KR100772568B1 - Pallet container - Google Patents

Abstract

The present invention relates to a pallet container of a rigid thin-walled inner container (12) made of thermoplastic material for storing and transporting a fluid or free flow load, wherein the support jacket and the support jacket are supported and the support jacket is firmly secured. Like a bottom pallet to be joined, it has a cage jacket 14 made of pipe bars that intersect so as to surround the inner container 12 closely, the cage having vertical and horizontal pipe bars 30 and 32 welded together firmly. Include.

Known pallet containers reveal significant defects (breakdown of pipe bars due to fatigue) when prolonged dynamic vibration stresses are experienced, for example, as experienced through stress due to long distance transport on poor roads.

According to the present invention, a suitable optimal vibrational elasticity with sufficient bending strength consists of pipes 30 and 32 which are vertical and / or horizontal to the contact plane in the intersecting area, with no recesses or laterally intersecting parts, i.e. This can be accomplished by retrofitting the cage jacket to have at least one recess at a distance from the weld point 34.

Description

Pallet Containers {PALLET CONTAINER}

The present invention relates to a pallet container having a thin-walled inner container made of thermoplastic material for storing and transporting a fluid or free-flowing product, the plastic container being a support casing with crossed pipe bars. It is closely surrounded by an outer cage jacket and a bottom pallet on which the thermoplastic container is supported and rigidly connected to the support casing.

Such pallet containers with welded pipe bars supporting the casing are generally known, for example in EP 0 734 987 A (Sch). The pipe bars supporting the casing of the disclosed pallet container consist of pipe bars with a circular profile, which are highly compressed at the intersection where they are welded. In EP 07 55 863 (F) another pallet container with a pipe bar having a cross-section of a square profile is known, which is only partially (approximately 1 mm each) at the four contacts in the cross section in order to promote better welding action. ) Have no compression, or otherwise, any indentations along their entire length, ie with reduced cross section. For example, another pallet container with a cage having a trapezoidal pipe bar open from DE 196 42 242 A is known. Here, straight surfaces with flanges laterally outward are welded to each other in the area where the bars intersect. Attaching the cage jacket to a flat bottom pallet, which may consist of plastic, wood, or steel pipe frames, for example, attachment means such as grips, clamps, brackets or screws that engage the lower and horizontally and circumferentially extending cage bars. Is made by. These methods of attachment are accomplished by any means that are nailed, riveted, screwed or welded to the top or top edge of the pallet.

If pallet containers are to be used in industrial or chemical industries, they must pass government approved inspections and implement various quality controls. For example, filled pallet containers must be subjected to internal pressure checks and drop tests from specific heights. Pallet containers or composite-IBCs (IBC = Intermediate Bulk Containers) of the type discussed herein, typically having a charge of 1000 liters, are preferably used for the transport of liquids. In particular, when transporting a filled composite-IBC by truck, significant shocking motions of the fluid container load may occur due to the impact of the transport and the movement of the transport vehicle, especially on bumpy roads, resulting in continuous movement of the wall of the inner container. The application of varying pressures results in radial vibrational movement of the cage jacket (continuous dynamic vibration stress). During long periods of transportation on poor roads, depending on the structure of the cage jacket, stress builds up and fatigue builds up in the cage bars and destroys them. As a result, such pallet containers are not suitable, for example, for export to the United States or for various uses.                 

A disadvantage of the embodiment of EP 0 734 967 A described above is that the circular pipe profile of the horizontal and vertical cage pipe bars, in particular in the cross section, is particularly susceptible to deformation, in particular in terms of the welding point, and thus is markedly compared to other areas. It shows reduced section coefficient. Welding of the pipe bars will certainly cause material brittleness in the region of the concave pipe bar profile. In addition, the pipe bar profile is further weakened because it forms a deeper recess in the vicinity of the recess with respect to the weld point.

