Tank system

Abstract

A tank system (10) for a transport system, in particular for a motor vehicle, for receiving a gaseous or liquid medium (12), preferably liquefied petroleum gas (LPG), comprises an inner tank (14) for receiving the medium and an outer tank (16), wherein the inner tank is supported in the outer tank by means of a floating bearing (21) with a floating bearing element and a fixed bearing (23) with a fixed bearing element, forming a gap (18). The floating bearing is designed such that it allows translational movement and / or expansion of the inner tank relative to the outer tank in an axial direction. The floating bearing element and / or the fixed bearing element consists at least partially, and in particular entirely, of plastic.

Description

[0001] The invention relates to a tank system for a transport system, in particular for a motor vehicle, for holding a gaseous or liquid medium, preferably liquefied gas.

[0002] The tank system according to the invention is a tank system for accommodating a gaseous or liquid medium, with which the transport system itself can be operated. However, it can also be a tank system with which the transport system transports a medium or delivers it to a specific location. The term "tank system" therefore refers to a system that can be integrated into a transport system and is designed to accommodate and / or deliver any type of gaseous or liquid media.

[0003] The gaseous or liquid medium can be any type of liquid or gas. The medium can, for example, be a fuel for operating a facility. This includes conventional fuels such as diesel or gasoline, but also so-called e-fuels or liquefied gas such as liquefied hydrogen (LH2) or liquefied natural gas (LNG). However, the medium can also be a medium to be transported in the chemical industry. The tank system according to the invention is particularly suitable for accommodating cryogenic media.

[0004] According to the invention, a transport system is understood to be a mobile system for transporting people and / or goods, such as a cargo bike, a motorcycle, a car, a truck, an aircraft, a train, and / or a ship, which can be powered by liquid or solid fuel or electrically. The transport system can, for example, be a motor vehicle that transports liquefied petroleum gas and / or is powered by liquefied petroleum gas.

[0005] The storage of liquefied gas places diverse demands on the tank system, as the medium must often be stored at cryogenic temperatures. Conventional tank systems for such applications are therefore usually double- or multi-walled, meaning they comprise an inner tank for containing the medium and at least one outer tank. The inner tank is mounted within the outer tank, forming an insulating gap. In this context, a mounting arrangement refers to a suspension, fixation, or mounting arrangement that reliably positions the inner tank within the outer tank and at a distance from it.

[0006] The design of the suspension or bearing is crucial for the quality of the tank system, as the bearing must withstand constant loads caused by internal and external influences. For example, it must be ensured that the bearing can withstand and / or absorb and compensate for external influences such as acceleration of the transport system, which can lead to relative deflection of the tanks, or road excitation, which can lead to vibrations of the bearing components.

[0007] In addition, there is usually a significant temperature difference between the inner and outer tanks. Since the bearing creates a connection between the inner and outer tanks, it forms a type of thermal bridge. To minimize heat loss, it is advantageous for this to have the lowest possible thermal conductivity. For example, partial evaporation of the stored medium due to undesired heating can lead to a loss of range of the transport system. In addition, there is usually a vacuum, especially a high vacuum, in the gap between the inner and outer tanks, which is why the bearing must also be suitable for (high) vacuum applications, i.e., it must not become brittle or outgas.

[0008] Furthermore, the space for the storage unit between the tank walls is limited, as the tank system as a whole must be as compact as possible to facilitate its integration. Furthermore, the tank system must be as economical and simple to manufacture as possible. Therefore, the tank system faces complex economic, mechanical, and thermodynamic requirements.

[0009] It is therefore an object of the present invention to provide a more economical, compact and robust tank system for a transport system.

[0010] This object is achieved according to the invention by a tank system for a transport system having the features of claim 1 and, in particular, in that the inner tank is mounted in the outer tank by means of a floating bearing with a floating bearing element and a fixed bearing with a fixed bearing element, forming a gap. The floating bearing is designed such that it permits a translational movement and / or an expansion of the inner tank relative to the outer tank in an axial direction. Furthermore, the floating bearing element and / or the fixed bearing element comprise a plastic. Preferably, the floating bearing element and / or the fixed bearing element are made of the plastic.

