RU2463513C2 - Overhead tank for system of transport vessels - Google Patents

Abstract

FIELD: machine building.

SUBSTANCE: overhead tank with body 1 consisting of parallel partially cylindrical shells 2, 4 that make chute 8, 10 extending in longitudinal direction. Chute end faces are closed by convex bottom 16, 18. Note here that expansion element 6, 6a, 6b made up of flat wall is arranged between said shells 2, 4. Top edge 12, 14 of said element extends into chute top while bottom edge penetrates through bottom chute area 8, 10. Expansion element 5 joints shells 2, 4 together shell element 42 extending in lengthwise direction rigidly coupled, at least at separate section, with shells 2, 4 and, partially, with flanged edges 12, 12a, 14, 14a of expansion element 6 to make bearing structure in chute area 8, 10. Invention covers also system of transport vessels, particularly, tank module 100 furnished with above described overhead tank 1.

EFFECT: higher strength.

11 cl, 12 dwg

Description

The invention relates to a pressure tank with a groove formed in parallel, forming a longitudinally extending groove, located next to each other, having the shape of cylinder parts of the shells with a housing, the end ends of which are respectively closed with a convex bottom. A pressure tank with partially circular cylindrical shell casings, the cross-section of which resembles a lying figure eight, is known, for example, from DE-A-36 06 247, DE-A-31 25 963, DE-A-29 51 554 and EP 10 67 326 IN 1. Such pressure tanks are intended, in particular, for the transport capacities of road vehicles, such as a tank trailer, or for tank container systems, in which tanks are required, which use a structural space with a reduced height and which are at the same time small, facilitating weight reduction by material consumption should provide high strength under pressure.

The best strength under the influence of pressure has a round-cylindrical cross section, in which, however, the rectangular cross section of the structural space with horizontally extending longitudinal sides is still not used enough. Such a cross-section of a structural space with a reduced height, for example, is also filled with several adjacent, durable under pressure, tanks having the shape of a full round cylinder (Fig. 10). Even with this design, space losses are still high. "Suitcase shape", elliptical (11) or oval cross-sections (Fig) do not have the necessary strength under pressure.

Therefore, pressure tanks have been developed according to the restrictive part of paragraph 1. These tanks have significant advantages with respect to the use of space in comparison with pressure tanks having the shape of a full round cylinder and are superior in pressure technology to “suitcase-shaped” or oval cross-sections of tanks that, in particularly used for petroleum products; however, they use space worse. In particular, for long pressure vessels it is advisable and in some respects even to provide for tensile elements between the partially cylindrical shells in order to connect the grooves to each other, taking into account the pressure technique. In this case, a tensile element made in the form of a flat wall, which protrudes into or penetrates into the upper or lower groove region, is especially simple to manufacture (see, for example, EP 10 67 326 B1). In this case, partially cylindrical shells, for example, located opposite each other, are installed on this wall and connected, respectively, welded with it.

There is a task to further improve such pressure tanks, equipped with a housing of partially round-cylindrical shells, with regard to the use of their space and / or their strength under pressure.

This problem is solved by a pressure tank according to paragraph 1, in which a shell element is provided that connects the shell shell and the tensile element. In this case, this sheath element covers the groove region, on the upper side as a roof element, and on the lower side as a bottom element, and forms with these elements, respectively, closed regions, a profile supporting structure in the intermediate region, which additionally stabilizes both with respect to internal and external pressure loads, and in relation to the loads associated with the movement of the tank.

For applications where a double casing is necessary, for example, for tanks that must be suitable for storing hazardous products, without the use of special design measures, such as trapping baths, the measure according to point 2 is used.

Due to the convexities extending in the longitudinal direction (here we mean the cylindrical / prismatic convexity around the longitudinal axis), respectively, to the aberrations, the stability (stability) of the shape of the shell elements is further enhanced (point 3).

According to paragraph 4, it is provided to close the region, which is formed from various contours of the openings of the convex bottom and shell (shell shells), with an intermediate element passing perpendicular to the longitudinal axis of the tank.