It is an object of the present invention to propose a pallet container with improved transport strength which solves the above mentioned disadvantages and provides a cage jacket with improved transport stress, ie resistance to long term vibrational stresses. Thus, the pallet container must be suitable for transporting hazardous fluids or free flow loads up to grade 6 (= highest standard of acceptable approval).

solution

According to the present invention, the object is achieved by providing a pallet container with a cage jacket of vertical and horizontal steel pipe bars, wherein the vertical and / or horizontal steel pipe bars have no recesses or contact surfaces in areas where the bars intersect. Only very small recesses are formed (the small recesses in one of the plurality of bars are no more than twice the width thickness of the pipe bar, specifically about 2 mm or less), or the pipe bars each cross laterally Part, i.e., at least one recess-a predetermined bending point-near the welding point, each recess being arranged at a distance of approximately 1/10 of the pipe bar width B from the welding point. When the predetermined bending point is moved to a predetermined distance away from the critical weld point to accommodate the varying bending stress resulting from the vibration of the cage jacket, it is brittle and no longer continuous bending stress at the weak weld point. This does not happen, but mainly occurs only in itself, which is not relatively vulnerable. That is, it occurs at the point where there is considerably greater bending elasticity and not directly at the reinforced intersection. In order to improve the bending elasticity of the vertical and / or horizontal pipe bars, they are not formed with recesses on the side opposite the contact plane in the intersecting area, or each pipe is laterally near the intersection, i.e. a predetermined bending point. At least one recess is provided on the other side of the welding point, and each recess may be formed at a distance of at least 1/10 of the pipe bar width B.

Providing at least two recesses in the side of the welding point of the vertical and horizontal pipe bars between two intersections, ie the contact plane and / or the side opposite the contact plane, provides excellent bending elasticity of the cage jacket.

At least one recess on the side of the welding point between two intersections of each vertical and / or horizontal pipe bar, ie their contact plane and the side opposite the side of the contact plane, so that the recesses are exactly opposite each other. It is very advantageous to provide, wherein the recess is arranged at a distance from the intersection, ie at least 1/10 of the pipe bar width B. As a result, the bending stress in the neutral phase is well located in the middle of the pipe bar.                 

According to one feature of the invention, the depth T of one recess for reducing the height H of the profile is kept as small as possible, i.e. approximately 15% to 50% of the profile height H, preferably 33%. do. The longitudinal extension of the recess in the longitudinal direction should be in the range of 1½ to 3 times the profile width B, preferably approximately twice the profile width B. In summary, a sufficiently high bending elasticity is obtained at a predetermined bending point, preferably at the concave portion, while minimizing the bending strength.

Since the strength of the vibration stresses generated in the cage jacket of a fluid-filled pallet container varies, the recesses in each of the horizontal and / or vertical pipe bars are different in the areas of the cage jacket and / or the strength of the vibration stresses in the horizontal and vertical pipes. It may be formed to have a depth that varies according to.

In a preferred embodiment, the vertical and / or horizontal pipe bars have a very special pipe profile, i.e. long sidewalls and short sidewalls extending in parallel, and extending at an angle to one another starting at an oblique and long parallel sidewall with respect to each other to a short wall. A closed profile having a trapezoidal cross section with two straight sidewalls connected is provided, wherein the two straight sidewalls extending obliquely with respect to each other have a crown angle of approximately 20 ° to 45 °, preferably approximately 36 °. To form. The trapezoidal closed profile of the pipe bar has a large cross-sectional coefficient and a large torsional cross-sectional coefficient because the side walls of the profile are located in a slightly oblique manner with respect to each other. This is particularly obtained when the height-to-width ratio (H / B) of the trapezoidal tube profile is in the range of 0.8 to 1.0, preferably 0.86. In one embodiment of the invention, the long parallel sidewalls of a pipe bar having a trapezoidal profile are such that they form an outward curvature (convex) at each of the two outer longitudinal edges in part of the area where the two pipe bars intersect. Concave inwards along approximately twice the width of the pipe profile, so that four contacts are formed at each intersection of vertical and horizontally extending cage bars that are firmly joined after welding, so that each of the cage bar intersections faces each other. The beams do not touch each other after the (long) parallel walls have been welded.

