Fitting for a fluid line connection and fluid line connection with such a fitting

Abstract

The present invention relates to a fitting (10) with an inner channel (13) for a fluid line connection (100), wherein the fluid line connection (100) comprises the fitting (10), a connecting nozzle (20) and a union nut (30).It is proposed that a base body (11) of the fitting (10) has an internal contour (IK) produced by primary forming and / or machining, which deviates at least in certain areas from a smooth through-bore such that, when the base body (11) is axially pressed into the connection spigot (20) during assembly by means of screwing by the union screw part (30), a deformation of the connection section (12) due to an angular deviation (Δ) from an outer cone angle (α) of a connection section (12) of the fitting (10) and an inner cone angle (β) in a connection bore (22) of the connection spigot (20) results in a circumferentially uniform deformation of the connection section (12) in a radial direction inwards.

Description

[0001] The present invention relates to a fitting for a fluid line connection, wherein the fluid line connection comprises: - the fitting, with any pipe connected to it and with a base body having a connecting section with an inner channel, which increases radially outwards from its connection end in a frustoconical shape with a conical angle and forms a circumferential sealing surface on its outer circumferential surface and has a shoulder with a stop surface adjoining this sealing surface, and - a connecting stub with a connecting thread and with a connecting bore which tapers from its opening in a frustoconical shape with a conical angle adapted to the conical angle of the sealing surface, and there forms a circumferential connecting surface on the inner circumference for contact with the sealing surface, as well as - a union nut with a clamping thread and a through-hole which has a circumferential clamping surface for interaction with the stop surface.

[0002] Furthermore, the present invention relates to a fluid line connection of the type described above.

[0003] Such a fluid line connection - however without a fitting, but instead with a direct connection of a pipe to the connection nozzle - is known from EP 2 872 811 B1 and is used, for example, in hydraulic systems in mechanical engineering and vehicle construction.

[0004] Such fluid line connections are specifically designed for connecting thin-walled pipelines with pipe pressures up to 800 bar NWP (Nominal Working Pressure). A ratio of pipe wall thickness s to pipe outer diameter d of 0.04 ≤ s / d ≤ 0.08 is preferred. To ensure reliable tightness of the pipe connection at these pressures, sufficiently large axial clamping forces must be transmitted by the union nut to the connection surface of the connecting piece and then to the pipe section being connected, particularly to its bearing surface and sealing surface. For reliable transmission of these axial clamping forces, the shoulder of the connecting piece must have a sufficient height, depending on the diameter and wall thickness of the pipe.

[0005] The invention according to EP 2 872 811 B1 is based on the objective of providing a pipe connection, a pipeline, and a connecting piece for the pipe connection, such that internal sinkage is avoided in thin-walled pipelines during a forming process, and at the same time the pipe connection can provide a sufficient sealing function. For this purpose, the cone angle of the connecting bore in the area of ​​the connecting surface of the connecting piece and the cone angle of the connecting section in the area of ​​the sealing surface of the pipeline are 30° to 50°. Due to the steeper cone angle of at least 30°, the sealing surface can be made shorter in the direction of the slope while maintaining the same shoulder height. This prevents internal sinkage in the area of ​​the sealing surface during a forming process used to create the connecting section on the pipeline.Furthermore, a sufficiently large axial clamping force can be transmitted by the union nut to the connection surface of the connecting piece and to the connecting section of the pipeline without plastically deforming the connecting section. In another embodiment of the invention, the cone angle of the connecting bore and the connecting section in the area of ​​the sealing surface is 40°. This allows for a particularly good balance between preventing inward sink marks on the sealing surface during the forming process and dimensioning the axial clamping force and the clamping force, thus ensuring optimal sealing of the pipe connection.

[0006] The applicant's known fluid line connection described above represents an essential component in line and connection technology of a system already known as VOSSLok. 40This is a commercially available piping system, primarily made of stainless steel, which can be used at both low and high pressures. To create the geometric shape of the pipe end to be joined, required for the fluid line connection, the system includes special tools for implementing an axial upsetting or a wobbling process.

[0007] To curb greenhouse gas emissions, there is a growing focus on alternative propulsion systems. Hydrogen-based mobility can make a significant contribution to achieving climate goals. However, the pipeline concepts required for hydrogen transport in both mobile and stationary applications place high demands on quality. For example, due to its small molecular dimensions, or atomic dimensions when diffusing, hydrogen has a higher diffusion coefficient in solids, such as steel, compared to other gases or even hydraulic fluids. In various pipeline applications, not only extremely high pressures, e.g., up to 1050 bar, but also high flow velocities, e.g., exceeding Mach 1, must be expected.