Additional stabilization occurs when, according to paragraph 5, the intermediate elements are respectively connected also to the end ends of the tensile element.

From the point of view of pressure and manufacturing techniques, such an intermediate element according to claim 6 is preferred; in particular, when it corresponds (follows) to the outer contour region of the inner circumferential contour of the convex bottom, that is, it can be inserted into it, and has an inner contour region that extends inwardly beyond the grooved region into the inner part of the tank, so that it is located on the side end wall, the circumferential contour of the shell of the body always passes along the surface of the intermediate element facing it. At the same time, the housing formed from the shell shells with its end ends can be respectively cleanly seated on the open end of convex bottoms, into which the corresponding intermediate elements are flush with the edge, without the need for additional adjustment or cutting operations. In this case, the contour regions meet at an acute angle in the arch, respectively, plantar regions of the shell membranes and provide there a reinforcement, which is preferable from the point of view of pressure engineering, which perceives the voltage peaks due to the internal pressure of the reservoir.

According to paragraph 7, this reinforcement is further improved and the stress peaks are smoothed out even more when rib-like elongations are provided at the ends of the intermediate elements, which, practically corresponding to the general circumferential contour of the bottom and shell of the body, extend beyond the arch, respectively, bottom area, in which stress peaks occur .

According to paragraph 8, the shell of the body have differently curved circumferential sections. Moreover, in particular, the bends in the upper and lower grooved regions are less, that is, with a wider bending radius than the bends of the circumferential sections that connect the upper husk with the lower plantar region of the shell membranes and form the lateral waist regions of the reservoir. Thanks to this measure, it is possible to reduce the depth of the groove that occurs at the junction between the partially cylindrical shells of the housing extending in the longitudinal direction, and at the same time increase the usable volume of the pressure tank without significantly reducing the pressure strength. At the same time, it is easier to attach a convex bottom, the opening of which covers this small grooved region, since the difference between the cross section of the bottom hole and the cross section of the body hole is reduced.

Additionally, the bends can also vary relative to each other in the upper and lower grooved region. This means that the depth of the groove on the bottom of the tank is different than on the top. A stronger bend - a smaller radius - leads to a deeper groove, and a smaller bend - a larger radius - leads to a flatter groove. A flatter groove in the lower region may, for example, be appropriate for the complete emptying of the adjacent plantar regions of the individual shell membranes. A deeper groove, on the other hand, gives such a pressure tank in this area a higher shape stability, so that it, for example, can be mounted on supports by means of saddle profiles running along the soles of the tank, e.g.

According to clause 9, different wall thicknesses in separate circumferential sections can also be provided.

Clause 10 relates to a system of transport containers, which is equipped with a pressure tank according to the invention.

Embodiments of the present invention are described below with reference to the drawings. They show:

figure 1 is a perspective view of a pressure vessel according to the invention,

figure 2 is a perspective view of a cross-section (section A-A) of the pressure tank shown in figure 1,

figure 3 is a perspective view of an image of a longitudinal section (section B-B) shown in figure 1 pressure tank,

figure 4 is a perspective view of the pressure tank shown in figure 1, in which the end bottom is lowered,

5 is a perspective view of the pressure tank shown in FIG. 4 without intermediate shields,

6 is a perspective view of the middle wall with inclined intermediate elements,

7 is a view of an alternative intermediate element in two alternative embodiments,

Fig. 8 is a schematic representation of two alternative cross-sectional embodiments of a cylindrical section of a tank,

Fig.9 is a block of the tank container with the tank corresponding to the invention,

figure 10 is a double cylindrical cross section according to the prior art,

11 is an elliptical (left half) and "suitcase-shaped" (right half) cross-section according to the prior art,

12 is an oval cross-section according to the prior art.

1 to 5, the pressure tank 1 includes two partially cylindrical shells 2, 4 of the housing, which, as can be seen in FIGS. 2 and 5, are longitudinally welded with a tensile element made in the form of a flat wall 6. The flat wall 6 has the same length as the partially cylindrical shell 2, 4 of the housing.

