EP1618047A1

EP1618047A1 - Pallet container

Info

Publication number: EP1618047A1
Application number: EP04727514A
Authority: EP
Inventors: Dietmar Przytulla
Original assignee: Mauser Werke GmbH
Current assignee: Mauser Werke GmbH
Priority date: 2003-04-25
Filing date: 2004-04-15
Publication date: 2006-01-25
Anticipated expiration: 2024-04-15
Also published as: BRPI0409784B1; AU2004233969B2; CN1812917A; ES2267063T3; US20050247710A1; US8408413B2; DE502004000779D1; DE112004000700B4; JP2006524611A; KR20060006941A; DE112004000700A5; EP1618047B1; CN100480148C; BRPI0409784A; IL171576A; WO2004096660A1; KR101125722B1; ZA200508674B; ATE329853T1; CA2523359A1

Abstract

A pallet container includes a bottom pallet and a thin-walled inner container, made of thermoplastic material and resting on the bottom plate, for storing and transporting liquid or free-flowing goods. Closely surrounding the plastic container is a lattice tube frame which includes vertical and horizontal tubular rods welded to one another and which is securely fixed to the bottom plate. In order to improve the lattice tube frame durability while maintaining sufficient stacking load-bearing capacity, at least the vertical tubular rods have regions of low tubular profile height and high tubular profile height, wherein the regions of low tubular profile height are uniformly linear and positioned outside the intersections, and the regions of high tubular profile height are positioned in an area of the intersections.

Description

pallet container

The present invention relates to a pallet container with a thin-walled inner container made of thermoplastic material for the storage and transport of liquid or flowable filling goods, with a space frame which tightly encloses the plastic container as a supporting jacket and with a base pallet on which the plastic container rests and with which the Support jacket is firmly connected, the tubular frame consists of vertical and horizontal tubular rods welded together at the intersection points.

State of the art :

Pallet containers are used for the transport and storage of liquid or flowable filling goods. During the transport of filled pallet containers - especially for goods with a high specific weight (e.g. over 1, 6 g / cm ³ ) - on bad roads with hard-sprung trucks, during rail or sea transport, the tubular frame is affected by the surge force of the goods significantly burdened. These dynamic transport loads generate considerable constantly changing bending and torsional stresses in the space frame, which inevitably lead to fatigue cracks and subsequent rod breakage if the exposure times are long.

Such pallet containers with a support jacket made of tubular frame are generally known in various designs; however, all previous support jacket designs have considerable disadvantages.

Those designs of tubular frame with a uniform continuous tubular profile, for. B. known from EP 0 755 863-A (Fu), DE 297 19 830-A (VL) or US 6 2244453 B1 (Mam) are subject to a fracture of the rod comparatively quickly in the case of bending alternating stresses caused by transport as a result of the oscillating surge pressure of the liquid filling material always begins or is initiated in the pulling area of the truss bars. The broken bars mainly take place in the vicinity of the welded crossing points of the tubular bars.

Those space frame with welded round tubes, for. B. known from EP 0 734 967 B1 (Seh), and with significantly reduced pipe cross-section height provided in the area of the intersection points (no continuous pipe profile, identical depths everywhere or reduced pipe cross-section height) have the serious disadvantage that in these areas the reduced pipe cross-section is considerable load occur sharply and thereby predetermined breaking or kink points z. B. are formed in drop tests, alternating bending stresses due to transport loads and in the hydraulic internal pressure test. The bar areas between the crossing points are considerably too rigid and stiff with all dynamic loads, they do not absorb any deformations; these only take place in the intersection area with the reduced pipe cross sections. In addition, further cross-sectional reductions or relief areas in all horizontal and vertical lattice pipes are mandatory at all welding points. B. EP 0 734 967 B1 (Seh) to protect them against tearing / detachment in the event of alternating bending stresses due to transport loads. However, it is considered to be very disadvantageous that the weakest pipe cross sections are arranged in the immediate vicinity of the welding points of the crossed lattice bars and that a permanent alternating deformation takes place immediately next to the welding points. As a result, the weld spots are overloaded and tend to be torn off. It is a well-known design theory for the welding specialist that dynamically stressed components are not welded exactly where the greatest dynamic deformation takes place.

