KR20030015251A - Palette container - Google Patents

Abstract

The present invention relates to a pallet container (10) having a rigid, thin walled inner container (12) made of thermoplastic material for the storage and transport of fluid or free-flowing loads, said pallet container being a support jacket. And a cage 14 of intersecting pipe bars closely surrounding the plastic container 12 and a bottom pallet 16 which supports the container and firmly attaches a support jacket thereon, the cage 14 having Vertical and horizontal pipe bars 30,32 that are rigidly welded to each other. Some known pallet containers exhibit significant defects (pipe bar breakage due to fatigue) upon the action of sustained dynamic vibration stresses, which are experienced, for example, through stress due to prolonged transport on poor roads. According to the present invention, an optimum suitable vibrational elasticity with sufficient flexural strength can be realized due to the improvement of the cage jacket in which the pipe bars 30, 32 consist of a closed profile with a special trapezoidal cross section.

Description

Pallet Containers {PALETTE CONTAINER}

Pallet containers with such welded pipe bar support jackets are generally known, for example as disclosed in EP 0 734 987 A (Sch). The pipe bar support jacket of the disclosed pallet container consists of pipe bars having a circular profile, the pipe bars being highly compressed at the welded intersection. Another pallet container with pipe bars with different cross-sectional structures is known from DE 297 19 830 U1 (vL), which pallets are recessed without any dimples and individually reduced in any cross section. It is characterized by having a specific uniform cross section through the entire length of the bar without parts. Another pallet container with a cage with an open profile pipe bar is known from DE 196 42 242. Here, straight outwardly facing flanges in the transverse direction are welded together in the area where the cage bars intersect. Open profiled cage bars have slight torsional rigidity and are difficult to handle pallet containers by hand due to their thin thickness and outer flanges having relatively sharp edges. Furthermore, various pallet containers with cage bars having a square cross section are known in the art.

The attachment of the bottom pallet to the cage jacket can be of a structure such as a flat pallet made of plastic or wood or a steel tube frame, usually with screws, brackets that engage, for example, the lower horizontal cage bar and the circumferentially extending cage bar. , By means of attachment such as clamps or grips. These attachment means are nailed, riveted, screwed or welded to the upper outer edge or top of the pallet.

For industrial use or when pallet containers are used in the chemical industry, the pallet containers must pass government approval inspections and implement various quality controls. For example, a filled pallet container must be subjected to a pressure test and a drop test from a specific height. Pallet containers, which usually have a filling volume of 1000 liters or complex-IBCs (IBC = Intermediate Bulk Container) of the kind discussed herein, are preferably used for liquid transport. In particular, when transporting filled composites (IBCs) in a truck, the shock of movement and the movement of the transport vehicle, especially on uneven roads, causes significant movement of the fluid container load, resulting in a change in pressure. Constant application of the inner container wall results in radial vibrational motion (continuous dynamic vibration stress) in the square-shaped pallet container. During long periods of transport on poor roads, stress is generated depending on the structure of the cage jacket, resulting in fatigue or breakage of the cage bars. As a result, such pallet containers are not suitable, for example, for export to the United States or for multipurpose use.

A disadvantage of the embodiments of EP 0 734 967 A described above is that circular pipe profiles of horizontal and vertical cage pipe bars, in particular in the region of the intersection point, tend to cause significant deformation, especially in the welding position, and thus are prominent compared to other regions. It shows that the section modulus is greatly reduced. In addition, the pipe bar profile still dents deeper adjacent to the dimple at the weld point, thus weakening the bar and, through welding, weakens the material of the area of the recessed pipe bar profile.

The present invention relates to a pallet container having a thin-walled inner receptacle made of thermoplastic material for the storage and transport of fluids or free-flowing goods, wherein the plastic container is crossed. It is closely surrounded by an outer cage jacket, which is a supporting casing consisting of a pipe bar and a bottom pallet, wherein a thermoplastic container is supported on the bottom pallet, and is firmly connected to the support casing.