Each of the shells 2, 4 of the housing includes differently curved circumferential sections 2a, 2b, 2c or, respectively, 4a, 4b, 4c. The circumferential sections 2a and 4a extend from the joint with the flat wall 6 to the husk 7 of the respective shells 2 and 4 of the body. Starting from the shelves, the circumferential sections 2b and 4b, respectively, extend to the lower plantar lines 9 of the shells 2, 4 of the body, from which the circumferential sections 2c and 4c extend to the flat wall 6. Moreover, the circumferential sections 2b and 4b in the waist region have a radius of curvature of 600- 1300 mm, while the upper and lower circumferential sections 2a, 2c and 4a, 4c have a radius of curvature of 600-3000 mm.

These radius ranges are indicated for tank containers or vehicles with a maximum width of 2600 mm. With other sizes, accordingly, other ranges and ratios of radii are possible, which in this case are adapted to the actual overall dimensions of tank containers or vehicles (railroad, truck).

The circumferential sections 2a and 4a form the grooved region 8, and the circumferential sections 2b and 4b form the grooved region 10. The upper end 12 and the lower end 14 of the flat wall 6 extend into the grooved regions 8 and 10; the lower end 14 reaches the plane defined by the plantar lines 9 of the shell 2 and 4 of the plane, and the upper end 12 extends beyond the plane defined by the hoses 7 of the shell 2 and 4 of the shell. Both ends 12 and 14 for stabilization are provided with a flange 12a or, respectively, 14a. The flat wall 6 is provided with a through hole 50, which is reinforced with a flange 52.

The ends of the shells 2 and 4 of the body are closed by convex bottoms 16 and 18 (FIGS. 1 and 3), which, in turn, can be inserted into the frame 22 of the container by means of the end ring 20 adjacent to them (FIGS. 1 and 9).

For alignment and concealment of the difference in cross-sections between the grooved regions 8 and 10 and the oval bottom cross-section, there are respectively provided intermediate elements 24 and 26, which are located across the longitudinal direction in the form of flat shields. In the illustrated embodiment, the lower intermediate members 26 are respectively provided with an outer contour region 28 (FIG. 4), which corresponds to a straight inner portion of the circumferential contour of the convex bottom 16 and 18 and extends between the two plantar lines 9 of the partially cylindrical shells 2 and 4 of the body. The inner contour region 30 extends inside the circumferential contours defining the circumferential region 10 of the circumferential regions 2c and 4c. The outer contour region 28 and the inner contour region 30 extend almost at an acute angle to each other and meet at the ends 32, which are located in the zone of the plantar regions (plantar lines 9).

At the upper intermediate element 24, the outer contour region 34 also corresponds to the straight upper portion of the circumferential contour of the bottoms 16 and 18 and extends with its inner regions 36 of the inner contour to the ends 38, which similarly end at the lower intermediate elements 26 in the arch areas (husks 7). While the lower intermediate elements 26 are completely located inside the bottom contour 1, the outer contour region 34 of the upper intermediate element 24 extends beyond the bottom contour and extends outside it at almost the same level as the flange 12a.

Figure 6 shows an example implementation (shell 2, 4 of the tank is not shown), which provides intermediate elements 24a, 26a, which also extend across the tank, but are inclined in the longitudinal direction. This embodiment allows in some areas to shorten the employee working by the tensile element flat wall 6 and thus save material and reduce weight. At the upper protruding intermediate element 24a from the tank, an outer contour region 34a is flanged, which is thus connected (welded) to the flanging 12a and the end 12 of the flat wall 6.

In the shells 2 and 4 of the housing, holes 40 are provided in which typical tank connections are inserted, such as an inspection hole, filler pipes, ventilation pipes, and safety valve pipes (see FIG. 4).