[0011] The inventive combination of floating and fixed bearings ensures that the inner tank is securely fixed in the outer tank, while simultaneously efficiently compensating for external and internal influences acting on or within the tank system. The bearings can, for example, compensate for forces and moments due to travel movements of the transport system, expansion and / or contraction of the inner tank due to temperature or pressure differences, and manufacturing tolerances. The tank system is therefore particularly durable and robust.

[0012] In addition, plastic is a cost-effective and easy-to-process material, so that the bearing elements are cheap and easy to manufacture, which is why the tank system according to the invention is characterized by improved economic efficiency.

[0013] It should be noted that the floating bearing element and / or the fixed bearing element can be hybrid components that comprise other materials in addition to plastic. For example, an axial end section of the elements that is in contact with one of the tanks can be made of metal to simplify fastening of the element. It is also conceivable for both axial end sections to be metallic, with a plastic section extending between them.

[0014] The plastic can be molded onto metallic components of the elements or attached in another way.

[0015] Further embodiments of the invention are set forth in the claims, the description and the accompanying drawings.

[0016] The plastic can be polyetheretherketone (PEEK), a high-strength and easy-to-process material with excellent mechanical and thermodynamic properties. PEEK is particularly suitable for low-temperature and / or high-vacuum applications because it does not become brittle or outgas under these conditions.

[0017] The plastic preferably has a thermal conductivity of less than 1.0 W / m*K, in particular less than 0.5 W / m*K, preferably 0.25 W / m*K. This minimizes heat transfer from the outer tank to the inner tank, resulting in the inner tank heating up only very slowly or hardly at all. This, in turn, prevents the inner tank from expanding due to heating and makes the tank system more energy-efficient overall.

[0018] For a particularly long-lasting and resistant design of the bearings, the plastic can have a modulus of elasticity between 3000 and 5000 MPa, in particular between 3600 and 4800 MPa, preferably between 4100 and 4300 MPa.

[0019] Furthermore, the inner tank can have a cylindrical basic shape, with its longitudinal axis running parallel to the axial direction. Additionally or alternatively, the outer tank can also have a cylindrical basic shape, with its longitudinal axis running parallel to the axial direction. In particular, the inner tank and the outer tank can be arranged coaxially, which allows the tank system to be better integrated into or mounted on the transport system.

[0020] The floating bearing and the fixed bearing can be arranged on opposite sides of the inner tank, in particular centrally on the longitudinal axis.

[0021] For particularly stable mounting of the inner tank in the outer tank, the loose bearing element and the fixed bearing element can be arranged coaxially, in particular coaxially with the axial longitudinal axis of the inner tank and / or the outer tank.

[0022] The fixed bearing element and the loose bearing element can each have a base body and at least one conical fastening section.

[0023] In particular, the loose bearing element can have exactly one conical fastening section, wherein the loose bearing element can have a sliding seat section adjoining the base body and opposite the fastening section.

[0024] The sliding seat section may have a non-rotationally symmetric cross-section so that all rotational degrees of freedom of movement of the inner tank with respect to the outer tank can be efficiently locked.

[0025] The fixed bearing element, on the other hand, can have exactly two conical fastening sections opposite one another in relation to the base body.

[0026] In addition, the base body of the fixed bearing element and / or the base body of the floating bearing element can have a conical shape. The conical shape is a stress-optimized contour shape. It enables a homogeneous stress distribution and thus a uniform load on the bearing elements.

[0027] Additionally or alternatively, the base body of the fixed bearing element can have, at least in sections, a smaller wall thickness than the at least one fastening section of the fixed bearing element.

[0028] Accordingly, the base body of the floating bearing element can also have, at least in sections, a smaller wall thickness than the fastening section of the floating bearing element and / or the sliding seat section.