1 is a front view of a pallet container according to the present invention,

2 is a side view of the testing-palette container,

3 is an enlarged cross-sectional view illustrating a trapezoidal pipe bar profile according to the present invention at a pipe bar intersection;

4 is another enlarged cross-sectional view illustrating a preferred trapezoidal pipe profile at the pipe bar intersection;

5 is a schematic cross sectional view of a hydrodynamic pressure effect of a fluid added on a container sidewall;

6 is a horizontal partial cross-sectional view of the outermost deflection point of the cage;

7 is an enlarged view of the intersection of a pipe bar with dimples,

8 is a trapezoidal cross-sectional view of the pipe bar viewed in the direction D of FIG. 7, FIG.

9 is a trapezoidal cross-sectional view of the pipe bar taken along line C-C of FIG.

10 is a square profile of the cross section of a pipe bar-without stress,

FIG. 11 shows a square profile of the cross section of the pipe bar according to FIG. 10-with an excessive stress,

12 shows a profile of a pipe bar in accordance with the invention-unstressed,

13 is a profile of the pipe bar according to the invention in accordance with FIG. 12-under stress,

14 is another pipe bar profile according to the invention,

15 is another pipe bar profile in accordance with the present invention, and

16 is a partial plan view of a corner arc of a pipe profile according to the invention.

It is an object of the present invention to solve the above-mentioned disadvantages and to propose a pallet container with improved conveying strength with a cage jacket which is a simple construction means having improved resistance to conveying stresses, individually long-term vibrational motion stresses. . On the one hand, the pallet container must meet the highest standards of acceptable levels for carrying dangerous fluids or free flow goods; On the other hand, it should be possible to construct a cage jacket with fewer vertical and / or horizontal cage bars without losing mechanical stability while fulfilling average transport requirements.

According to the present invention, this object is achieved by providing a pallet container with cage jackets of vertical and horizontal steel pipe bars, the cage bars having a trapezoidal cross section with a closed profile and elongated sidewalls extending in parallel. It has a short sidewall extending parallel to and two straight sidewalls extending obliquely with respect to each other, which is connected to the short wall starting from the parallel long sidewalls extending obliquely toward each other, and obliquely with respect to each other The two extending straight sidewalls are characterized by a crown angle of approximately 20 ° to 45 °, preferably of approximately 36 °. The trapezoidal closed profile of the pipe bar has a high bending cross section coefficient and a high torsional cross section coefficient due to the profile sidewalls positioned in a slightly oblique manner with respect to each other. This is realized particularly when the height to width (H / B) ratio of the trapezoidal tube profile is in the range from 0.8 to 1.0, preferably approximately 0.86. According to the pallet container according to the invention, a cage jacket can be realized which withstands the usual conveying stresses foreseen without significant loss of mechanical load carrying capacity and which consists of only five instead of six total horizontal cage bars.

In one embodiment of the invention, the parallel long sidewalls of a cage bar with a trapezoidal profile, in part at the intersection of the two cage bars, are vertically and horizontally extending cages that are rigidly joined after welding. The two outer longitudinal edges form convex portions such that four points are formed at each intersection of the bars, recessed inwards along approximately two times the width of the cage bars, so that each cage bar crosses In the part, the (long) parallel walls facing each other do not touch each other even after they are welded.

In a preferred embodiment, the parallel long wall of the cage bar with the trapezoidal profile is formed along the entire length thereof in such a way that there are formed convex portions (projections) extending outwardly at the two outer longitudinal edge portions. At each intersection of cage bars that are recessed inward (= continuous longitudinal depressions or profiling), and extending horizontally and vertically, four contact points are formed which are firmly connected after welding, opposing parallel One (long) walls are kept away from each other after being welded. A trapezoidal cage bar that pitted along its entire length proved to be particularly good in its use.

In a variant of this embodiment, the long parallel walls of the trapezoidally profiled pipe bars are recessed inward only partially in the area of the intersection, and the long parallel walls of the other trapezoidal pipe bars are along the entire length. It is recessed inward. This can already turn out to be fully sufficient for the average stress load. The depth of the profiling dimples of the long parallel walls is approximately 1 to 2 times the wall thickness of the profiled pipe bar (approximately 1 mm to 2 mm); In a real pallet container, the profiled pipe bar wall thickness is 1 mm, and the depth (A) of the dimple is also 1 mm, so that after welding (contact points of the crossed cage bars record about 1 mm from each other), at each intersection, The opposing long parallel walls are approximately 1 mm apart from each other and do not contact each other after welding. This is particularly important because often pallet containers are stored outdoors and are therefore exposed to weather factors. By providing a distance between cage bars at the welding point, the accumulated rainwater can be easily dried, thereby substantially preventing rust generation. If the weld surfaces are in contact, rusting is inevitable, which will result in severe rusting of the cage bars in a short time.