An additional casing element 42 is provided in the tank vault, which is welded to the casing shells 2 and 4 by its lateral edges 44 in the arch areas, and by its end ends 46 to upper intermediate elements 24, at least in separate sections. In the middle of the sheath element 42, a flange 47 extends in the longitudinal direction, which practically lies on the flange 12a and is attached to it by cork seams 48. In this case, the circumferential sections 2a, 4a, the upper end 12 of the flat wall 6 with the flange 12a and the sheath element 42 form a stabilizing longitudinal a bearing assembly that is closed at its ends by upper intermediate elements 24 and thus is further stabilized.

Shell 2 and 4 of the body are covered in the illustrated embodiment (FIGS. 1, 2 and 4) with a double shell 5, which accordingly ends in the upper region (practically at the maximum level of filling) of the pressure tank 1 and completely covers the plantar regions 2b, 4c and together with the lower groove area 10, passing flat between the plantar lines 9. This double shell 5 prevents the contents from escaping when the shells 2 and 4 of the body are damaged. It can be supplemented (not shown) by additional outer bottoms, which in this case also form a double shell in the region of convex bottoms 16 and 18. In the lower region, the double shell 5 for further stabilization can also be connected by cork seams with a flange 14a at the lower end 14 of the flat wall 6. Similar fixation is also possible in the plantar regions through intermediate layers inserted there (for example, double flaps) on the outside of the shells 2 and 4 of the housing, so that here in the lower groove region 10, a stabilizing supporting element is realized.

5, there is no double shell 5. In one of the embodiments not shown, a flat, convex, or flanged sheath element may be located in the lower groove region 10, which in this case defines a similar load-bearing structure as the upper sheath element 42.

In the depicted exemplary embodiment, the ends 32, 38 of the intermediate elements 24 and 26 extend respectively in the regions of the plantar, respectively, vaulted shells 2 and 4 of the body, which also simultaneously form transitions in which the straight circumferential sections of the bottoms 16 and 18 pass into curved circumferential sections. Therefore, from the point of view of the pressure technique, this point is especially critical. In particular, to further reduce stress peaks arising there under internal pressure, in the embodiment of FIG. 7, rib-shaped extensions 132a, 132b are shown which, corresponding to the general circumferential contour of the bottoms 16, 18 and the shells 2, 4 of the casing, extend beyond the hoses 7.

Moreover, in the embodiment “a” (on the left), the entire intermediate element 24 is enlarged and protrudes by the region 132a behind the left hook 7. In the embodiment “b” (on the right), there is only one tab 132b that protrudes beyond the hook 7.

On Fig presents other options for the cross section, in which the cylindrical region of the shell, which includes shell 2, 4 of the housing and a flat wall 6, consists of one (version A) or, accordingly, two (version B) parts, when this, respectively, the flat regions 6, 6a, 6b are flanged on the convex hulls 2, 4 of the body, and the ends of the shells are respectively welded to the edge lines 102, 104. The two-piece design B includes two shell elements 2, 4 with a correspondingly flat partial region 6a, 6b. In this design, the ends of the shells of the body are also welded to the edge lines 102, 104, and the flat partial regions 6a, 6b are welded to each other in the longitudinal direction of the tank (along the seam 106).

There are also embodiments (not shown) in which the shells of the body not only have independent radii of curvature, but which also have different wall thicknesses in separate circumferential sections. Due to this, with wider (larger) radii of curvature, it is possible to equalize, as a rule, higher pressure loads. This load-bearing design allows additional weight reduction or, accordingly, allows higher pressure loads.

For such tanks, which are equipped with a double shell 5, this outer shell 5 can also be used as an effective structural element, perceiving pressure loads. A prerequisite for this is the force transfer connection between the inner tank and the outer tank. This happens, for example, through a support grid (not shown) provided between the inner and outer walls, which allows the force to be transmitted pointwise or linearly between the walls of the tank. At especially problematic points, additional nodal shields for connection (not shown) can also be provided, which make it possible to especially efficiently divert the load peaks arising on the inner wall into the outer wall.

