JP2936328B1 - Low vibration container - Google Patents

Abstract

A low-vibration container mounted and transported on a vehicle is provided. An outer frame member (2) is mounted on a truck (4a) of a vehicle (4), and an inner box (1) for holding and loading an inner box (1) for storing a load is provided. The inner box is supported by the upper spring member 1a and the stroke adjuster 1b in series, and a plurality of vibration insulators 1d are arranged between the lower part of the inner box and the lower part of the outer frame member, to thereby reduce the total weight of the inner box. The main weight is supported by the plurality of upper spring members, the remaining total lower load is supported by the plurality of vibration insulators, a pressure load signal of the pressure sensor 1g built in the vibration insulator is input, and an output signal is output. And a controller 3 for controlling the stroke of the stroke adjuster.
A low-vibration container characterized by having a structure capable of getting on and off the vehicle is secured.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a chicken and egg transported on a cargo truck such as a large truck or a railway car.
The present invention relates to a low-vibration container capable of transporting a load sensitive to vibration, such as fresh food products such as beer, milk and wine, liquid products, or precision equipment.

[0002]

2. Description of the Related Art Vibration isolation measures for a prior art container include vibration reduction of a vehicle drive mechanism such as an air suspension mechanism and an active suspension mechanism, and low vibration of an engine and a power transmission mechanism. Trucks and vehicles with low volume are used, and the vibration of the container itself is hardly reduced. In some fields, flexible cushioning is provided around the container or around the truck to transmit the vibration to the container. There were only some cases of relaxation.

[0003]

As a countermeasure against vibration of the prior art container, the vibration of the container itself is hardly reduced, and in some fields, a flexible cushioning material is provided around the container or on a truck. Therefore, it is not sufficient to reduce the vibration of fresh food, liquid products, or precision equipment stored in the container. For example, in the case of chicken eggs, which is a representative material of fresh food,
It has been reported that the deterioration of the freshness inside the eggs becomes extremely large by transportation for about 10 hours, and there is a problem that the quality of liquid foods such as beer, wine, milk and the like is deteriorated.

[0004]

In order to solve the above-mentioned problems, a low-vibration container according to the present invention has an outer frame member mounted on a truck of a transport vehicle such as a truck and the like. Using an upper spring member having a long flexure length from the ceiling, the inner box for storing the transported goods is supported, and a vibration insulator is arranged between the lower part of the inner box and the lower part of the outer frame member. The main weight is supported by the plurality of upper spring members, and the remaining total lower load is supported by the vibration insulator.

[0005]

BEST MODE FOR CARRYING OUT THE INVENTION A low vibration container according to the present invention is provided with a fishing net and an inner box having a total weight M of inner boxes for storing fresh food items such as eggs, beer, milk, wine, etc. ,
The outer frame member is placed on a truck of a transport vehicle such as a truck, and a plurality of columns are erected on both side surfaces of the outer frame member. A connecting member reinforces and supports between the columns, wall members are arranged on both side surfaces of the outer frame member, and projecting members are provided in the direction of both upper side surfaces of the respective columns,
A mounting member is fixed along the longitudinal direction of the middle part on both sides of the inner box, and a stroke adjuster composed of a hydraulic cylinder or the like and an upper spring member are connected in series between the mounting member of the inner box and the overhanging member of the column. through the by Tsuri支, among the inner box total weight M by the upper spring member, and able to Tsuri支by upper spring member of the total top applied load P _t a plurality of upper use springs number N, which accounts for major weight A plurality of n vibration insulators each having a pressure sensor disposed between the lower part of the inner box and the upper surface of the lower connecting member of the outer frame member, and the total weight of the inner box is provided by the n vibration insulators. Of M, several 10% of total lower load p
We shall support the _t, for holding the setting for the inner box to the total weight M and total lower applied load p _t constant, enter the pressure load signal of the pressure sensor of the isolators, the stroke output signal A controller having an active function for controlling the stroke of the adjuster is provided, and the inner box provided inside the fishing rod in the outer frame member is integrated with the outer frame member so as to be able to get on and off the vehicle.

In the low-vibration container of the present invention, equipment necessary for storing the loaded contents, such as a temperature / humidity control device in the inner box, can be provided.

In the low-vibration container according to the present invention, the outer frame member in which the inner box is provided inside the fishing rod can be formed as an outer box.

In the low vibration container of the present invention, the total weight M of the inner box can be assumed to be about 10 tons, and the container including the outer frame member can be assumed to be about 11 tons.