In a preferred embodiment, the long parallel walls of the cage bars having a trapezoidal profile form recesses inwardly along their entire length such that outwardly extending curved portions (convex portions) are formed at the two outer longitudinal edges. (= Continuous longitudinal recesses or profiles), in which case each intersection of each horizontal and vertically extending cage bar is formed with four contact points which are firmly connected after being welded (long) opposing parallel walls Afterwards, they are positioned to be in contact with each other at a predetermined distance from each other. In model experiments, trapezoidal cage bars with recesses along their entire length proved to be very good in use.

In a variant embodiment, the long parallel walls of the trapezoidal profile pipe bars only partially concave inwardly at the intersections, while the long parallel walls of the other trapezoidal pipe bars concave inwards along their entire length. Already this has proven to be very suitable for loads of average stress.

The depth of the profile concave of the long parallel wall is approximately twice the thickness of the profile pipe bar wall, and in actual pallet containers, the wall thickness of the profile pipe bar is 1 mm and the depth (A) of the concave is also 1 mm. Since the contact points of the intersecting cage bars melt by approximately 1 mm-it is clear that the long parallel walls facing each other at each intersection are spaced by approximately 1 mm from each other, so that they do not touch each other even after welding. This is particularly important because pallet containers are sometimes stored outdoors and exposed to bad weather. Providing a predetermined distance between cage bars at the weld point causes the rainwater to dry easily, substantially preventing rusting. If the welding surface is in contact, rust is inevitable, causing excessive corrosion to the cage bar in a short time.

When the pipe bar is compared to a known bib bar profile, no partial recesses are formed at the weld points to reduce the bending cross-sectional coefficients at the intersections and to relieve static and / or dynamic stresses at the weld points of the cage bars. It is a unique feature of the present invention that dents, ie recesses, are provided corresponding to a predetermined distance after the welding point on the same side and / or opposite side of the surface. Preferred trapezoidal profiles are configured such that recesses can be formed easily without severe displacement of the material. Only recesses are formed in certain areas of the cage pipe bar (= recesses, ie dents, such as the formation of a predetermined "vibration element") to reduce vibration stress and fluctuating flexural tension peaks at intersections or at four weld points. Obtained. When welding one pipe bar to another pipe bar, reinforcing the pipe with incidental brittleness results in the pipe bar at this location being particularly sensitive to vibration stress at this point. For example, significant vibrational stresses present in transportation by trucks can cause the welding point or pipe bar itself to break at the welding point in a short time.                 

According to the present invention, the desired "necessary vibration point" of the cage jacket support casing is not provided at exactly the intersection or the region adjacent thereto, but is provided at least a distance from the welding point of the intersection. In any case, the required vibration point provided by forming the recess is smaller than 50% of the pipe bar cross section. They are formed in the range of 10% to 45% of the pipe bar cross-sectional height, preferably approximately 1/3 (33%). As a result, the bending strength of the concave pipe bar is somewhat reduced, but the fracture tendency due to fatigue is considerably reduced.

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

2 is a side view of the inspection pallet container,

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

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

5 is a cross-sectional view schematically illustrating the effect of the fluid load on the fluid in the container side wall,

6 is a horizontal partial cross-sectional view of the most outwardly squeezed point in the cage,

7 is an enlarged view of an intersection of a pipe bar having a recess;

8 is a cross-sectional view of the trapezoidal shape of the pipe bar according to FIG. 7D;                 

9A shows a recess of a trapezoidal cross section of a pipe bar (narrow side) C-C,

9b is a recess of the trapezoidal cross section of the pipe bar (wide side) C-C,

10 is a square profile of a pipe bar cross section unstressed,

11 is a square profile of a cross section of a pipe bar according to FIG. 10 subjected to stress and overstress,

12 is a profile of a pipe bar according to the invention, which is not stressed,

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

14 shows another pipe bar profile according to the invention with two recesses,

15 shows another pipe bar profile according to the invention with four recesses,

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

17 is a square pipe bar profile with two recesses,

18 shows another square pipe bar profile with two to four recesses,

19 is a circular cross section of a pipe bar with two recesses,

20 shows an open trapezoidal pipe bar profile with two recesses,

21 is another circular cross section of a pipe bar with two recesses.