From WO 01/89954-A as well as from WO 01/89955-A, a pallet container with a trapezoidal tubular profile of the lattice bars is also known, in which the vertical and / or horizontal tubular bars each have an indentation laterally next to an intersection. These partial indentations are intended to act as a "bending hinge" and to reduce the bending resistance moment of the tubular rods. It has been shown that these limited indentations lead to a noticeably longer service life, but the stress peaks concentrated at one point in the event of long-term overuse can still not completely rule out a broken rod.

The previously known tubular frame with a uniform continuous tubular profile, on the other hand, have the disadvantage that the horizontal and vertical tubular bars are subject to bending and torsional stiffness in the event of alternating bending stresses or over their entire length; As a result, fatigue cracks and rod breakage occur here after a comparatively short period of stress, particularly in the vicinity of the welded crossing points of the tubular steel bars.

The known tubular frame made of welded round tube (Seh) with a reduced tube cross-section at the crossing points and additional partial relief areas have the following disadvantages: - The height of the reduced pipe cross sections must be the same at all welded intersections, it must not be adapted to a different bending load.

- The circular tubes with a circular cross-section next to the crossing points welded in the pipe fittings are very rigid, they do not deform when they are subjected to alternating bending stresses.

- The round tubes next to the welded crossing points are also very torsion-resistant, they do not deform under torsional stress.

The horizontal lattice profile bars are twisted under alternating bending stresses by radial movements of the vertical bars with which they are welded. This creates additional tensile and compressive loads on the welding points.

- All loads or tensions caused by transport loads such as B. Pressure, tensile, torsional loads can only be absorbed by the locally limited partial entries (target kink points or break points) directly next to the crossing points.

Task:

It is an object of the present invention to provide a pallet container with a tubular tubular frame made of welded tubular rods, which no longer has the disadvantages of the prior art and in which - taking into account the stacking load of a filled stacked pallet container (double stacking) in addition to the usual transport loads of the and sloshing liquid contents - in particular the vertical pipe rods are more durable against fatigue cracking and rod breakage.

This object is achieved in the generic pallet container, the lattice bars of which have a continuously closed profile, according to the present invention in that at least the vertical lattice bars have a higher bending moment only in the area of their crossing points to be welded and a comparatively lower one in the entire remaining areas between two crossing points Have bending moment of resistance. The tube rods welded together have a higher tube profile height at the crossing points and thus represent limited areas with high bending and torsional rigidity, while the lattice bars lying outside a crossing point have a lower tube profile height and the areas with a lower bending and torsional rigidity represent. It is further provided that the tubular bars have two alternately arranged different cross sections over their entire length, one with a reduced tube profile height and reduced bending resistance moment over a comparatively larger rod length and a cross section with partially increased tube profile height with a higher bending resistance moment, which over a comparatively short rod length extends the area of the welded crossing points. Due to the design according to the invention, in which the areas with a reduced pipe profile height and a lower bending resistance moment are arranged continuously between two crossing points, the area of the welded crossing points is effectively protected against fatigue cracks and rod breakage, i.e. not by a local predetermined bending point directly next to the welding points with rigid areas between the crossing points, but through the entire area between the welded crossing points, which is designed as an elastic, flexible area.

Since the pallet containers have a longer and a shorter side (dimensions 1200 X 1000 mm), the greatest dynamic deformations logically take place in the longer side walls of the pipe grid support jacket, where most of the pipe rod breaks usually occur. The inventive design of the tubular bars, in which the areas with a reduced tubular profile height - viewed in the longitudinal direction of the tubular bars - are designed to be considerably longer than the areas with a higher tubular profile height with a higher bending resistance moment (at least twice as long), in particular the longer side wall of the tubular grid support jacket while maintaining sufficient rigidity against stacking loads as a vibration unit as a whole set so that even with long-term loads from vibrations in the transporter no more tube rod breaks occur.