In the low-vibration container of the present invention, the stroke control of the stroke adjuster comprising a hydraulic cylinder can be performed by controlling the hydraulic pressure from a hydraulic source by a hydraulic servo valve. A pneumatic damper as a dashpot having a vibration damping action and being built in parallel at the center with a cushion spring, which is a multiple elastic sheet made of, for example, a rubber sheet or the like, and a compressed air of the pneumatic damper. It can be composed of an air pressure sensor that detects the load pressure. A pressure load signal from the air pressure sensor is input to the controller, an output signal for controlling the hydraulic servo valve is output, and the stroke as an active function is output. the can also control the stroke of the regulator, the total lower applied load p _t which is set against the inner box gross weight M constant In addition to lifting, it has the effect of feedback control also the vertical amplitude of the inner box.

In the low-vibration container according to the present invention, irregular horizontal vibration absorption due to sudden start / stop or a curve of the vehicle is caused by a frictional force between the inner box and a vibration insulator disposed at a lower portion. Although it has a reducing absorption effect, it is also possible to insert a shock absorber or the like between the inner box and the side of the outer frame member, between the front and rear.

In the low-vibration container according to the present invention, the natural frequency of the inner box is represented by the total upper load P
_Since the main weight of _t is loaded, as will be described later, it is substantially determined by the natural frequency f of the upper spring member, and when N springs are used in parallel, F = NKx: where K: spring constant,
F: force, and x: is represented by the vertical coordinate, the total upper load weight P _t, the maximum deflection length: if X (cm), P
_t g = NKX, and the maximum spring force: if P = P _t / N, so the Pg = KX, will be determined by the natural frequency f with respect to one of the spring. Therefore, assuming that ω: angular velocity, ω ² = K / P = g / X and f = ω / 2π,
(2πf) ² = g / X, where g = 980 cm /
By substituting sec ² , f ² = 25 / X, and it can be seen that the natural frequency f is inversely proportional to the maximum deflection length: X (cm), and becomes independent of the load weight, but is related through X. Accordingly, the upper spring member main weight load, maximum deflection length for one of the springs to be used, the total upper applied load P _t maximum deflection length corresponding to: be designed to X, natural frequency f ₀ = ( 25 / X) ^1/2 Hz can be obtained.

In order to make the natural frequency f ₀ Hz of the upper spring member in the low vibration container of the present invention, the maximum spring force is:
For P = _Pt / N, the maximum deflection length: X may be obtained. For a cylindrical helical spring made of a steel wire having a circular cross section and having a maximum spring force: P and a maximum deflection length: X, the wire diameter d and the number of turns i of the steel wire can be calculated from the following formula: d ³ = 16 PR / πτ (1) i = XdG / 4πR ² τ (2) where R (cm): radius of winding, τ (kg / cm ² ):
Torsional stress and G (kg / cm ² ): transverse elastic modulus. As described in Examples, τ = 950 (kg / cm
² ) If G = 8.7 × 10 ⁵ (kg / cm ² ), X = 2.8 cm is obtained and the natural frequency f ₀ = 3 Hz
It turns out that it is feasible.

In the low-vibration container of the present invention, a vibration insulator is provided at the lower part of the inner box further supported by the upper spring member. The combined natural frequency f of the inner box is ignored ignoring the function of the controller. In a simplified case, it can be obtained as follows. Relative to the total lower applied load p _t, the use of the said vibration insulator n, to said vibration insulator per, lower applied load p = p _t / n, and the maximum deflection length for which: the x. P _t g = NKX, and p _t g = nkx, K is the upper spring constant and k is the spring constant of the vibration insulator. An inner box gross weight _{M = P t + p t,} ω: if synthetic angular velocity, and ^{ω 2 = (NK + nk)} / M. The total upper load weight P _t, the ratio of total lower applied load _{p t s = p t / P} t
Ω ² = (g / X) · (1 + s) ⁻¹ (1 + Xs
/ X). Here, if X / x = 1 is selected, (2π
f) ² = ω ² = (g / X), and if the natural frequency f _{0 of} the upper spring member is (2πf ₀ ) ² = g / X, (f / f ₀ ) ² = 1, that is, synthesis The natural frequency f is equal to the natural frequency f ₀ . Therefore, if X = x is set, the combined natural frequency f = f ₀ Hz may be set.

If the stroke of the stroke adjuster in the low-vibration container of the present invention is set to a length sufficiently including the maximum deflection length: X, a predetermined total lower load load _pt can be set.