In FIG. 1 , reference numeral 10 denotes a pallet container according to the invention, which is a rigid inner container 12 made of thermoplastic material, which is blow molded into a thin wall, with the upper bars and the pipe bars closely surrounding the inner container intersected. The container 12 is provided with a cage jacket 14, which is rigidly but detachably or replaceably connected to the bottom pallet 16. As shown in FIG. The front view shown shows a narrow side of the pallet container 10 with a discharge valve disposed near the bottom of the inner container 12. The lower front edge of the bottom pallet 16, which is presented here in a wooden pallet structure, represents the weakest point in the pallet container, which edge part is subjected to the greatest stress during approval testing, in particular in the diagonal drop test. Exposed. A specially constructed cage bar (see FIG. 7) with recesses is shown in the circle.

Prior to the development of the pallet container according to the present invention, five types of pallet containers, which are known and commercially available, are subjected to precise comparative stress tests (internal pressure test, drop test, vibration test, acceptance pressure limit test, respectively, which test the loading capacity). (test for pressure capacity upset). In a series of vibration tests during long-haul tests of trucks on poor roads, a particularly frequent vulnerability among various cage jackets was evident.

The test pallet container 10 shown in FIG . 2 (here shown as no elastic enhancement recess), which was subjected to intentional continuous overload test for testing purposes, was first broken according to the comparative test results in the dynamic vibration test in horizontal and vertical cage bars. Those vulnerabilities that are losing or starting to break are circled (see FIGS. 10 and 11).

3 shows an area of the cross section of a closed pipe bar profile 18 having a trapezoidal cross section according to the invention, in which the short and long walls 20, 22 extend in parallel to each other and have two straight walls ( 24 are two straight sidewalls of the profile 18 extending obliquely with respect to one another and starting at an elongated parallel wall 22 and extending obliquely to connect with the shorter wall 20 so that the two straight sidewalls of the profile 18 are in the range of 20 ° to 45 ° Preferably a crown angle 26 of 36 °. The ratio of height to width of the trapezoidal profile of the pipe bar is in the range of 0.8 to 1.0, preferably approximately 0.86. Due to the relatively high height trapezoidal profile (without depressions on the oblique sidewalls), correspondingly high bending stiffness is obtained, and the pipe bar consists of a circular profile due to the closed and compact structure of the trapezoidal profile It shows improved torsional stiffness compared to pipe bar profile with open profile. The crossing distance of the horizontally extending axis of the wall 24 extending obliquely with respect to each other at the crown angle 26 is approximately the height H of the profile, or approximately 2H measured starting from the long parallel wall 22. The distance is in the range of 0.75 to 2.5H.

A more preferred trapezoidal profile 18 is shown in FIG. 4. In a simple embodiment, only a portion of the long parallel wall 22 is recessed inwardly at the intersection of the two pipe bars in such a way that the curvature 28 (convex) is outwardly convex at each of the two outer longitudinal edges. By forming four contacts at each intersection of the pipe bars extending horizontally and vertically, which are firmly connected to each other after welding, the long parallel walls 22 of each pipe bar intersection continue to be spaced apart from each other without any contact after welding. It is.

In a particularly preferred embodiment, the long parallel walls 22 are recessed inward along the entire length of the pipe bar, and the two outer edges in the longitudinal direction are provided with outwardly convex bends 28. The pipe bar with the recessed trapezoidal profile 18 turned out to be excellent and is made from a circular pipe template having a diameter of 18 mm (circumference 56.55 mm). The depth of the recess 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 overall formed pallet container, the wall thickness of the pipe bar is 1 mm and the depth of the recess is 1 mm. Welding to each of the four contacts of each intersection of the pipe bars is carried out by electrical resistance pressure welding. When four points of welding are performed, the intersecting cage bars are pressed against each other by approximately 1 mm so that the opposing parallel walls 22 of each intersection continue to be spaced apart from each other by approximately 0.5 mm to 2 mm, preferably approximately 1 mm, to contact each other after welding. I never do that. (Distance A = 1 mm). This is a particularly important aspect because pallet containers are sometimes stored outdoors and exposed to weather. By cage bars spaced apart from each other at the weld point, the buildup is substantially prevented by exposing rain to air to dry. Welding surfaces that are in contact with each other are inevitably rust-prone and can be severely corroded to the entire cage for a short time. Also, the illustrated cross section is approximately equal to the width B1 of the short parallel wall 20 opposite the width of the long parallel wall 22 existing between the edge 28 portions provided with the outwardly convex curved portion 28. It is clearly shown.