The harmful bending and torsional stresses that occur during normal transport loads and additionally due to double stacking (superimposed additive pressure load) are absorbed by the entire elastic areas between the rigid crossing points, so that there are no longer excessive local stress peaks at or next to the welded crossing points.

Furthermore, the truss tube according to the invention is torsionally softer in the long areas with a lower tube profile height outside the intersection points, ie it enables more torsion or generates less compressive and tensile stresses at the welded intersection points with the same torsion angle. The invention is explained and described in more detail below on the basis of exemplary embodiments shown schematically in the drawings. Show it :

FIG. 1 a front view of a pallet container according to the invention,

2 shows the pallet container according to the invention in a side view with a stacked second pallet container (double stacking), FIG. 3a hydrostatic pressure distribution in the plastic container, FIG. 3b bulging of the side wall of the plastic container, FIG. 4 deformations of the pallet container by surge forces with superimposed stacking load (side view), FIG. 5 deformations of the pallet container by surge forces and

Stacking load (top view), FIG. 6 lateral deformations of a vertical lattice bar in section: a) normal, b) with deflection outwards and c) inwards, FIG. 7 a consideration of forces at a welded lattice bar crossing point, FIG. 7 b cracking due to bending stress at a crossing point, FIG. 7 c tearing off a welding point at an intersection, FIG. 8 a, b T-beam model with associated stress distribution during bending, FIG. 9 a, b trapezoidal profile with associated stress distribution during bending, FIG. 10 truss bars according to the invention with increased pipe profile height in

Crossing area (square-rectangular profile), FIG. 11 shows a preferred embodiment of trellis tubes according to the invention with increased tube profile height in the intersection area, FIG. 12 cross section through a profile tube trellis according to the invention at a welded intersection (large tube profile height), FIG. 13 cross section through a profile tube trellis outside the welded area

Crossing points (low pipe profile height), FIG. 14 shows a further cross section through a profiled tubular grid rod outside the welded crossing points (low tubular profile height), FIG. 15 shows another cross section through a profiled tubular grid rod outside the welded crossing points (low tubular profile height), FIG. 16 shows another cross section through a profiled tubular grid rod outside the welded intersections (low tube profile height), Figure 17 a shows a longitudinal section of tubular bars on a welded

Crossing point (large pipe profile height), FIG. 17b shows a cross section in the vertical pipe grid rod (large pipe profile height), FIG. 17c shows a cross section in the vertical pipe grid rod (small pipe profile height), FIG. 18 shows an external view of welded crossing areas of the grid pipe frame with profile tube lattice bars according to the invention, FIG. 19 shows an interior view of the welded crossover areas of the lattice tube frame with profile tube lattice bars according to the invention and FIG. 20 elastic deformations of a preferred vertical lattice bar due to surge forces and stacking loads a) normal, b) deflection outwards and c) deflection inwards .

1 shows a pallet container 10 according to the invention with a plastic inner container 12, a tubular support jacket 14 and a base pallet 16 in a front view with a lower removal fitting (pallet width 1000 mm).

The pallet container 10 is shown in FIG. 2 in a side view (pallet length 1200 mm), an identical second pallet container being stacked. Here, the lower pallet container during transport z. B. on a truck in addition to the changing surge pressure loads of the liquid filling material in a significant and overlapping manner by the stacking load of the up and down and back and forth stacked pallet container (double stacking).

When a plastic inner container 12 is filled with liquid filling material 18, there is a course of the hydrostatic internal pressure P / shown in FIG. 3 a, which increases linearly from top to bottom, the center of gravity S of the liquid filling material increasing to about a third of the height of the Inner container is located. In the case of dynamic transport loads, this causes an alternating bulging of the inner container 12, illustrated in FIG. 3 b, with maximum lateral bulging exactly at the height of the center of gravity S. With the dynamic vibrations of the system, the inner container "pumps", the level of the liquid filling material increasing by the height L (level) changes, while the side wall changes by the amount "O" (outside) and "I" (inner side) by the normal position and the underbody (swinging up and down) accordingly in the middle by an amount "O" ' and "I" 'elastically deformed outwards and inwards (in a reinforced form in the stacked pallet container). FIG. 4 shows this vibration state with an additional stacking load “StP” for a long side wall of the pallet container, the tubular bars of the lattice cage necessarily having to undergo these elastic deformations outwards and inwards.