[0008] To enable short detours, e.g., of 90°, even in confined installation spaces, the aforementioned fluid line connection system also includes components that can act as space-saving fittings, partially replacing the pipe's function. The geometry of such fittings or other components, such as end caps, must, when the aforementioned fluid line connection is used, correspond to the conical outer contour of the pipe shape in the connection section, as defined in the pipe connection system of EP 2 872 811 B1. The contour of the inner channel is that of a simple through-hole.

[0009] If the axes of the components to be joined are not perfectly aligned, as is characteristic of swivel fittings (so-called swivel systems), force application during assembly can, in unfavorable cases, cause the fitting to become misaligned in the connection bore of the connecting piece. This misalignment can then directly—and thus, detrimentally, even during assembly—cause leakage. A deviation in the concentricity of the fitting's through-hole relative to the sealing cone of the connecting piece can exacerbate this problem.

[0010] Due to an angular misalignment between the cone angle of the fitting's connecting section and the cone angle of the connecting bore of the spigot, a bending stress occurs during assembly. This stress arises when the fitting is forced axially further into the connecting spigot by the union nut during tightening. This deformation, also known as "buckling," occurs earlier or later than the other side at the connecting end of the fitting in a radial direction, and can also adversely affect the entire system, leading to misalignment. The stiffness (section modulus) of the wall of the fitting's connecting section—that is, its resistance to buckling or, in the terminology of engineering mechanics, to bending—and its degree of variation depend on the materials used and the manufacturing process of the fitting, e.g.,...its material and surface properties, due to factors such as manufacturer and batch, are difficult or impossible to predict due to fluctuations within often wide permissible tolerance ranges, so that no appropriate preventive measures could be taken.

[0011] The invention is based on the objective of creating a fitting of the type mentioned above with a high sealing effect, which avoids the disadvantages described above.

[0012] The problem underlying the invention is solved by a fitting having the features of the characterizing part of claim 1.

[0013] Accordingly, it is provided that the fitting has a base body formed by primary forming and / or machining, wherein the base body has an internal contour produced by primary forming and / or machining from its connection end, which deviates at least in some areas from a smooth through-bore in such a way that, when the base body is axially pressed into the connection stub during assembly by means of screwing by the union nut, a deformation of the connection section due to an angular deviation between the cone angle of the connection section and the cone angle of the connection bore results in a circumferentially uniform deformation in the radial direction inwards.

[0014] Primary forming is a well-known major group of manufacturing processes and, according to DIN 8580:2022-12 "Manufacturing processes - Terms, classification", encompasses all manufacturing processes in which a solid body with a geometrically defined shape is produced from a formless material. Primary forming is used to produce the initial form of a solid body.

[0015] Machining, or cutting, is the collective term for a group of manufacturing processes that give workpieces a specific geometric shape by mechanically removing excess material from raw parts in the form of chips. The most important machining processes are turning, drilling, milling, and grinding. According to the aforementioned DIN 8580 standard, machining belongs to the main group of separation processes and is the most important group in terms of industrial significance. Machining with geometrically defined cutting edges, which is preferred for producing the internal contour, refers to processes in which the number and geometry of the cutting edges are known. Machining with geometrically undefined cutting edges, on the other hand, refers to processes in which neither the geometry nor the number of cutting edges is known.DIN 8589-3:2003-09 “Manufacturing processes machining - Part 3: Milling; Classification, subdivision, terms” contains the associated machining tools, machine tools, achievable dimensional accuracies and roughnesses as well as definitions for both types of machining.

[0016] In a preferred embodiment, the invention provides that the contour of the inner channel runs essentially parallel to the radially outer contour of the fitting, which is positioned at the conical angle at the connection end, in certain areas. Thus, a substantially constant wall thickness is present in these areas.

[0017] This wall thickness can be greater than that of the thin-walled pipes mentioned at the beginning, which advantageously increases the diffusion barrier to the outside for a medium guided in the fitting, such as hydrogen, compared to a thin-walled pipe.

[0018] Preferably, the contour of the inner channel, particularly near the end of the connection, can have a circumferential groove extending radially outwards from a through-bore forming the basic shape of the inner channel. "Near" is defined as a distance from the start of the groove to the end of the connection that is less than one and a half times the groove width, preferably less than the groove width, and particularly preferably less than half the groove width.