[0029] With a suitable choice of base body geometry, the stability of the corresponding bearing element is determined by its shape, allowing for thinner wall thicknesses compared to conventional designs without compromising the reliability of the bearing. A thinner wall thickness also reduces the thermal conductivity of the component, thus improving the insulation between the tanks.

[0030] Furthermore, the floating bearing and the fixed bearing can each have at least one flange element and the fastening section can be fixed axially and rotationally fixed to the flange element.

[0031] In particular, a clamping connection can be formed between the fastening section and the flange element using a clamping ring and / or a conical nut. This enables a firm yet material-friendly fixation of the bearing elements in the bearings.

[0032] The sliding seat section of the floating bearing element can be mounted in a rotationally fixed but not axially fixed manner in or on a guide sleeve of the floating bearing, the cross-section of which is preferably complementary to that of the sliding seat section. The guide sleeve can be a component of any design onto which the sliding seat section can be slidably attached or into which the sliding seat section can be slidably inserted. The guide element preferably has a non-rotationally symmetrical cross-section complementary to the sliding seat section, so that all rotational degrees of freedom of movement of the sliding seat section relative to the guide section (and thus ultimately rotational movement components of the tanks relative to one another) can be efficiently blocked.

[0033] In addition, for optimal use of installation space, the flange element and / or the guide sleeve can extend at least partially, preferably completely, into the interior of a base body of the inner tank. For example, the inner tank has a corresponding recess or similar feature into which the flange element and / or the guide sleeve extend. Since, in this design, parts of the floating bearing and / or the fixed bearing are accommodated by the basic shape of the inner tank, the tank system can be designed to be particularly compact.

[0034] The invention is described below by way of example using advantageous embodiments with reference to the accompanying figures. They show, schematically: Fig. 1 shows a cross-sectional view of a tank system according to the invention; Fig. 2 shows a perspective view of a movable bearing element; Fig. 3 shows a perspective view of a fixed bearing element; Fig. 4 shows a cross-sectional view of the tank system in the region of the movable bearing; and Fig. 5 shows a cross-sectional view of the tank system in the region of the fixed bearing.

[0035] The Figure 1 The tank system 10 shown for a transport system comprises an inner tank 14 and an outer tank 16. The inner tank 14 is mounted in the outer tank 16 by means of a loose bearing 21 and a fixed bearing 23, forming a gap 18.

[0036] The interior of the inner tank 14 contains liquefied gas, such as liquefied hydrogen or liquefied natural gas. Accordingly, very low or even cryogenic temperatures prevail inside the inner tank 14, for example, temperatures of less than 150 Kelvin, preferably less than 50 Kelvin, more preferably less than 10 Kelvin. A high vacuum, for example, a pressure between 10 -3 and 10 -7 mbar, preferably prevails in the gap 18, so that temperature equalization between the inner tank 14 and the outer tank 16 is minimized.

[0037] It is understood that instead of the liquefied gas, any type of liquid or gaseous medium 12 can be accommodated in the inner tank 14. Accordingly, a temperature of more than 150 Kelvin, for example, room temperature, can prevail in the inner tank 14, depending on the type and nature of the medium 12. Accordingly, a high vacuum is also optional. For example, a weak vacuum can be formed in the gap 18. However, ambient pressure can also prevail in the gap 18 and / or the gap 18 can be filled with an insulating liquid or a gas such as air or an inert gas, or with another insulating material.

[0038] The inner tank 14 and the outer tank 16 have a cylindrical basic shape, with their respective longitudinal axes running parallel to the axial direction I. Other shapes are also conceivable. For example, the inner tank 14 and / or the outer tank 16 can also have a spherical shape or other shapes.

[0039] The fixed bearing 23 is designed such that it essentially blocks all degrees of freedom of movement of the inner tank 14 relative to the outer tank 16, i.e., the inner tank 14 is fixed in the outer tank 16 in the region of the fixed bearing 23 in a rotationally fixed and tensile manner. The floating bearing 21 is also designed to prevent a rotational movement of the inner tank 14, but allows a translational movement and / or an expansion of the inner tank 14 relative to the outer tank 16 in the axial direction I.