Figure 5 shows the long side wall of the pallet container in plan view. It is clear that the deformation of the side wall towards the outside is approximately twice as large as the deflection of the side wall towards the inside. When considering load conditions, the weakest point or the most stressed area must be taken into account. The two vertical bars in the middle of the long side walls of the lattice cage in the area of the largest bulge are also subject to the greatest loads because these vertical bars are most adversely affected by the action of the stacking load "StP" of the stacked further pallet container. The damage that usually occurs to these vertical bars can be kinking or breakage below the lower horizontal bar and tearing of the welded connections with the uppermost rotating horizontal bar. The stacked pallet container (Fig. 2) also represents an independent vibration system in the case of transport vibrations. The bottom pallet lies on the outside all around on the lattice frame or on the top horizontal lattice bar of the stacked pallet container and swings - also in the middle of the long side wall - most of the way down and also places a high load (like hammer blows) on the middle vertical bars of the stacked pallet container.

In FIGS. 6 a, 6 b and 6 c, a vertical tubular bar 20 in the region of a lower crossing point "X" with a lower welded-on horizontal tubular bar 22 is considered. FIG. 6 a shows the standard position (normal state), while in FIG. 6 b the state of the greatest deflection (amount "O") to the outside and in FIG. 6 c the state of the largest deflection (amount "I") to the inside , When the vertical tubular rod bends outwards (FIG. 6 b), the outside of the rod is subjected to high tensile stresses and the inside of the rod is subjected to corresponding compressive stresses. When the vertical tubular rod bends inwards (FIG. 6 c), however, the outside of the rod is exposed to lower compressive stresses and the inside of the rod is subjected to corresponding tensile stresses. These deformation states occur with dynamic transport loads in rapid alternation of approx. 3 Hz (vibrations / sec = approx. 180 hits / minute).

When viewing FIG. 4, it becomes clear that the vertical tube rod below the crossing point "X" is bent more than above this crossing point. The reason for this is that the lower end of the vertical tubular rods is firmly fixed to the floor pallet 16 and the distance from the crossing point "X" to the floor pallet 16 is comparatively short. This in turn results in special loading situations, which are illustrated in FIGS. 7 a, 7 b and 7_c. Due to the different degrees of deflection of the vertical bars (top, middle and bottom; and outside and in the middle in the long side wall of the lattice frame), the horizontal tubular rods are twisted in themselves, which creates a torsional stress which manifests itself in the lower welding points of the crossing point "X" under consideration as an additional tensile stress "Z", which is additive in its effect (FIG. 7 a ). This can lead to a fatigue crack or broken rod (Fig. 7 b) or z. B. in circular tube profiles lead to tearing / detachment of the weld points (Fig. 7 c).

FIGS. 8 a and 8_b illustrate a T-beam with its associated stress state when subjected to bending loads to explain the tensile / compressive stresses that occur. The neutral fiber layer (= elastic line) passes through the center of gravity SF of a bending beam (T-beam). In the case of a symmetrical cross-section (e.g. round tube, square cross-section or rectangular cross-section), the neutral fiber layer lies in the middle of the bending beam because the center of gravity is also there. As illustrated in FIG. 8 a, the area center of gravity SF in the T-beam is shifted downwards towards the broad side of the T-beam. The result of this is that the section modulus of the T-beam is greater for the lower edge fibers on the wide side than for the upper edge fibers on the narrow side, and thus the stresses below are lower than at the top. Typically, almost any material can be subjected to significantly higher pressure loads than tensile loads. H. Endure higher compressive stresses than dangerous tensile stresses. This is important for the correct installation position of a dynamically loaded component.