In the low-vibration container of the present invention, the natural frequency f of the vertical vibration can be set to about several Hz, so that the total weight M of the inner box for storing fresh food items such as eggs, beer, milk, wine, etc. Since the vibration of the vehicle itself with respect to the inner box having the rotation speed of the engine is several thousand rpm, if the vertical vibration frequency caused by the regular operation is about several tens Hz, the attenuation rate of the vibration frequency is several minutes. And the energy due to vibration is proportional to the square of the velocity, and therefore proportional to the square of the frequency. The low-vibration container reduces the influence on perishable foodstuffs to about several tenths. Has an action.

In the low-vibration container of the present invention, the vibration insulator is constituted by a parallel connection of a cushion spring and a dashpot having a vibration damping / absorbing action. Can be minimized.

In the low-vibration container of the present invention, if the total weight M of the inner box in the design values of the upper spring member and the vibration insulator changes according to the type of the storage material to be stored, for example, if the weight is reduced to half. , designed X corresponds to the total upper applied load P _t, the design natural frequency f ₀ = (25 / X)
^In the case of ^1/2 Hz, the weight is reduced by half, so the deflection is X / 2.
cm and its natural frequency f = 2 ^1/2 f ₀ Hz. Since the vibration insulator does not change when the function of the controller is simplified and ignored, the combined natural frequency f = 2 ^1/2 f ₀ Hz.
It may be about 2 ^1/2 f ₀ Hz. Therefore, even if the load weight is reduced by half, the vibration frequency can be maintained at about 1.4 f ₀ Hz, and the change in the deflection extends the stroke of the stroke adjuster, and secures a predetermined load weight on the vibration insulator. Has the ability to do things. Therefore, if f ₀ = 3 Hz, the combined natural frequency f = 4.2 Hz.

[0018]

DESCRIPTION OF THE PREFERRED EMBODIMENTS In the drawings of an embodiment of the present invention, FIG. 1 is a schematic rear view of a partially-mounted state of a low-vibration container in use, FIG. 2 is a schematic side view of a partially-mounted state in the used state, and FIG. FIG. 4 is an explanatory view of the mechanism of the vibration container, and FIG. 4 is a characteristic table of the upper spring member used for the low vibration container.

The low-vibration container according to the embodiment of the present invention will now be described with reference to FIGS. 1 and 2. As shown in FIGS. 1 and 2, the inner box has a total weight M = 10 for storing fresh food items such as eggs, beer, milk and wine. An outer frame member (2) for mounting an inner box (1) having a ton with reduced vibration is placed on a truck (4a) of a transport vehicle (4) such as a truck, and both side surfaces of the outer frame member , Three pillars (2a) are erected, and a plurality of connecting members (2c) are reinforced and supported at upper and lower portions between the vehicle side surface and both side surfaces of the pillars, and the outer frame member has two side surfaces. A wall member is provided on each of the pillars, and overhanging members (2b) are provided in both upper side surfaces of each of the columns, and an attaching member (1c) is provided along a longitudinal direction of the middle portion on both side surfaces of the inner box.
And a stroke adjuster (1b) composed of a hydraulic cylinder and an upper spring member (1a) are supported in series between a mounting member of the inner box and a projecting member of the column, and of the inner box the total weight M = 10 richer in the spring member, the total upper applied load P _t = 8 tons and able to Tsuri支by upper uses spring number N = 12 pieces of the upper spring member, Tsuri支been the Six vibration insulators (1d) each having a pressure sensor (1g) on the upper surface are disposed on a pair of connecting members between the columns at the lower portion of the inner box, and the inner box is formed by the six vibration insulators. of the weight M = 10 tons shall support the total lower applied load p _t = 2 tons for holding the setting = 2 t total lower applied load p _t against the inner box the total weight M = 10 tons constant The pressure load signal of the vibration insulator pressure sensor is input and the output signal Characterized in that it equipped with the controller (3) for controlling the stroke of the stroke adjuster.

FIG. 3 is an explanatory view of the mechanism including the controller (3) in the low-vibration container of the present embodiment. The stroke control of the stroke adjuster (1b) composed of a hydraulic cylinder is performed by the hydraulic source (3b). Hydraulic pressure to hydraulic servo valve (3
The vibration insulator (1d) includes a cushion spring (1e), which is a multiple elastic sheet made of a rubber sheet or the like, and a pneumatic damper (1) built in parallel at the center.
f) and an air pressure sensor (1g ') for detecting the load pressure of the compressed air of the pneumatic damper, and inputting a pressure load signal from the air pressure sensor to the controller,
An output signal for controlling the hydraulic servo valve is output, the stroke of the stroke adjuster is controlled, and the inner box total weight M = 10
In addition to keeping the total lower load load _pt = 2 tons set for the tons constant, it also has the effect of feedback controlling the vertical amplitude of the inner box (1).