[0040] The floating bearing 21 and the fixed bearing 23 are each arranged on opposite narrow sides 24, 26 of the inner tank 14, specifically centrally on the longitudinal axis of the cylindrical shape of the inner tank 14 and the outer tank 16, respectively. Accordingly, the inner tank 14 and the outer tank 16 are arranged coaxially. In particular, the inner tank 14 is arranged with respect to the outer tank 16 such that the gap 18 separating them has essentially the same width on an upper side 11 and on a lower side 13 of the inner tank 14. However, the floating bearing 21 and the fixed bearing 23 can also be arranged offset with respect to the longitudinal axis. Furthermore, a configuration is conceivable in which the floating bearing 21 and the fixed bearing 23 are each arranged centrally on the upper and lower sides 11, 13 of the inner tank 14.

[0041] Furthermore, it is understood that instead of exactly one movable bearing 21 and exactly one fixed bearing 23, two or more movable bearings 21 and / or fixed bearings 23 can also be provided for supporting the inner tank 14 in the outer tank 16. The translational degrees of freedom of the movable bearings 21 should be arranged parallel. For example, at least two fixed bearings 23 can be arranged in the region of the first narrow side 23 of the inner tank 14 and at least two movable bearings 21 in the region of the second narrow side 24 of the inner tank 14 and / or at least two fixed bearings 23 can be arranged in the region of the top side 11 of the inner tank 14 and at least two movable bearings 21 in the region of the bottom side 13 of the inner tank 14, or vice versa.

[0042] The floating bearing 21 has a floating bearing element 20 and the fixed bearing 23 has a fixed bearing element 22, each of which is described in detail below with reference to Figures 2 and 3.

[0043] The Figure 2 The floating bearing element 20 shown has—figuratively speaking—essentially the basic shape of a trumpet with inhomogeneous wall thickness. In the embodiment shown, the floating bearing element 20 comprises a base body 33, a conical fastening section 40 adjoining the base body 33, and a sliding seat section 38 extending in the longitudinal direction of the floating bearing element 20.

[0044] The sliding seat section 38 adjoins the base body 33, is arranged on a side of the base body 33 opposite the fastening section 40, and has a non-rotationally symmetrical cross-section. The cross-section of the sliding seat section 38 has a rotationally symmetrical shape, also referred to as a P3G shape. However, the cross-section of the sliding seat section 38 can also have any other non-rotationally symmetrical cross-section, for example, that of a rectangle or a triangle.

[0045] The base body 33 of the floating bearing element 20 has a contour in which the shape of the fastening section 40 smoothly transitions into the shape of the sliding seat section 38. However, the base body 33 can also have another suitable shape.

[0046] The base body 33 furthermore has a smaller wall thickness than the sliding seat section 38, whereby the inner tank 14 and the outer tank 16 are better insulated from each other (see also Fig. 4 ). Optionally, a thicker wall thickness can be provided in the area of ​​the fastening section 40 than in the area of ​​the base body 33 in order to provide sufficient fastening stability. Alternatively, the wall thickness of the floating bearing element 20 can also be constant.

[0047] The diameter 42 of the fastening section 40 of the floating bearing element 20, in particular measured at the end face of the fastening section 40, is larger than a radial dimension 44 of the sliding seat section 38 (see Figure 4 ). The diameter 42 of the fastening section 40 at its end face can, for example, be 1.5, two, three, or four times as large as the radial dimension 44 of the sliding seat section 38.

[0048] The Fig. 3 The fixed bearing element 22 shown has a rotationally symmetrical conical shape with varying wall thickness. In the embodiment shown, the fixed bearing element 22 comprises a conical first fastening section 28, a conical base body 32 adjoining the first fastening section 28, and a conical second fastening section 30 adjoining the base body 32.

[0049] The diameter 34 of the first fastening section 28 of the fixed bearing element 22 is smaller than the diameter 36 of the second fastening section 30 of the fixed bearing element 22, in particular measured at the respective end faces of the fastening sections 28, 30 (see Figure 5). The diameter 36 of the second fastening section 30 at its end face can, for example, be two, three, four, or five times as large as the diameter 34 of the first fastening section 28.