Similarly, i. H. A tubular rod with a trapezoidal profile (with a wide side and a narrow side) behaves approximately like a T-beam, as can be seen in FIGS. 9 a and 9_b. If you consider the worst case load on a long side of the lattice frame with the greatest deflection outwards of a vertical tubular rod in the area of the trapezoidal profile, the tensile stresses on the outer broad side of the tubular rod, where the welding points are arranged, result in lower tensile stresses than Compressive stresses on the inward-facing narrow side of the vertical tubular rod (see Fig. 9 b): Oz <ÖD.

From this it is clear that the vertical pipe rod in the area of the favorable trapezoidal profile is subject to lower dangerous tensile stresses when the critical deflection to the outside (T-beam model) than if a symmetrical pipe cross-section such as. B. would be present in a round tube.

FIG. 10 shows an embodiment in accordance with the present invention. The basic profile of the tubular bars is designed as a square profile (edge length e.g. 16 mm = high rectangular profile). In the crossing areas, the horizontal and vertical tube bars 20, 22 a large tube profile height "H" of z. B. 16 mm, while in the free areas of the tubular rods outside the crossing points a low rectangular profile with a reduced, lower tube profile height "h" of z. B. 12 mm is provided. The reduction of the tube profile height from "H" to "h" was carried out from the side on which the horizontal and vertical tube rods are welded together.

A preferred embodiment according to the present invention is shown in FIG. The basic profile of the tubular bars is a trapezoidal profile. The horizontal and vertical tubular bars 20, 22 in the intersection areas likewise have a large tubular profile height "H" of 16 mm and in the free areas of the tubular bars outside the intersection areas a reduced, lower tubular profile height "h" of approximately 12 mm in approximately rectangular cross-section ( low rectangular profile). Here, however, the reduction of the pipe profile height from "H" to "h" was introduced from the side opposite the welding points. This has the advantage that the sides on which the horizontal and vertical tubular rods are welded to one another are linearly continuous and undeformed. As a result, there are no significant changes or jumps in the amount of the maximum tensile stresses with deflection (amount "O") of a vertical tubular rod to the outside.

In the lower region of the vertical tubular rod 20, a further advantageous embodiment variant is shown here, in which the reduction of the tubular profile height from "H" to "h" was carried out from both sides (welded side and the side opposite the welding points), which results in manufacturing advantages and result in no one-sided deformation stress. Furthermore, when reducing the tube rod height on both sides, only a smaller, i.e. H. form half of the height difference (H - h) / 2 (per side e.g. 2-3 mm) into the high basic profile.

FIG. 12 shows a preferred trapezoidal tubular profile as a high basic profile in a cross-sectional view through a tubular tubular bar according to the invention at a welded crossing point (large tubular profile height). The height "H" is 16 mm and the width is approx. 18 mm. In Figure 13, the cross section through the tubular profile bar is gem. Fig. 12 shown outside the welded intersection with low pipe profile height "h". The height "h" is 12 mm and the width is approximately 20 mm. The reduction of the tube profile height from "H" to "h" was done from the broad side of the trapezoidal base profile. FIG. 14 shows another cross-sectional version of a tubular tubular bar outside the welded crossing point lower tube profile height "h". The height "h" is 12 mm and the width is approximately 19 mm. The reduction of the tube profile height from "H" to "h" was done from the narrow side of the trapezoidal base profile; the profile is approximately rectangular. Another version of a reduced tube cross section is shown in FIG. 15. In order to reduce the tube profile height H of the trapezoidal base profile, the narrow side was also molded inwards into the tube cross section; there is also an approximately rectangular profile.

A further version of a pipe cross section with a reduced height is illustrated in FIG. 16. The pipe profile height H was reduced by molding the two opposite, sloping side walls of the trapezoidal basic profile inwards into the pipe cross section.

FIG. 17 shows the preferred embodiment with a trapezoidal basic profile H over the crossing point and a reduced-height rectangular tubular bar profile h between the crossing points. The reduction of the tube profile height from "H" to "h" was carried out for the horizontal and vertical tube rods 20, 22 in each case from the side opposite the welding points.