In another particular configuration of the present invention, at least dimples are provided on the long parallel wall side of the trapezoidal pipe bar that are laterally separated at each welding point. These dimples lower the height H of the pipe bar, reducing the critical maximum of dynamic vibration stress and various bending stresses on sensitive welds. According to the invention, also on each side of the trapezoidal pipe bar, adjacent to the welding point, a dimple is provided, which is spaced at a distance of at least 1/10 of the width B of the pipe bar. Thus, during the dynamic vibration stress, the critical tension maximum value deviates by that distance from the weld point to the adjacent area. According to this particular configuration, in the case of providing a pipe bar having dimples transversely from the weld point, it is possible to substantially reduce the static or dynamic stress on the weld connection, so that the maximum stress is realized, and the weld points are is not provided in the deformation zone, it is possible to keep their high flexural strength (flexural strength). The above-described invention has the following features: Compared to the known pipe bar profile, according to the present invention, the pipe bars are not partially recessed at the welding point, but reduce the bending cross section coefficient to the intersection point and reduce the cage bar. In order to alleviate the static and / or dynamic stresses at the welding points of, dents or dimples are provided, respectively, away from the welding points on the same side and / or opposite side of the profile. The trapezoidal profile is configured to be easily recessed without severe material displacement. Dimples of pipe bars (denting, such as the desired formation of `` vibration elements '', individually indenting) are provided only at certain areas of the pipe bar, resulting in unstable flexural tension maximums on welded intersections or four weld points. And reduce vibration stress. In the case of welding one pipe bar together with a second pipe bar, if the pipe stiffening occurs with the brittleness of the material involved at this location, the pipe is particularly sensitive at this point to the vibrational stress. You make a bar. For example, significant vibrational stresses present in truck transport can break the weld or the pipe bar itself at the weld in a very short time. According to the invention, the cage bar support jacket is configured such that the "vibration points in question" are not at or directly at the intersection and at least slightly away from the welding point of the intersection. Certain vibration points formed by forming dimples are less than 50% of the pipe bar cross section in any case. They are arranged in the range of 10% to 45% of the height of the pipe bar cross section, preferably approximately 1/3 (33%). As a result, the flexural strength of recessed pipe bars is somewhat reduced, but the sensitivity to fatigue due to fatigue is significantly reduced.

The reference numeral 10 shown in FIG . 1 is a pallet container according to the present invention. In FIG. 1, the inner container 12 and the rigid inner container 12 which are thin and blow molded from a thermoplastic material (HD-PE) having an upper opening are formed. It shows a cage of closely enclosed crossed pipe bars 14, which are rigidly but detachably or interchangeably connected to the bottom pallet 16. The front view shown shows a narrow side of a pallet container 10 with an outlet valve disposed in a plastic container 12 near the bottom. In the construction of the wooden pallet (US Runner) shown here, the bottom front of the bottom pallet 16, in which the discharge valve 18 is located, represents the weakest point of the pallet container, which is the approval test, Especially during diagonal drop tests, they are exposed to the greatest stress. The special structure of the cage bar with dimples (see FIG. 7) is shown in a circle.

Prior to the description of the pallet container according to the present invention, a precise comparative stress test (pressure test, drop test, vibration test, pressure capacity upset test, loading capacity of five known pallet containers on the market) was carried out. Test). In a series of vibration tests during the simulation of long haul truck transport on poor roads, particular vulnerabilities of various cage jackets, which occur frequently, can be isolated.

For the purpose of the test purpose intentionally proposed for the continuous overload test, the test pallet container 10 shown in FIG. 2 (here shown without elasticity-increasing dimples) was carried out while applying dynamic vibration stress (FIG. 10, FIG. 11), the points marked on the horizontal and vertical cage bars, which are first damaged and start to break according to the comparative test results, are shown in a circle to illustrate.

