same plane by abutting the side surfaces of the lower base 11 and the upper base 12. Air cargo to be transported on anti-vibration pallet P because it is configured to assemble pallet assembly C of a size corresponding to the loaded cargo by adding joint means J according to the size of air cargo to be loaded as a unit. Depending on the shipper, there are various sizes, but it is necessary to prepare anti-vibration pallets with different sizes depending on the size of the loaded cargo. As a result, the freight transportation pallet apparatus A can greatly reduce the cost of transportation equipment as much as it is not necessary to prepare a large number of vibration-proof pallets according to size.

  On the other hand, in the pallet apparatus A for cargo transportation, when a pallet assembly C of a size corresponding to the loaded cargo is used by assembling with the joint means J according to the size of the loaded air cargo, When air cargoes having different weights are mounted on each other, tower loads distributed in different weights are applied to the vibration isolation pallets, that is, the vibration isolation means V of each unit, but the compression coil springs 35 of the vibration isolation means V are nonlinear. Since it is an unequal pitch coil spring having spring characteristics, even if the mounting load applied to each vibration isolating means V differs depending on the coil installation position, the amount of elastic displacement of each nonlinear compression coil spring 35 is made the same to prevent vibration (buffer). The effect can be exhibited uniformly.

  As described above, in the cargo transportation pallet apparatus A, the vibration isolation pallet P is added by the joint means J in accordance with the size of the air cargo to be mounted, and the pallet assembly C having a size corresponding to the mounted cargo is assembled and used. However, the joint means J can be configured as shown in FIGS. 20 to 32 instead of the configuration in the above-described embodiment.

  In the embodiment described above, the joint means J is provided between the upper bases 12 when connecting the upper bases 12 that are slightly smaller in length and width than the lower bases 11 on the assembly of the lower bases 11. The connection tool 45 was fitted into the gap formed and connected. However, according to the present invention, as in the other embodiments described below, the lower carrier 11 and the upper carrier 12 having the same length and width are connected by the joint means J, and the anti-vibration pallet P is mounted on the air cargo. The pallet assembly C of a size corresponding to the loaded cargo can be assembled by adding to the size of the pallet.

  For this reason, as shown in FIGS. 22 and 23A, the undercarriage 11 has a fork pocket (fork) for carrying the vibration isolating pallet P alone on both ends of the vertical frame members 14 and 15 and the reinforcing frame member 16. Fork pocket 56 for carrying a pallet assembly C to which four anti-vibration pallets P are added, and a horizontal frame member between the fork pocket 56 and the fork pocket 54 As shown in FIG. 23 (B), rectangular box-shaped component storage pockets 57 having entrances and exits are provided on the sides 19 and 20 on the same side as the fork pockets 54 and 56. As shown in FIG. 23C, the vertical frame member 14 has bolts at both ends of the standing plate portion 59 that faces the standing plate portion 58 that forms the side surface of the outer frame portion a and is adjacent to the component storage pocket 57. Mounting holes 60 and 60 are provided as joint means J.

  As shown in FIG. 24, the upper frame 12 has a bottomed cylindrical component storage pocket 61 having openings at the upper plane portions 24a, 29a, and 30a at positions adjacent to the four corners of the outer frame portion x. Are provided as joint means J. As shown in FIG. 20, airline rails 69 are laid on the four sides of the flat portions 24a, 25a, 29a, 30a in order to fix the cargo with ropes or the like.

  The joint means J of the other example shown in the figure includes a first coupling 65 that connects the lower platforms 11 and a second coupling that connects the upper platforms 12 on the assembly of the lower platform 11 connected by the first coupling 65. A tool 70 is provided.

  As shown in FIG. 25, the first connecting tool 65 for the undercarriage has a structure in which the other end of the chain 64 in which a bolt 63a and a nut 63b are connected to one end is fixed and connected to a bifurcated sandwiching member 62. . The sandwiching member 62 has a bifurcated shape in which a pair of elongated sandwiching plate pieces 62b are erected in parallel on a base plate 62a. In the other example shown in the figure, when the first connector 65 is not used, the first connector 65 is attached to the vertical plate member 59 of the vertical frame member 14 by tightening the bolt 63a with the nut 63b through the mounting hole 60 of the lower base 11 as shown in FIG. On the other hand, as shown in FIG. 23B, the sandwiching member 62 is inserted into the component storage pocket 57 from the doorway and stored.

  As shown in FIG. 26, the second connection tool 70 for the upper base has a structure in which the other end of the chain 72 having the connection ring 71 connected to one end is fixed and connected to a bifurcated insertion member 73. The insertion member 73 has a bifurcated shape in which a pair of rectangular insertion plate pieces 73b are erected in parallel on a base plate 73a. In the illustrated other example, when the second connector 70 is not used, the fixing steel plate 31 is passed through the fixing bolt 66 of the vibration isolating means V as shown in FIG. On the other hand, as shown in FIG. 28, the insertion member 73 is inserted into the component storage pocket 61 from the doorway and stored.

  Accordingly, in the other examples shown in the drawings, when not in use, the first base 65 and the second base 70 for the upper base are provided on the lower base 11 and the upper base 12 respectively. Sometimes these connectors can be prepared quickly and accurately, and can be safely stored without being lost when not in use.