In Fig. 5 , the change of the bending deformation of the cage jacket due to the dynamic vibration stress is schematically represented. The hydrostatic pressure of the loaded fluid product, illustrated on the right, is the maximum cage deflection (D _a , D _i ) corresponding to approximately 33% of the cage height, which occurs at approximately the height of the center of gravity (S) of the loaded product. The outward amplitude at this height is approximately twice the amplitude of the inner, which is why the risk of the largest cracking of the cage pipe bar is present in the lower half region of the cage while vibration stress is applied.

Figure 6 schematically shows a partial cross-sectional view which illustrates a horizontal cross-section at the location of maximum deformation impact portion (D _a, D _i). Here there is no interference of the oscillating deformation in the outward direction while the inner fluid column encounters the opposing side wall. Thus, the lower circumferential horizontal bar 30 is subjected to large bending stresses, especially in the vicinity of the corner region 38.

FIG. 7 shows the intersection 36 of the vertical bar 32 and the horizontal bar 30 in a view inside the cage. Four welding points are displayed at the intersection part 36. The trapezoidal pipe profile consisting of the horizontal bar 30 and the vertical bar 32 is provided with a cross section 36 and one recess 34 on each side immediately near the four welding points, respectively. 34 is spaced apart at the point of the intersection 36 by at least 1/10 of the pipe bar width B. FIG. FIG. 8 shows a diagram D of an undeformed trapezoidal profile 18, and FIG . 9B shows an example of a cross section of the recess 34 along the CC line. The recess 34 of the pipe bar can be made on the side of the "long" parallel wall 22 (FIG. 9B) and / or on the side of the opposing "short" parallel wall 20 according to FIG. 9A . Thus, at least two recesses may be provided outside of the trapezoidal profile and / or two recesses may be provided between the intersections of the cage bars because numerous variations can be obtained. However, it is evident that the pipe bars of these embodiments are not depressed or deform only in their vicinity, not directly at the point of intersection or at each weld.

Reducing the height H of the profile, the depth T of the one recess 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 recess is approximately 33% of the profile height H. The longitudinal extension of the recess 34 along the bar should be in the range of approximately 1½ to 3 times the profile width B, and in a preferred embodiment the longitudinal extension of the recess 34 is the profile width B Is approximately twice the extension of.

FIG. 10 illustrates a known type of unstressed pipe profile with a square profile along the entire length of the bar. As illustrated in FIG. 11, it can be seen that after already undergoing a relatively short dynamic vibration stress, cracks are formed on the horizontal bar 30 at each welding point of the intersection.

The formation of cracks or individual rupture of the cage bars always occurs in the areas where the maximum tensile force acts or where the cage jacket is maximally convex. Vertical pipe bars are arranged inside the cage jacket and horizontal pipe bars are arranged outside. Cracks and breaks always occur in the area of the intersection immediately after the weld (see the circles indicated in FIG. 2). The cracks begin to form in the vertical pipe bar and always move inward from the outside with respect to the jacket and start out on the inside of the horizontal bar and move outward. In comparative tests, a cage jacket made from a cage bar with an open profile and provided with an outwardly angled edge provides good load capacity because the weld is relatively far within the intersection but the cage jacket is vibrated. It was found to respond worst to stress.

In FIG. 12 a closed trapezoidal pipe profile 18 according to the invention is shown in which the horizontal bar 30 is provided with two recesses 34 in order to compare with the square pipe profile. As illustrated in the exaggerated manner in FIG. 13 , no cracks were formed even after prolonged exposure to vibrational stress. On the other hand, this is due to the intersecting area at the welding point without the recesses leading to fragility, while the recesses 34 reduce the bending cross-sectional coefficient when they are placed at a minimum distance from the intersections and the "bending hinge "As a kind of function, it prevents impacts on weak welds at maximum tension and prevents them from sagging toward ductile regions farther away.