Inner box in the low-vibration container of the present embodiment
The natural frequency of (1) is the total weight of the inner box M = 10 tons.
And the total upper load P_t= Loads 8 tons of main weight
Determined by the natural frequency f of the upper spring member (1a), N
When springs are used in parallel, F = NKx: where K: spring
Constant, F: force, and x: vertical coordinate, total upper negative
Load P_t= 8 tons, maximum deflection length: X (c
m), P_tg = NKX, and the maximum spring force: P
= P_tIf / N = 666kg, then Pg = KX
Therefore, it is determined by the natural frequency f for one spring.
You. Therefore, if ω: angular velocity, ω^Two= K / P = g /
X and f₀= Ω / 2π, (2πf₀) ^Two= G / X
Where g = 980 cm / sec^TwoAnd substitute f
₀ ^Two= 25 / X, and the natural frequency f is the maximum deflection length:
It is understood that it is inversely proportional to X (cm), and is independent of the load weight
Where X is related.

In the low vibration container of this embodiment, the upper spring member (1a) is designed so that the natural frequency f = 1 Hz. Maximum spring force: For _{P = P t / N = 666kg} , maximum deflection length: becomes Xcm,, shows a characteristic of the upper spring member per Figure 4. For a cylindrical helical spring made of a steel wire having a circular cross section and having a maximum spring force: P and a maximum deflection length: X, the wire diameter d and the number of turns i of the steel wire can be calculated from the following formula: d ³ = 16 PR / πτ (1) i = XdG / 4πR ² τ (2) where R (cm): radius of winding, τ (kg / cm ² ):
Torsional stress and G (kg / cm ² ): transverse elastic modulus. For steel wire, τ = 950 kg / cm ² and G =
If it is 8.7 × 10 ⁵ kg / cm ² , the value shown in FIG. 4 is obtained. Since X = 2.8 cm, the natural frequency f ₀ = 3 Hz
Becomes

In the low-vibration container of this embodiment, the upper spring member (1a) is further provided with a vibration insulator (1d).
If the function of the controller is ignored and simplified, the combined natural frequency f of the inner box (1) is obtained. If n = 6 of the vibration insulators are used for the total lower load load _pt = 2 tons, the lower load load p = _pt /
n = 333 kg, and the maximum deflection length for this: x
And P _t g = NKX, and p _t g = nkx, K is the upper spring constant and k is a cushion spring constant of the vibration insulator. An inner box gross weight M = 10 Ton = P _t + p _t,
ω: Assuming that the resultant angular velocity is ω ² = (NK + nk) / M. The total upper applied load P _t = 8 tons if the total lower applied load p _t = 2 ton ratio _{s = p t / P t =} 1/4, ω 2 = (g / X) · (1 + s) - ¹・ (1 + Xs /
x). If X / x = 1, then (2πf)
² = ω ² = (g / X), and assuming that the natural frequency f _{0 of} the upper spring member is (2πf ₀ ) ² = g / X,
(F / f ₀ ) ² = 1, and since f ₀ = 3 Hz, f = f
It can be set to about 3 Hz. Therefore, x = X, i.e. for the lower applied load _{p = p t / n = 333kg} , maximum deflection length: x = if about 2.8 cm, synthetic natural frequency f = it can be approximately 3.0 Hz.

In the low-vibration container of this embodiment, the pneumatic damper (1f) of the vibration insulator (1d) has a surface pressure of 1.
5 kg / cm ² , damping coefficient: 2.56 kg · sec
/ Mm, and an air pressure sensor (1
g '), and the hydraulic servo valve (3
outputting an output signal for controlling the a), the control stroke of the stroke adjuster (1b), holding a total lower applied load p _t = 2 tons is set for the inner box to the total weight M = 10 tons constant In addition, the vertical amplitude of the inner box (1) is
The feedback control can be performed to about mm.

In the low-vibration container of this embodiment, the stroke of the stroke adjuster (1b) composed of a hydraulic cylinder sufficiently includes a maximum deflection length: X = 2.8 cm.
cm was adopted.