[0050] The base body 32 of the fixed bearing element 22 has a smaller wall thickness than the fastening sections 28, 30, whereby the inner tank 14 and the outer tank 16 are better insulated from each other (see also Fig. 5 ). However, the wall thickness of the base body 32 and the first fastening section 28 can also be less than the wall thickness of the second fastening section 30, or the wall thickness of the base body 32 and the second fastening section 30 can be less than the wall thickness of the first fastening section 28. Alternatively, the wall thickness of the fixed bearing element 22 can also be constant.

[0051] The floating bearing element 20 and the fixed bearing element 22 are made of a plastic or polymer. The plastic is preferably a semi-crystalline thermoplastic polymer. The plastic has a thermal conductivity of less than 1 W / m*K, in particular less than 0.5 W / m*K, preferably 0.25 W / m*K, and / or a modulus of elasticity between 3000 and 5000 MPa, in particular between 3600 and 4800 MPa, preferably between 4100 and 4300 MPa. This ensures optimal insulation between the inner and outer tanks 14, 16, while the bearings 21, 23 simultaneously exhibit a high degree of robustness. Furthermore, plastic is easy to process.

[0052] An example of such a plastic is a plastic from the polyether ketone family, such as polyetheretherketone (PEEK). This plastic is particularly well-suited for extreme operating conditions, such as those encountered in high-vacuum and low-temperature applications. PEEK also exhibits excellent mechanical and thermal properties. At room temperature, for example, PEEK has a thermal conductivity of approximately 0.25 W / m*K, a modulus of elasticity of approximately 4200 MPa, a tensile strength of approximately 110 MPa, and an elongation at break of approximately 11%.

[0053] As in Fig. 4As shown, a guide sleeve 46 of the floating bearing 21 is mounted on the outer tank 16, which partially projects into the interior of a base body of the inner tank 14. The floating bearing 21 also comprises a first bearing sleeve 48 mounted on the inner tank 14, to which a first flange element 50 is mounted. The first bearing sleeve 48 projects into the interior of the base body of the inner tank 14 and accommodates a significant portion of the floating bearing 21. As a result, the tank system 10 has a particularly compact shape. The guide sleeve 46 and the first bearing sleeve 48 are connected to the shells of the tanks 14, 16, for example by welding.

[0054] The guide sleeve 46 is designed for the movable mounting of the sliding seat section 38 and has a corresponding, non-rotationally symmetrical cross-section, which is complementary to that of the sliding seat section 38, such that the sliding seat section 38 is mounted in a guide sleeve 46 in a rotationally fixed but not axially fixed manner. Due to the complementary shape, the sleeve 46 and the section 38 lie flat against one another, so that a substantially uniform surface pressure is formed between the outer side of the sliding seat section 38 and the inner side of the guide sleeve 46. Put simply, the sliding seat section 38 can move or shift relative to the guide sleeve 46 in the axial direction I in the guide sleeve 46, but cannot rotate in the guide sleeve 46.As a result, all rotational degrees of freedom are locked, while any expansion or displacement of the inner tank 14 in the axial direction I as well as manufacturing inaccuracies are compensated.

[0055] The first flange element 50 closes off the first bearing sleeve 48 on the inner tank side in the axial direction I and comprises a conical mounting portion 52 for mounting the fastening portion 40 of the floating bearing element 20. Between at least part of the fastening portion 40 and the mounting portion 52, a clamping connection is formed by means of a first clamping ring 54, which is fixed to a base body of the first flange element 50 by means of one or more first screws 54. By means of this releasable clamping fixation, the floating bearing element 20 is firmly secured to the inner tank 14, but can also be removed quickly and easily, for example for maintenance work or to replace the floating bearing element 20.