FIG. 3 shows a cross section of a closed pipe bar profile 18 according to the invention, which has a trapezoidal cross section, long and short walls 22, 20 extending parallel to one another and obliquely with respect to one another. And two straight walls 24 starting at an elongate parallel wall 22 connected obliquely to the short wall 20, where two straight side walls of the profile 18 extend obliquely with respect to each other. Is in the range of 20 ° to 45 °, preferably a crown angle 26 of approximately 36 °. The ratio of height to width of the trapezoidal profile of the pipe bar is in the range from 0.8 to 1.0, preferably approximately 0.86. Due to the relatively high height of the trapezoidal profile (without bending of the beveled sidewalls), a correspondingly high flexural stiffness is realized, and due to the closed and compact structure of the trapezoidal profile, the pipe bars Shows improved torsional rigidity compared to having a pipe bar profile or an open profile with a structure having a circular profile. The length to the intersection of the elongated horizontal axis of the walls 24 extending obliquely with respect to one another while forming the crown angle 26 is approximately the height of the profile H, ie approximately 2H measured from the long parallel wall 22. to be. This length may be in the range of 0.75H to 2.5H.

A trapezoidal profile 18 that is preferably utilized is shown in FIG. 4 . In a simple manner, the long parallel wall 22 is only partially inward at the intersection of the two pipe bars, in such a way that a convex portion 28 protrudes outward on each of the two outer longitudinal edges. As a result of the dimple, four contact points are formed at each intersection of the horizontally and vertically extending pipe bars, which are firmly connected to each other after welding, so that at each pipe bar intersection they face (long) parallel to each other. The walls 22 are still spaced from each other after welding.

In a particularly preferred embodiment, long convex walls 22 are recessed inward along the entire length of the pipe bar , so that convex portions 28 are provided which project outwardly at two outer longitudinal edges. Pipe bars with a continuously recessed trapezoidal profile 18 have proven to be excellent and are known to be made of a pipe template of 18 mm diameter (56.55 mm circumferential length). The dimple depth of the longitudinal profile should be approximately one or two times the wall thickness of the pipe bar (approximately 1 mm to 2 mm); In the finished pallet container, the wall thickness of the pipe bar is 1 mm and the depth of the dimple is 1 mm. Welding of each of the four contacts at each intersection of the pipe bars is carried out by means of electrical resistance welding. When four-point welding is performed, the intersecting cage bars are pressed together approximately 1 mm, so that the opposing parallel walls 22 at each intersection are still approximately 0.5 mm to 2 mm, preferably approximately 1 mm apart from each other, even after welding Do not touch (distance A = 1 mm). This is especially important because pallet containers are often stored outdoors and exposed to weather. Since the cage bars are separated from each other at the weld, the rainwater that will accumulate there is exposed to the atmosphere and dried, substantially preventing rust. Weld surfaces that are in contact with each other are inevitable in rust generation, which can lead to severe rust generation of the entire cage in a very short time. The example of the cross section also clearly shows that the width of the (long) parallel wall 22 between the outwardly protruding edges 28 is approximately equal to the width B1 of the opposing (short) parallel wall 20. Shows.

The schematic representation of FIG. 5 shows the changing deformation warp of the cage jacket due to the dynamic vibration stress. The hydrostatic internal pressure (shown on the right side of FIG. 5) when loading fluid goods is the maximum cage deflection (approximately 33% of cage height) that occurs at approximately the gravity (S) center level of the goods loaded. D _a , D _i ) and at this level the outward oscillation magnitude is approximately twice as large, because the maximum risk of crack formation in the cage pipe bar is at the lower half of the cage when vibrating stress is applied. Because there is.

The schematic representation of the partial cross-sectional view of FIG . 6 shows a horizontal cross sectional view at the position of the maximum bending influences D _a , D _i . There is no interference of the oscillating deflection directed towards the outside, but the inner fluid column encounters opposite side walls. Thus, the lower circumferential horizontal cage bar 30 is subjected to large bending stresses, especially near the corner bend 38.