[0019] The cross-sectional shape of the groove can be optimally formed from a fluid mechanics perspective by a surface composed of a triangular area and a quarter-circle area, with one vertex of the triangle, particularly a right-angled, asymmetrical triangle, pointing towards the end of the connection. The hypotenuse of the triangle preferably runs radially outwards, and the shorter leg of the triangle preferably coincides with the radius of the quarter-circle area. Compared to a groove with a right-angled cross-section, such a groove shape disturbs the fluid flow pattern in the connection section less.

[0020] By means of an inner contour designed according to the invention – and, moreover, optimized as described above as preferred – a defined "kinking" of the wall in the connection area of ​​the fitting can be ensured during assembly, whereby the influence of the aforementioned parameters, such as raw material, batch, manufacturer, etc., is minimized or, in the best case, completely eliminated. Furthermore, this defined "kinking" allows a slight "slipping" (gliding) of the outer contour of the connection section on the inner contour of the opening of the connecting piece, which causes the connecting parts to conform to each other during the assembly process and smooth out on their respective surfaces.Since roughness peaks grind each other down, thereby also increasing the adhesion between the fitting and the connection spigot, this effect allows for comparatively larger tolerance ranges in surface quality, which can reduce overall manufacturability and costs.

[0021] The basic idea of ​​the invention is based on the fact that, surprisingly, with other materials, with a similar but not identical geometric design - e.g., as mentioned, thin walls are not required - and with other forming processes that differ from pipe forming and which are advantageously achievable without special forming tools, a mounting behavior of the connection section of the fitting can be simulated which has essentially the same advantages as that of an end-formed pipe contour.

[0022] Accordingly, the advantages of the invention, based on known, simple basic operating principles, include reliable functionality, similar or identical deformation behavior to a comparable pipe system, the avoidance of faulty assembly leading to leaks, and finally – particularly through resilience to tolerance-related variations in the material and geometry of the blanks used to manufacture the fittings – potential cost savings. Furthermore, easy integration into existing fluidic piping systems and seamless compatibility with them are ensured. Preferred applications of the invention are fluid, and especially gas, applications, particularly in hydrogen-carrying systems.

[0023] Further details, features, and advantageous embodiments of the invention will become apparent from the exemplary embodiments described below and illustrated in the drawings, as well as from the dependent claims. The drawings show: Fig. 1 a longitudinal section through a preferred embodiment of a fitting according to the invention in a fluid line connection according to the invention, Fig. 2 one opposite Fig. 1 enlarged section of the connection area of ​​the fitting according to the invention in the fluid line connection according to the invention during assembly, Fig. 3 a further section of the fitting according to the invention in the fluid line connection according to the invention after assembly, wherein the embodiment differs slightly in details from the one in Fig. 1 and Fig. 2 differs from the embodiment shown.

[0024] In the various figures of the drawing, identical parts are always labelled with the same reference symbols.

[0025] Regarding the following description, it is expressly emphasized that the invention is not limited to the exemplary embodiments and not to all or several features of the described combinations of features; rather, each individual partial feature of the exemplary embodiment(s) can have an inventive significance independently of all other partial features described in connection therewith, both on its own and in combination with any features of another exemplary embodiment, as well as independently of the combinations of features and cross-references of the claims.

[0026] In Fig. 1 - as already mentioned - is a preferred embodiment of a fitting 10 according to the invention shown in a preferred fluid line connection 100 according to the invention.

[0027] The fitting 10 has a base body 11, preferably made of a metallic material, in particular steel, copper, brass, or stainless steel, and comprising a connecting section 12, which in turn has an inner channel 13. The connecting section 12 increases radially outward from its connecting end 14 in a frustoconical shape with a cone angle α and forms a circumferential sealing surface 16 on its outer circumferential surface 15. A shoulder 17 with a stop surface 18 adjoins the outer circumferential surface 15 directly or at a distance in the axial direction XX.

[0028] A pipe can be connected to the fitting 10 at the second end, which is not shown in the figure, in the usual way, if necessary.

[0029] In addition to the fitting 10, the fluid line connection 100 according to the invention comprises a hollow cylindrical connecting nozzle 20 with a connecting thread 21 and with a connecting bore 22, which tapers from its opening in a frustoconical shape with a cone angle β adapted to the cone angle α of the sealing surface 16, and forms a circumferential connecting surface 23 on its inner circumference for bearing against the sealing surface 16. The in Fig. 2 The quantity designated by A denotes the length over which the connecting bore 22 is conically formed with the cone angle β.