In the low-vibration container of this embodiment, the dimensions of the inner box (1) are about 2 m in height, 1.8 m in width, and 9 m in length.

[0027]

The present invention is embodied in the form described above and has the following effects.

Using the low-vibration container of the present invention, a large container is integrated with an inner box provided inside a fishing support on an outer frame member to reduce mechanical vibration from the vehicle to about several Hz independently of the vehicle. Low-vibration structure, the same low-vibration transportation is possible no matter what kind of vehicle this container is loaded on.
This has the effect that long-distance transport is possible while maintaining the quality of supplies without giving special consideration to the vehicle.

By using the low-vibration container of the present invention, since the outer shape of the container is an integrated structure of a conventional simple shape, loading and unloading to the vehicle is easy, and even when the container is to be stored in a stationary state, In addition, the container inside box can be stored integrally without separating it from the outer frame member as the outer box, and the equipment necessary for storing the loaded contents, such as the temperature and humidity control device in the inner box, can be provided. Having.

Since the low-vibration container of the present invention is equipped with a controller having an active function, a low-vibration state is automatically realized even when the weight of the loaded material changes, so that a wide variety of types having different specific gravities are provided. It has the effect of being able to respond immediately to loaded cargo.

In the low-vibration container of the present invention, the inner box is supported by using an upper spring member having a long deflection length from the ceiling in the outer frame member along the support, and the lower part of the inner box and the lower part of the outer frame member are supported. A vibration insulator is provided, a main weight of the total weight of the inner box is supported by the plurality of upper spring members, and the remaining lower load is supported by the vibration insulator. Since this does not occupy a large area, there is little effect of sacrificing the loading space for mass loading.

[Brief description of the drawings]

FIG. 1 is a partially cut-away schematic rear view of a low-vibration container according to an embodiment of the present invention in a used state.

FIG. 2 is a partially cut-away schematic side view of the use state of the low-vibration container, showing an embodiment of the present invention.

FIG. 3 is an explanatory view of a mechanism of a low-vibration container, showing an embodiment of the present invention.

FIG. 4 shows a characteristic table of an upper spring member used for a low-vibration container, showing an embodiment of the present invention.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Inner box 1a Upper spring member 1b Stroke adjuster 1c Mounting member 1d Vibration insulator 1e Cushion spring 1f Pneumatic damper 1g Pressure sensor 1g 'Air pressure sensor 2 Outer frame member 2a Column 2b Overhang member 2c Connecting member 3 Controller 3a Hydraulic Servo valve 3b Hydraulic power source 4 Vehicle 4a Bogie _Pt Total upper load load N Number of upper springs used P Maximum spring force X Maximum deflection length L Free length d Wire diameter i Number of turns R Winding radius _pt Total lower load load n Lower working vibration Number of insulators M Total weight of inner box

──────────────────────────────────────────────────続 き Continued on front page (58) Field surveyed (Int. Cl. ⁶ , DB name) B65D 88/12 B60P 1/64 B65D 90/12

Claims (2)

(57) [Claims] An outer frame member (2) for supporting and installing an inner box (1) having a total weight M of the inner box and containing a load material is mounted on a truck (4a) of a transport vehicle (4). A plurality of columns (2a) are erected on both sides of the outer frame member, and a plurality of connecting members (2c) are reinforced and supported between the columns by a plurality of connecting members (2c) above and below the vehicle side and both sides. An overhanging member (2b) is provided in both upper side surfaces of each of the columns, and a mounting member (1c) is fixed along the longitudinal direction of the middle portion on both sides of the inner box. A stroke adjuster (1b) and an upper spring member (1a) are supported in series between the overhang member and the upper spring member, and the total upper load occupying the main weight of the inner box total weight M by the upper spring member. a load P _t is decided to Tsuri支by a plurality of upper spring member, between the lower connecting member upper surface of the inner box bottom and outer frame member Arranged plurality of vibration insulator having a pressure sensor (1 g) and (1d), by the vibration insulation, shall support the remainder of the total lower applied load p _t of the inner box the total weight M, the for holding constant a predetermined setting said total lower load applied p _t against the inner box total weight M, enter the pressure load signal of the pressure sensor of the vibrating insulation, control the stroke of the stroke regulator output signal A low-vibration container characterized by comprising a controller (3) that is capable of getting on and off the vehicle by integrating the inner box provided inside the outer frame member with the fishing support. 2. The apparatus according to claim 1, wherein the inner box is provided with equipment necessary for preserving the quality of the contents loaded in the inner box.
Low vibration container as described.