7 is an interior view of the cage, showing the intersection 36 between the horizontal pipe bar 30 and the vertical pipe bar 32. Four welding points are marked at the intersection 36. The trapezoidal pipe profiles of the horizontal bar 30 and the vertical bar 32 are provided with intersections 36, individually four weld points, one dimple 34 on each side, so that the dimples ( 34 are at least 1/10 of the pipe bar width B with respect to the point of the intersection 36. A view of the undeformed trapezoidal profile 18 in the D direction is shown in FIG. 8, and an exemplary view of the dimple 34 along the C-C line is shown in FIG. 9. Dimples 34 in the pipe bar may be formed on the ("long") parallel wall 22 side and / or on the opposite ("short") parallel wall 20 side. Thus, numerous variants can thus be realized, so that between two cage bar intersections, at least two dimples can be provided outside of the trapezoidal profile, and / or two dimples can be provided inside. It may be. However, an important point in these embodiments is that the pipe bars not only dent or deform directly at the point of intersection or individually at the welding point, but are also separated from them. Reducing the height H of the profile, the depth T of one dimple 34 should be kept as shallow as possible, ie within the range of 15% to 50%; In a preferred embodiment, the depth T of the dimple is approximately 33% of the height H of the profile. The longitudinal extension length of the dimple 34 along the bar should be approximately 1.5 to 3 times the width B of the profile, in a preferred embodiment the longitudinal extension length of the dimple 34 is approximately the profile width ( It is about twice as much as B).

10 shows a known kind of unstressed pipe profile with a square shaped profile along the entire length of the bar. As illustrated in FIG. 11, after undergoing a relatively short period of dynamic vibration stress, cracks were formed directly on the horizontal bar 30 at the intersection, individually at the weld.

Crack formation or individually rupture of the cage bar always occurs in the region of greatest tensile force. That is, the jump out of the cage jacket takes place in the largest position. The vertical pipe bar is disposed inside the cage jacket and the horizontal pipe bar is placed outside the cage jacket. Cracks and fracture points always occur in the region of the intersection next to the weld point (see the circled portion in FIG. 2). Cracks that begin to form in the vertical pipe bar (for the jacket) always move from outside to inside, and also always start from inside of the horizontal bar and move outward. In comparative tests, cage jackets were made of cage bars using an open profile, and it was found that outwardly angled flat edges were provided which showed good loading capacity, since the weld points were relatively close to each other within the intersection. Because they are far away, they work the most against vibrational stresses.

Compared to the square pipe profile, in FIG. 12, the closed trapezoidal pipe profile 18 according to the invention has two dimples 34 in the horizontal bar 30. As shown in the exaggerated manner in FIG. 13, crack formation does not occur even after long exposure to vibrational stress. This is because, on the one hand, the welds of the intersecting areas are very stable because they are free of defect-inducing dimples, and on the other hand, when the dimples 34 are located at least slightly away from the intersections, This is because it lowers the bending section modulus and acts as a kind of "bending hinge," which acts to prevent the impact of maximum tension on sensitive welds and deflects them towards more flexible areas.

A particular problem in constructing a particular embodiment of the cage jacket is that the vertical and horizontal cage bars must be as stable and rigid as possible to prevent excessive popping out of the pallet container, for example by internal pressure; On the one hand, since the high bending cross-sectional coefficients must be provided to offset the constant dynamic vibration stress, the two criteria described above work in the opposite direction. Given the favorable, low production costs, it is necessary to find the optimal solution. According to the recent trend according to the invention, known pallet containers with cage bars with flat profiles along the length of the bars, for example as disclosed in DE 297 19 830 U1, may be suitable as storage containers. However, it is not suitable as a container for transporting dangerous fluid loads subject to dynamic vibration stress.

The above-cited patent publication is based on the prior art, which is known only for known pallet containers having a cage jacket made of pipe having a circular cross section provided with dimples at least at the weld tube intersection. Using the profiled pipe according to the invention (without any localized dimples) described on page 2 of this specification, the expression avoids local tension accumulation and ... Not to mention precisely, it simply shows that when the cage jackets of these pallet containers are subjected to transport stress, the opposite relationship between flexural strength and vibrational elasticity is not taken into account.

The depth T of the dimple 34 in the trapezoidal profile according to the invention is approximately 25% to 50%, preferably 33%, of the height H of the pipe bar profile. In general, a pipe of 15 mm in height is sufficient to have 5 mm (= 33%) of dimples, so that the vibration stress at the welding point is kept low or eliminated while keeping the pipe rigidity high enough. This stiffness is important for keeping the amplitude of the transverse projections of the vibrating cage at a low level.