[0056] As in Fig. 5As shown, the fixed bearing 23 comprises a second bearing sleeve 58 which is mounted on the inner tank 14, wherein a second flange element 60 is mounted on the second bearing sleeve 58 and closes off the second bearing sleeve 58 on the outer tank side in the axial direction I. The second flange element 60 has an internal thread 70 on the inner tank side and a conical third mounting section 76 adjoining it on the outer tank side. For a secure axially and rotationally fixed fixation of the fixed bearing element 22 to the inner tank 14, the first fastening section 28 of the fixed bearing element 22 is clamped at least in sections between the third mounting section 76 of the second flange element 60 and a conical nut 74, wherein the conical nut 74 is pressed onto at least part of the first fastening section 28 by means of a central screw 72 which is screwed into the internal thread 70 of the second flange element 60.

[0057] The fixed bearing 23 further comprises a third flange element 62 with a second conical mounting portion 64 for mounting the second fastening portion 30 of the fixed bearing element 22. Between at least a part of the second fastening portion 30 and the second mounting portion 64, a clamping connection is formed by means of a second clamping ring 66, which is fixed to a base body of the third flange element 62 by means of one or more second screws 68.

[0058] The second bearing sleeve 58 is mounted to the inner tank 14, for example, by welding. The same applies to the connections between the second flange element 60 and the second guide sleeve, as well as the third flange element 62 and the outer tank 16.

[0059] In the present embodiment, the bearing sleeve 58 has holes or recesses 78 to save material and reduce thermal conductivity.

[0060] Due to the releasable clamping of the respective fastening sections 28, 30, the fixed bearing element 22 is axially and rotationally fixedly secured to the tanks 14, 16, but can also be easily and quickly removed, for example, for maintenance work or to replace the fixed bearing element 22. However, other forms of fixing the respective fastening sections 28, 30, 40 are also conceivable, for example, an adhesive connection or fixing by means of screws in holes in the fastening sections 28, 30, 40.

[0061] It is understood that the arrangement of the fixed bearing 23 can also be the other way around, ie the second flange element 60 can also be mounted on the inner tank 14 and the second bearing sleeve 58 on the outer tank 16, including a correspondingly mirrored arrangement of the other components of the fixed bearing 23.

[0062] The floating bearing 21 can also comprise more than one floating bearing element 20, and the fixed bearing 23 can comprise more than one fixed bearing element 22, each with a corresponding number of the remaining components of the bearings 21, 23. For example, the floating bearing 21 can have two, three, or more floating bearing elements 22, and / or the fixed bearing 21 can have two, three, or more fixed bearing elements 22. In these cases, the floating bearings 21 are designed such that the degrees of freedom of displacement defined by them are arranged in parallel.

[0063] In principle, the fastening sections 28, 30, 40 can have anti-rotation features to create a rotationally fixed fixation not only through a clamping effect. Such features can be, for example, ribs, grooves, or similar, which interact with complementary features on the corresponding counterparts 74 and / or 76, 64 and / or 66 or 52, 54. A non-rotationally symmetrical shape of the aforementioned components can also provide anti-rotation protection. List of reference symbols:

[0064] 10Tank system 11Top of the inner tank 12Fuel 13Bottom of the inner tank 14Inner tank 16Outer tank 18Gap between inner and outer tank 20Loosening bearing element 21Loosening bearing 22Fixed bearing element 23Fixed bearing 24, 26Narrow sides of the inner tank 28, 30, 40Fastening sections of the bearing elements 32, 33Base body of the bearing elements 34, 36, 42Diameter of the fastening sections 38Sliding seat section 44Radial dimension of the sliding seat section 46Guide sleeve 48, 58Bearing sleeves 50, 60, 62Flange elements 52, 64, 76Conical mounting sections 54, 66Clamping rings 56, 68Screws 70Internal thread 72Central screw 74Cone nut 78Hole or recess Iaxial direction

Claims

1. Tank system (10) for a transport system, in particular for a motor vehicle, for holding a gaseous or liquid medium (12), preferably liquefied gas, comprising an inner tank (14) for holding the medium (12) and an outer tank (16), wherein the inner tank (14) is mounted in the outer tank (16) by means of a loose bearing (21) with a loose bearing element (20) and a fixed bearing (23) with a fixed bearing element (22) to form a gap (18), wherein the loose bearing (21) is designed such that it allows a translational movement and / or an expansion of the inner tank (14) relative to the outer tank (16) in an axial direction (I), and wherein the loose bearing element (20) and / or the fixed bearing element (22) is made at least in sections, in particular completely, of plastic, wherein the plastic is preferably polyetheretherketone.