Fig. 9 shows a pressure tank 1 installed in a module of a tank container in which it is connected to this module by end rings 20. The illustrated module 100 of the tank container is designed for hook-mounted lifting devices and includes loading rails 101 and an aggregate room 102, as well as the module 103 of the folding railing, so that the illustrated module can be used as a practically independent autonomous supply unit.

Other options and executions of the present invention can be found in the content of the claims.

Claims (11)

1. A pressure tank (1) with a housing formed from parallel, forming a longitudinally extending groove (8, 10) located next to each other partially cylindrical shells (2, 4), the end ends of which are respectively closed by a convex bottom (16, 18 ), and between the partially cylindrical shells (2, 4) is located, made, in particular, in the form of a flat wall (6; 6a; 6b), a tensile element whose upper or lower edges (12, 14) protrude into the upper, respectively lower grooved areas (8, 10), respectively they permeate it, characterized in that a connecting shell (2, 4) of the housing and a tensile element (6) are provided, a longitudinally extending shell element (42), which is rigidly connected to the shells at least in separate sections ( 2, 4) of the housing and, in particular, with a flanged edge (12, 12a; 14, 14a) of the tensile element (6), so that a support structure is formed in the groove region (8, 10). 2. Pressure tank (1) according to claim 1, in which the shell element (42) is an integral part of at least partially covering the shell (2, 4) and the outer shell (36) tightly connected to it. 3. The pressure tank (1) according to claim 1, wherein the shell element (42) is provided with a convexity extending in the longitudinal direction, respectively, with a flange (47). 4. The pressure tank (1) according to claim 2, in which the contour of the opening of the convex bottoms (16, 18) in the groove area is other than the contour of the opening of the shells (2, 4) of the housing, and the region thus defined is closed by a plane passing in one a plane perpendicular to the longitudinal axis of the tank, an intermediate element (24; 26). 5. Pressure tank (1) according to claim 4, in which the intermediate element (24; 26) is rigidly connected to the end end of the tensile element (6; 6a; 6b) and the shell element. 6. The pressure tank (1) according to claim 4, in which the intermediate element (24; 26) has an outer contour region (28; 34), which in the groove region (8, 10) corresponds to the inner circumferential contour of the convex bottom (16, 18 ), and the region (30; 36) of the inner contour, which passes in the groove region (8, 10) inside the circumferential contour of the shells (2, 4) of the casing, while both regions (28; 34; 30; 36) of the contour converge in in the arch, respectively plantar areas (7, 9) ends (32; 38) and pass almost at an acute angle to each other. 7. Pressure tank (1) according to claim 4, in which the ends (32; 38) of the intermediate element have rib-shaped extensions (132a, 132b), which, corresponding to the general circumferential contour of the bottoms (16, 18) and shells (2, 4) cases, go beyond the arch, respectively, the plantar region (7, 9). 8. Pressure tank (1) according to claim 1, in which at least one shell (2, 4) of the housing has differently curved circumferential sections (2a, 2b, 2c; 4a, 4b, 4c), in particular one circumferential section (2a, 2c; 4a, 4c) in the upper, respectively lower arch areas (8, 10) and one circumferential section (2b; 4b) between the arch and plantar areas (7, 9), while the circumferential section (2b ; 4b) between the arch and plantar regions (7, 9) is more bent than the circumferential section (2a, 2c; 4a, 4c) in the upper, respectively lower grooved areas (8, 10), and / or the circumferential section (2a; 4a ) in the upper kovoy region (8) is bent stronger / weaker than the circumferential portion (2c, 4c) on the bottom of the flute area (10). 9. Pressure tank (1) according to claim 8, in which the circumferential sections (2a, 2b, 2c; 4a, 4b, 4c) have different wall thicknesses. 10. The system of transportation containers equipped with a pressure tank (1) according to one of claims 1 to 9. 11. The system of transportation containers according to claim 10, characterized in that it is made in the form of a module (100) of the tank container.

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