FIG. 14 illustrates an embodiment having two dimples 34 on one side of a pipe bar profile facing away from welds with short parallel walls 20, as shown in FIG. 15, a modified version of the embodiment. Particularly useful variants are shown. A pipe profile (18) of the trapezoidal shape is there is each dimple (34) on one side of the shorter parallel wall 20 a side and a cross point (36) neighboring long parallel wall 22 in the lateral direction of the service, the dimple Are opposite to each other. Here, the dimples are spaced about one tenth of the width B of the pipe bar profile from the intersection point 36. Positioning the dimples 34 on each sidewall 20, 22 extending in parallel enhances, in particular, the elastic or “hinge effect” of the pipe profile.

According to the technical aspects of the present invention, the structure of the dimples 34 in the horizontal and vertical pipe bars 30 and 32 may have different depths depending on the strength of the dynamic stress expected to be caught on the cage jacket 14. . Thus, depending on the specific needs or needs, optimal vibrational elasticity in the horizontal and vertical pipe bars can be controlled in various areas of the cage jacket, for example in the long sidewalls or short front and rear walls of the pallet container, while maintaining sufficient flexural strength. .

16 illustrates another important embodiment for reducing the adverse effects of dynamic vibration stress on horizontal pipe bars. In a region parallel to the 90 ° bent corner area and the vertical pipe bar, the horizontal pipe bars 30 of the cage jacket 14 flatten to act as hinged "bending joints". In the corner area, the horizontal pipes do not need to have high bending resistance, where more important is the higher elasticity. Particularly advantageous test results show a horizontal pipe bar 30 flattened in the corner region 38 of the support jacket 14 from inside and / or outside by at least one quarter of the diameter height H of the profile 18. It is realized by the provided pallet container. In one practically constructed embodiment, the horizontal pipes in the lower region of the cage jacket are flattened by approximately 20% from the inside and approximately 35% from the outer corner arch, while the horizontal pipes in the upper region of the cage jacket are It is configured to gradually reduce flatness.

Although the essential features of the present invention have been described schematically and in an exaggerated manner in the accompanying drawings, it should be noted that the description is not to be construed as limiting, but merely for the purpose of illustration and for better understanding.

It is also to be understood that variations may be combined in various ways, and other combinations are possible, within the scope of the present invention. Possible modifications described above, in particular in the lower region of the cage jacket, may be provided with different means for fully realizing the flexural strength with optimum and appropriate pipe bar elasticity.

Reference List

10 pallets container A distance (22-22)

12 HD-PE inner container B profile pipe width

14 Cage Jacket B ₁ Reduced Width (22)

16-floor pallet H profiled pipe height

18 Trapezoidal Profile S Gravity Load Points

20 Short Parallel Wall T-Dimple (34) Depth

22 Long parallel wall D _a External deformation

24 Sloped straight wall D _i internal deformation

26 crown angles

28 Convex (protrusion)

30 horizontal bar

32 vertical bars

34 dimples (30, 32)

36 Intersections (30, 32)

38 corner arc (30)

40 flat parts (38)

Claims (16)