  When the cargo transport pallet apparatus A of the other example shown in the figure is assembled to a size that mounts the anti-vibration pallet P on one surface of, for example, a 96-inch pedestal plate B according to the size of the air cargo to be mounted. 29 and FIG. 30, the lower base 11 and the upper base 12 of the anti-vibration pallet P are respectively connected by the first connecting member 65 and the second connecting member 70 of the four joint means J to correspond to the loaded cargo. A pallet assembly C having a size is assembled, and two of the four pallet assemblies C include a vibration isolating pallet P in which the first connecting device 65 and the second connecting device 70 are respectively combined with a lower base 11 ′ and an upper base 12 ′. The same lower base 11 'and upper base 12' equipped with this connecting tool and the same non-equipment lower base 11 'and upper base 12' are assembled diagonally.

  Therefore, as shown in FIG. 29, the lower base 11 is adjacent to the vertical bases 11 adjacent to each other in the left and right directions in the figure by contacting the standing plate portions 58 and 79 that form the side surfaces of the vertical frame members 14 and 15. While it connects using the 1 connector 65, it does not connect with the base 11 adjacent to the horizontal direction of the upper and lower sides in the figure. The connection of the undercarriage 11 is made by combining the one equipped with the first connector 65 and the one not equipped, and the two connected units are not connected.

  When connecting the vertically adjacent bases 11 using the first connector 65, the sandwiching member 62 is taken out from the component storage pocket 57, and as shown in FIG. 58 and 79 are inserted and connected.

  On the other hand, on the assembly of the four lower bases 11, the upper base 12 abuts the upper base 12 adjacent to the left and right in the vertical direction in FIG. 30 and the side surfaces 24b and 25b of the vertical frame members 24 and 25, The upper frame 12 adjacent in the vertical direction in the figure is connected using the second connector 70 after the side surfaces 29b and 30b of the horizontal frame members 29 and 30 are abutted.

  When connecting the four upper bases 12 using the second connecting tool 70, the insertion member 73 is taken out from the component storage pocket 61 of the upper base 12 equipped with the second connecting tool 70, and then shown in FIG. As described above, the bifurcated insertion plate pieces 73b and 73b are inserted into the adjacent component storage pockets 61 and 61 at eight locations, respectively, so that the side portions 24, 25, 29, and 30 are sandwiched.

  Therefore, in the cargo transport pallet apparatus A of the other example shown in the figure, for example, the four undercarriages 11 are assembled in a rectangular shape on the same plane by the joint means J and connected on the assembly of the undercarriage 11. Each of the four gantry bases 12 connected up and down by the vibration isolating means V is connected in a rectangular shape on the same plane, and the four vibration isolating pallets P according to the size of the large (96 inch) air cargo are connected. The large pallet assembly C can be assembled and used.

  Moreover, in the cargo transport pallet apparatus A of the other example shown in the figure, when a plurality of lower mounts 11 and upper mounts 12 are added, the upper and lower mounts are preliminarily mounted without fixing them using bolts, nuts and the like. The sandwiching member 62 of the first connector 65 and the insert member 73 of the second connector 70 are respectively taken out from the component storage pockets 57 and 61, and the sandwiching member 62 sandwiches the upright plate portions 58 and 79 with bifurcated sandwiching pieces 62b. By simply inserting the insertion member 73 into the adjacent component storage pockets 61 and 61 and sandwiching the side surface portions 24, 25, 29, and 30, the insertion member 73 can be easily connected without trouble.

  By the way, in the above-described illustrated embodiment, the air cargo D is mounted as a cargo on the anti-vibration pallet P, and the air cargo D is loaded into the cargo compartment of the aircraft as the transportation means, and the vibration and impact received during the transportation. A cargo transport pallet apparatus A for buffering is shown. However, in the freight transport pallet apparatus of the present invention, the freight transport means is not limited to an aircraft, and includes marine transport ships, rail transport trains, road transport trucks, and the like, and is therefore mounted on a vibration-proof pallet. The freight is not limited to air freight and widely includes sea freight, rail freight and road freight.

A Cargo pallet equipment B Pedestal plate C Pallet assembly D Air cargo J Joint means K Spring constant P Anti-vibration pallet R Lashing material V Anti-vibration means W Mounted weight (load)
fn natural frequency 11 lower frame 12 upper frame 35 compression coil spring 40 viscoelastic sheet

Claims (3)

In the cargo pallet system equipped with a vibration-proof function to load the cargo and load it into the cargo compartment of the means of transportation and buffer the vibrations and shocks received during transportation.
A plurality of anti-vibration means are provided between the rectangular pedestal plate that is fixed to the floor of the cargo compartment, the rectangular frame-shaped lower platform that is placed on the pedestal plate, and the rectangular frame-shaped upper platform that is loaded with cargo. And a vibration isolating pallet that elastically supports the upper gantry by connecting both gantry up and down by the vibration isolating means, and a lashing that secures cargo loaded on the vibration isolating pallet to the pedestal plate With materials,
The anti-vibration means includes a non-linear compression coil spring having non-linear spring characteristics, and the natural frequency of the compression constant of the compression coil spring is constant even if the loaded weight of the cargo is displaced within a predetermined weight range. Set
A pallet apparatus for freight transportation, wherein the lashing material is hung directly around the loaded cargo together with the anti-vibration pallet and secured to the pedestal plate.   The anti-vibration pallet includes joint means for connecting the lower frame and the upper frame on the same plane with their side surfaces abutted on each other, and the size of the cargo mounted on the lower frame and the upper frame as a unit The pallet apparatus for freight transportation according to claim 1, wherein a pallet assembly of a corresponding size is assembled by adding the joint means according to the above.   The pallet device for freight transportation according to claim 1 or 2, wherein the vibration isolation means is formed by adhering a viscoelastic sheet to an outer periphery or an inner periphery of the nonlinear compression coil spring.

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