2. Tank system (10) according to claim 1, wherein the plastic has a thermal conductivity of less than 1.0 W / m*K, in particular less than 0.5 W / m*K, preferably 0.25 W / m*K.

3. Tank system (10) according to one of the preceding claims, wherein the plastic has a modulus of elasticity between 3000 and 5000 MPa, in particular between 3600 and 4800 MPa, preferably between 4100 and 4300 MPa.

4. Tank system (10) according to one of the preceding claims, wherein the inner tank (14) has a cylindrical basic shape whose longitudinal axis runs parallel to the axial direction (I), and / or wherein the outer tank (16) has a cylindrical basic shape whose longitudinal axis runs parallel to the axial direction (I), in particular wherein the inner tank (14) and the outer tank (16) are arranged coaxially.

5. Tank system (10) according to one of the preceding claims, wherein the movable bearing (21) and the fixed bearing (23) are arranged on opposite sides (24, 26) of the inner tank (14), in particular centrally on the longitudinal axis.

6. Tank system (10) according to one of the preceding claims, wherein the loose bearing element (20) and the fixed bearing element (22) are arranged coaxially, in particular coaxially with the axial longitudinal axis of the inner tank (14) and / or the outer tank (16).

7. Tank system (10) according to one of the preceding claims, wherein the fixed bearing element (22) and the loose bearing element (20) each have a base body (32, 33) and each have at least one conical fastening section (28, 30, 40).

8. Tank system (10) according to claim 7, wherein the loose bearing element (20) has exactly one conical fastening section (40), wherein the loose bearing element (20) has a sliding seat section (38) adjoining the base body (33) and opposite the fastening section (40).

9. Tank system (10) according to claim 8, wherein the sliding seat portion (38) has a non-rotationally symmetrical cross-section.

10. Tank system (10) according to one of claims 7 to 9, wherein the fixed bearing element (22) has exactly two conical fastening sections (28, 30) opposite one another with respect to the base body (32).

11. Tank system (10) according to one of claims 7 to 10, wherein the base body (32) of the fixed bearing element (22) and / or the base body (33) of the loose bearing element (20) have a conical shape.

12. Tank system (10) according to one of claims 7 to 11, wherein the base body (32) of the fixed bearing element (22) has, at least in sections, a smaller wall thickness than the at least one fastening section (28, 30) of the fixed bearing element (22).

13. Tank system (10) according to one of claims 7 to 12, wherein the base body (33) of the floating bearing element (20) has, at least in sections, a smaller wall thickness than the fastening section (40) of the floating bearing element (20) and / or the sliding seat section (38).

14. Tank system (10) according to at least one of claims 7 to 13, wherein the movable bearing (21) and the fixed bearing (23) each have at least one flange element (50, 60, 62) and the fastening section (28, 30, 40) is fixed axially and rotationally fixed to the flange element (50, 60, 62), in particular wherein a clamping connection is formed between the fastening section (28, 30, 40) and the flange element (50, 60, 62) by means of a clamping ring (54, 60, 66) and / or a conical nut (74).

15. Tank system (10) according to one of claims 8 to 14, wherein the sliding seat section (38) of the movable bearing element (20) is mounted in a rotationally fixed but not axially fixed manner in a guide sleeve (46) of the movable bearing (21), the cross section of which is complementary to that of the sliding seat section (38), in particular wherein the flange element (50, 60, 62) and / or the guide sleeve (46) protrudes at least partially, preferably completely, into the interior of a base body of the inner tank (14).

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