The concave portion acting as a predetermined bending point means that the height H of the pipe bar profile is reduced, and serves to reduce the stress against the vibration stress generated at the weak weld point where the critical stress is maximum while the bending stress is changed. . Thus, in the event of dynamic vibration stress, the maximum critical tensile force propagates away from the welding point to an adjacent area of a certain distance thereto. Due to this special construction, on the weld connection by the concave of the pipe bar provided laterally near the welding point, the maximum stress is reduced so that no welding point is provided in the deformation zone to maintain their high flexural strenth. The static or dynamic stress of is substantially reduced.

A particular problem with configuring certain embodiments of cage jackets is that, for example, vertical and horizontal cage bars should be as stable and robust as possible to prevent excessively convex pallet containers applied by internal pressure. In order to offset the constant dynamic vibration stress, a high bending cross section modulus must be provided, in which the two criteria mentioned above must act in opposite forms. Consideration should be given to the appropriate, ie low production costs, while finding the optimal solution. Thus, according to a recent trend of the present invention, known pallet containers with cage bars having a flat profile along the length of the bar, for example as in DE 297 19 830 U1, carry dangerous fluid loads subject to dynamic vibration stresses. It is not suitable as a container. That is, it is suitable as a storage container but not as a transport container subjected to dynamic vibration stress. The above-mentioned patent publication is based on the prior art in connection with a known pallet container having a cage jacket made from a pipe having a circular cross section at least provided with a recess at the intersection of the welded pipe. The content of page 2 of the patent publication referring to the "avoiding localized tensile forces accumulation by using the profile pipe according to the present invention (without localized recesses) ..." Not exactly mentioned, it simply shows that the cage jacket of the pallet container should take into account the opposing relationship between flexural stiffness and vibrational elasticity if it is intended to transmit stress.

The depth T of the recess 34 of the trapezoidal profile according to the invention is approximately 25% to 50%, preferably approximately 33% of the height H of the pipe bar profile. Generally, a 5 mm recess (= 33%) is suitable for a pipe having a height of 15 mm, whereby the vibration stress at the welding point is kept low or eliminated, while the pipe can maintain a sufficiently high rigidity. This stiffness is important in order to keep the oscillating cage at a low level in the lateral convex vibration.

FIG. 14 illustrates an embodiment with two recesses 34 on the side of the pipe bar profile facing away from the weld point of the short parallel wall 20, as shown in FIG . 15 , a modification of this embodiment. One particularly useful variant is illustrated. The trapezoidal pipe profile is provided with recesses 34 on each side of the short parallel wall 20 and the long parallel wall 22 laterally near the intersection 36 so that the recesses exactly face each other. Here, the recess is spaced from the intersection 36 at a distance of approximately 1/10 of the pipe bar profile width B. FIG. Placing the recesses 34 in each of the short parallel walls and the long parallel walls 20, 22 extending in parallel enhances, in particular, the "hinge effect" or elasticity of the pipe profile.

According to the technical content of the present invention, the structure of the recesses 34 of the horizontal and vertical bars 30 and 32 may be configured at different depths depending on the strength of the dynamic stresses applied on the cage jacket 14. Thus, depending on the specific needs or needs, while maintaining sufficient flexural stiffness, the optimum vibration resilience of the horizontal and vertical pipe bars is controlled in various areas of the cage jacket, for example on the long sidewalls or short front and rear walls of the pallet container. Can be.

FIG. 16 illustrates another important embodiment which reduces the adverse effects of dynamic vibration stress on horizontal pipe bars. In the corner area, the horizontal bars 30 of the cage jacket 14, which are bent at 90 ° and parallel to the vertical direction, are flattened so that they can also serve as hinged “bending joints”. In the corner area, the horizontal pipe does not need to have a large bending resistance, which is more important here is high elasticity. Particularly preferred test results are in a pallet container having a horizontal bar 30 which is flattened by at least 1/10 of the diameter 18 height H from the inside and / or outside in the corner region 38 of the support jacket 14. Obtained. In one of the actually fabricated embodiments, the horizontal pipe of the lower region of the cage jacket is flattened by approximately 20% from the inside and approximately 35% from the outer corner arc, while the flats of the upper region of the case jacket are gradually reduced. It is configured to be.