In Figure 18, the detail of a lattice frame is illustrated in a top view from the outside with four crossing points. The horizontal and vertical pipe bars are welded to each other by means of four welding points per crossing point (through the outer ribs of the pipe bars lying on top of each other and crossing each other).

The total pipe rod length Lh between two crossing points with lower

Pipe profile height h was flattened from the large pipe profile height H = basic profile,

(or rolled, flattened, molded) and is between 100 mm to 260 mm, preferably about 130 mm.

The comparatively short pipe bar length, which extends over an intersection

LH with high pipe profile height H is between 40 mm to 120 mm, preferably approx.

60 mm (= 3 x tube rod width of 20 mm).

Accordingly, the view from the inside (onto the elevations H of the vertical tubular rods 20) is shown in FIG. 19.

In order to achieve a high degree of bending stiffness in the area of the welded crossing points with a lower bending stiffness or higher elasticity in the entire area of the lattice bars outside the crossing points, various advantageous measures can be implemented. It can be provided, on the one hand, that the horizontal tubular bars 22 outside the crossing points have the same or a lower tube profile height than the vertical tubular bars 20 outside of the of intersections. On the other hand, it can be provided that the vertical tubular grating bars 20 within the intersection areas have an equal or higher tubular profile height than the horizontal tubular grating bars 22. Furthermore, the vertical and / or the horizontal tubular bars 20, 22 within the intersection areas over a length LH of the respective tubular bar 20, 22 in the longitudinal direction of the tubular bar from at least two times the width of the tubular bar (2 x 20 mm) to six times the width of the tubular bar, preferably one about three times the width of the tubular bar. For the low bar profile (low tube profile height) of the vertical and / or the horizontal tubular bars 20, 22 outside the intersection areas, a length Lh of the respective tubular bar 20, 22 - in the longitudinal direction of the tubular bar - from at least three times the tubular bar width (3 x 20 mm) to to an eight-fold pipe rod width, preferably an approximately six-fold pipe rod width, is recommended.

In terms of manufacturing technology, it is advantageous if the lower tube profile height h is formed with a consistently high tube profile height H by regions (lateral curvature) on both sides (curling) of the initial profile rod.

Another possibility of reducing the tube profile height H can be achieved in some areas by one-sided and / or two-sided molding (curling, rolling) from two opposite sides of the initial profile bar (basic profile).

These measures, individually or in an advantageous combination, lead to a considerable one. Improvement of the overall elasticity behavior of a lattice wall level and relief of the welded intersection areas and bring about a noticeable reduction in the susceptibility to breakage (= fatigue fracture) in the case of long-lasting and strong bending alternating stresses, such as e.g. B. with extraordinary transport loads of filled pallet containers for truck transports on poor routes.

In the case of the vertical and / or horizontal pipe bars, the differences in the pipe profile height can be as follows:

1. differing over the length of the pipe grid,

2. only on vertical pipe bars,

3. on vertical and horizontal pipe bars, or / and

4. Realized only in some areas on the tubular lattice bars where they are required in accordance with the stresses that occur. FIG. 20 a shows a vertical tubular rod 20 in the preferred position in the normal position. With dynamic loading, the tubular rod 20 swings around this normal position and bends outwards according to FIG. 20b and inwards according to FIG. 20c.

Through this inventive design of the tubular rods - in comparison to the known pallet containers - especially for the long side walls of the lattice frame, a larger amount "O" of the greatest elastic deflection to the outside and a larger amount "I" of the greatest elastic deflection to the inside are made possible without that the occurring voltage peaks reach such high values that in a very short time lead to fatigue cracks and brittle fractures of the most stressed vertical bars.

The lattice cage with its many "long" areas of low profile bar height therefore proves to be a much more elastic spring system in comparison to known lattice cages of conventional pallet containers.