A pallet container 10 having a thin-walled inner container 12 made of thermoplastic material for the storage and transport of fluids or free-flowing goods, wherein the plastic container 12 is a supporting casing. An outer cage jacket 14 serving as) and a thermoplastic container supported thereon and closely surrounded by a bottom pallet 16 which is rigidly connected to the support casing; In the pallet container the cage jacket 14 consists of vertical and horizontal pipe bars 30 and 32 welded together at the intersection point 36, The pipe bars 30, 32 are formed of two long and short walls extending in parallel with each other and extending at an oblique angle with respect to each other and extending and connected to the short walls starting from the parallel long walls 22. With a closed profile 18 having a trapezoidal cross section with a straight wall 24, the two straight and obliquely angled sidewalls of the pipe profile 18 are preferably in the range of 20 ° to 45 °. Preferably a crown angle of approximately 36 °. The method of claim 1, The height / width ratio H / B of the trapezoidal pipe profile 18 is in the range of 0.8 to 1.0, preferably approximately 0.86. (Fig. 3). The method according to claim 1 or 2, The long parallel walls 22 of the trapezoidal pipe profile 18 in the region of the intersection 36 of the two pipe bars 30, 32 are inwardly formed in such a way that the convex portions are formed at the two outer longitudinal edge portions. As they are recessed, four contact points are formed at each intersection 36 of the horizontally and vertically extending pipe bars, which are firmly connected to each other after welding, facing each other at each pipe bar intersection 36. The pallet containers are characterized in that the long walls are still spaced from each other after welding and do not touch each other (FIG. 4). The method according to claim 1 or 2, The long parallel walls 22 of the trapezoidal profile 18 are recessed inwards along the entire length of the pipe, with convex portions 28 (projections) formed on each of the two outer longitudinal edges, and horizontal And four contact points are formed at each intersection 36 of the vertically extending pipe bars 30, 32, which are firmly connected to one another after welding, and at each intersection the long parallel walls 22 facing each other. Pallet space, characterized in that they are still spaced apart and do not touch each other (FIG. 4). The method according to claim 3 or 4, The long parallel wall 22 of the trapezoidal profile of one of the pipe bars 18 is recessed inward in the area of the intersection, and on the other pipe bar 30, 32 of the trapezoidal profile 18. A pallet container, characterized in that an elongate parallel wall (22) extends inwardly along the entire length of the pipe bar. The method according to any one of claims 1 to 5, After welding, the pallet A characterized in that the distance A between the two long parallel walls 22 of the crossing pipe bars 30 and 32 is in the range of approximately 0.5 mm to 2 mm, preferably approximately 1 mm. 4) The method according to any one of claims 1 to 6, A long parallel wall extending between the outwardly extending convex portions of the outer edge portion, in the cross section of the trapezoidal profile 18, has the same width B1 as the opposing (short) wall 20. . The method according to any one of claims 1 to 7, The trapezoidal pipe profile 18 has at least one dimple on one side of the elongate parallel wall 22 which is spaced apart adjacent in the transverse direction of the welding point. (FIG. 14) The method according to any one of claims 1 to 8, Each trapezoidal pipe profile (18) is characterized in that it has a dimple (34) spaced about one tenth of the width (b) of the pipe bar profile in the transverse direction of the weld point. (Fig. 7, Fig. 14) The method according to any one of claims 1 to 9, At least two dimples 34 are provided between the short parallel walls 20, ie two crossing points 36 on the opposite side of the welding point, and / or at least two dimples 34 are formed on the long parallel walls ( 22) a pallet container, characterized in that it is provided on the welding point side. The method according to any one of claims 1 to 10, The depth T of the dimple 34 which reduces the height H of the profile is kept somewhat shallow, ie between about 15% to 50% of the height H of the profile, preferably about 33%. Characterized by a pallet container. (FIG. 9) The method according to any one of claims 1 to 11, The lengthwise extension of the dimple 34 (along the longitudinal direction) is approximately 1.5 to 3 times the width B of the profile, preferably about twice the width of the profile B. Pallet container. (Fig. 7) The method according to any one of claims 1 to 12, On the short parallel wall 20 side and the long parallel wall 22 side, each trapezoidal pipe profile 18 is adjacent in the transverse direction of the cross section 36, at least from the cross section 36. A pallet container characterized in that a dimple 34 is provided approximately 1/10 of the width B of the bar profile. (FIG. 15). The method according to any one of claims 1 to 13, The dimples of the pipe bars 30, 32 have different structures depending on the strength of the dynamic vibration stress in the various regions of the cage jacket 14 or / and in the horizontal and vertical pipe bars 30, 32. Pallet container. A pallet container 10 having a thin-walled inner container 12 made of thermoplastic for the storage and transport of fluid and free-flowing goods, the plastic container 12 having an outer cage jacket serving as a support casing. 14) and said pallet container, which is supported by a thermoplastic container thereon and tightly surrounded by a bottom pallet 16 rigidly connected to said support casing, The corner region of the horizontal pipe bar 30 of the cage jacket 14 bent at 90 ° is flattened parallel to the vertical direction. (FIG. 15) The method of claim 15, The horizontal pipebar 30 bent at an angle of 90 ° in the corner region of the cage jacket 14 is flattened by at least one quarter of the cross-sectional height H of the profile 18 from the inside and / or outside. Pallet container, characterized in that configured to (Figure 15).