17 shows the intersection of two pipe bars with a special square profile 42. Here, in the case of a bar, the pipe wall is slightly recessed along its entire length to obtain a four point contact at the intersection of the pipe bars, whereby the pipe bars are welded to each other. A recess is shown in the cross section along plane CC. FIG. 18 shows a pipe bar profile 44 similar to the above with vertical and horizontal pipe bars of square cross-section, where recesses partially created in one of the pipe walls are similarly created only in the region of the intersection. A four point contact is obtained in which two pipe bars intersecting each other are welded to each other. A cross section along plane BB also shows recess 34.

The vertical and / or horizontal pipe bars may have a closed profile with round, ie circular cross section. 19 shows the circular profile 46 with a recess 34 along the section line AA. In yet another embodiment, it may have an open profile with a trapezoidal cross section. 20 illustrates an open trapezoidal profile 48 with recesses 34 along the section line DD.

Finally, in Fig. 21, another circular pipe profile 50 is shown, in which case the intersecting pipe bars are only partially recessed in the area of the intersection 52 so that a favorable four-point contact is obtained. The two pipe bars are welded together. Here, predetermined bending points, i.e., recesses 34, are provided on the surface opposite the welding point.

It is to be understood that the variations as shown may be combined in various ways and other combinations are also within the scope of the present invention.

Possible variants described above, in particular the lower region of the cage jacket, can be provided with various means for obtaining sufficient flexural strength with an optimum suitable pipe bar elasticity.

Explanation of symbols for main parts of the drawings

10 pallet container

12 inner container HD-PE

14 cage jacket

16 Bottoms Palette

18 trapezoidal profile

20 short parallel walls

22 long parallel walls                 

24 straight inclined walls

26 crowns each

28 Convex (protrusion)

30 horizontal bars

32 vertical bar

34 recesses (30,32)

36 intersections (30,32)

38 corner arc (30)

40 flat parts (38)

42 square profile Ⅰ

44 Square Profile Ⅱ

46 Round Profile Ⅰ

48 open trapezoidal profile

50 round pipe bar profile Ⅱ

52 intersections (50)

A distance (22-22)

B pipe profile width

B ₁ reduced width (22)

H pipe profile height                 

S load gravity point

T recess 34 depth

D _a outer deformation

D _i inner deformation

Claims (19)

Pallet container 10 having a thin-walled inner receptacle 12 made of thermoplastic material for the storage and transportation of a fluid or free-flowing product, the inner container 12 serving as a support casing Surrounded by an outer cage jacket (14) and a bottom pallet (16) on which the thermoplastic container is supported; The cage jacket (14) is a pallet container consisting of vertical and horizontal bars (30, 32) welded together at an intersection (36), The vertical and horizontal bars 30, 32 have no recesses in their contact planes in the intersecting area, and each of the vertical and horizontal bars is laterally near the intersection 36, i. And at least one concave portion (34) at a predetermined distance from said predetermined distance is at least one tenth of said pipe bar profile width (B). The method of claim 1, The pallet 30 or the horizontal bar 32 is characterized in that at least two recesses 34 are provided between two intersections, on their contact plane side or on the side opposite the contact plane. container. The method according to claim 1 or 2, The depth T of the recess 34 which reduces the height of the profile is kept as small as possible in the range of 15% to 50% of the pipe bar profile height H. The method according to claim 1 or 2, Pallet container, characterized in that the longitudinal (longitudinal) extension of the recess (34) is in the range of 1½ to 3 times the width of the profile (B). Claim 5 was abandoned upon payment of a set-up fee. The method according to claim 1 or 2, Said vertical and horizontal bars (30,32) having a closed profile with a rectangular cross section. Claim 6 was abandoned when the registration fee was paid. The method according to claim 1 or 2, Said vertical and horizontal bars (30,32) having a closed profile with a round shape, each with a circular cross section. delete delete delete delete delete delete delete delete delete delete delete delete delete

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