References list

10 pallet containers Pι ^" hydrostat. Internal pressure

12 inner containers HD-PE S center of gravity

14 Lattice tube support jacket 0 Deflection to the outside

16 Floor pallet I inward deflection

18 liquid filling O 'deflection to the outside

20 vertical tube rod I ^' deflection inwards

22 horizontal pipe rod "X" lower crossing point

"Z" tension H high pipe rod height

M center point h reduced tube rod height

SF center of gravity σz tensile stress

AI area rectangle 1 σ _D compressive stress

A ₂ area rectangle 2 Abstandι distance SF -AI

LH length high tube rod height Θ2 distance SF -A2

Lh length reduced tube rod height

Claims

claims

1.) Pallet container (10) with a thin-walled inner container (12) made of thermoplastic material for the storage and transport of liquid or flowable filling goods, with a space frame (14) tightly enclosing the plastic container (12) as a supporting jacket and with a bottom pallet (16 ), on which the plastic container (12) rests and with which the tubular frame (14) is firmly connected, the tubular frame (14) comprising vertical and horizontal tubular rods (20, 22) welded to one another at the crossing points, characterized in that at least the vertical pipe rods (20) have areas with different pipe profile heights, the areas with lower pipe profile heights (h) being provided in a uniform, linear manner between and outside the crossing points and the areas with higher pipe profile heights (H) at or within the crossing points.

2.) Pallet container according to claim 1, characterized in that the tubular rods (20, 22) have two alternately arranged different cross-sections over their entire length, a cross-section with reduced tube profile height (h) and reduced bending resistance moment over a comparatively large rod length (Lh) and a cross section with a partially increased tube profile height (H) with a higher bending resistance moment, which extends over a comparatively short bar length (LH) over the area of the welded intersection points.

3.) Pallet container according to claim 1 or 2, characterized in that the areas with low tube profile height (h) are formed centrally between two crossing points and the areas with high tube profile height (H) running centrally over each crossing point.

4.) Pallet container according to claim 1, 2 or 3, characterized in that the areas with low tube profile height (h) between two crossing points - viewed in the longitudinal direction of the tube rod - are at least twice as long

(Lh> = 2 x LH) like the areas with high pipe profile height (H) that run over each intersection.

5.) Pallet container according to claim 1, 2, 3 or 4, characterized in that the tubular bars (20, 22) are designed with respect to their tube profile height outside the intersection as a low rectangular profile and in the area of the intersection as a high rectangular profile.

6.) Pallet container according to claim 1, 2, 3 or 4, characterized in that the tubular bars (20, 22) are designed with respect to their tube profile height outside the intersection as a low rectangular profile and in the area of the intersection as a high trapezoidal profile.

7.) Pallet container according to at least one of claims 1 to 6, characterized in that the horizontal tubular bars (22) outside the crossing points have the same or lower bar profile (tube profile height) than the vertical tubular bars (20) outside the crossing points.

8.) Pallet container according to at least one of claims 1 to 7, characterized in that the vertical tubular bars (20) within the intersection areas have the same or higher bar profile (tube profile height) than the horizontal tubular bars (22).

9.) Pallet container according to at least one of claims 1 to 8, characterized in that the high bar profile (tube profile height) of the vertical and / or the horizontal tubular bars (20, 22) within the crossing areas over a length (LH) of the respective tubular bar ( 20, 22) in the longitudinal direction of the tube rod extends from at least twice the tube rod width up to six times the tube rod width, preferably approximately three times the tube rod width.

10.) Pallet container according to at least one of claims 1 to 9, characterized in that the low bar profile (low tube profile height) of the vertical or / and the horizontal tubular bars (20, 22) outside the intersection areas over a length (Lh) of the respective tubular bar (20, 22) - in the longitudinal direction of the tube rod - extends from at least three times the tube rod width to eight times the tube rod width, preferably approximately six times the tube rod width.

11.) Pallet container according to one of the preceding claims 1 to 10, characterized in that the lower tube profile height (h) is formed by regionally bilateral molding (curling) of the starting profile rod with a continuously high tube profile height (H).

12.) Pallet container according to one of the preceding claims 1 to 11, characterized in that the lower tube profile height (h) by regionally one-sided and / or bilateral molding (curling, rolling) from two opposite sides of the initial profile bar with a continuously high tube profile height ( H = basic profile) is formed.