[0030] The frustoconical section of the connection bore 22 is adjoined by a hollow cylindrical section, the inner diameter of which corresponds in particular to the smallest inner diameter of the connection surface 23. The end of the connection nozzle 20 facing away from the fitting 10 is not shown in the figures and can be designed either for connecting a component of a fluid system (e.g., a valve block or a unit) or, mirrored to the end shown, for connecting a pipeline, with a further connection bore 22 and a further connection thread 21.

[0031] The cone angle α of the connecting section 12 in the region of the sealing surface 16 and the cone angle β of the connecting bore 22 in the region of the connecting surface 23 can be in the range of 30° to 50°. Preferably, the cone angle α of the connecting section 12 in the region of the sealing surface 16 and the cone angle β of the connecting bore 22 in the region of the connecting surface 23 are each 40°, particularly preferably 37°.

[0032] As a further component, the fluid line connection 100 according to the invention comprises a union nut 30 with a clamping thread 31 and with a through-opening 32, which has a circumferential clamping surface 33 for interacting with the stop surface 18 of the fitting 10. The union nut 30 can be, for example, as shown in Fig. 1 shown - designed as a union nut, wherein the connecting thread 21 of the connecting nozzle 20 is designed as an external thread on the outer circumference of the connecting nozzle 20 and the clamping thread 31 is designed as an internal thread on the inner circumference of the through opening 32 of the union nut.

[0033] The base body 11 of the fitting 10 is formed by primary forming and / or machining, wherein the base body 11, starting from its connection end 14, has an inner contour IK – hereinafter also referred to as the (outer) contour of the inner channel 13 – produced by primary forming and / or machining, which deviates at least partially from a smooth through-bore DB in the inner channel 13 such that, when the base body 11 is pressed axially XX into the connection 20 by the union fitting 30 during assembly (arrow F) by tightening the threads 31, 21 of the union fitting 30 and the connecting spigot 20, a circumferentially uniform deformation of the connection section 12 occurs due to an angular deviation Δ between the cone angle α of the connection section 12 and the cone angle β of the connecting bore 22. Connecting section 12 is adjusted radially inwards (arrow M in Fig. 1).

[0034] The fitting 10 is inserted into the connection bore 22 of the connection spigot 20 with its connecting section 12, wherein the union nut 30, advantageously designed as a union nut, is screwed onto the connection thread 21 of the connection spigot 20 with the clamping thread 31. When the union nut is screwed onto the connection spigot 20, an axial clamping force F is exerted on the stop surface 18 of the fitting 10 by means of the clamping surface 33, which causes the sealing surface 16 of the fitting 10 to be pressed against the connection surface 23 of the connection spigot 20, so that it comes into sealing contact with the connection surface 23.

[0035] A special feature of the in Fig. The embodiment shown in Figure 1 consists in the shoulder 17 with the stop surface 18 being arranged on the connecting section 12 for indirect interaction with the circumferential clamping surface 33 of the union nut 30 in a radially outer circumferential groove 19, axially spaced from the sealing surface 16. The circumferential clamping surface 33 of the union nut 30 is itself arranged in a radially inner groove 34, complementary to the groove 19 in the base body 11, whereby the interaction of the stop surface 18 of the shoulder 17 with the circumferential clamping surface 33 of the union nut 30 is effected indirectly via a ring part 40 held in the two complementary grooves 19 and 34.

[0036] In the Fig. In the embodiment shown in 3, the interaction of the stop surface 18 of the shoulder 17 with the circumferential clamping surface 33 of the overlock screw part 30 is instead achieved directly by direct contact.

[0037] Fig. Figure 2 illustrates – as do the other figures – that the contour IK of the inner channel 13 preferably runs essentially parallel to the radially outer contour of the outer circumferential surface 15, which is positioned at the cone angle α at the connection end 14. Thus, a substantially constant wall thickness W is present in these areas, which can advantageously be thicker than that of a thin-walled pipe, thereby providing a comparatively larger diffusion barrier for the fluid.

[0038] Furthermore, it illustrates Fig. 2 - as not fully illustrated by reference numerals in the other, smaller-scale figures - that the contour IK of the inner channel 13, particularly near the connection end 14, has a circumferential groove N extending radially outwards from a through-bore DB forming the basic shape of the inner channel 13. A distance X from the start of the groove N - viewed from the connection end 14 - is in particular less than one and a half times the (axial) groove width NB, preferably less than the groove width NB, and most preferably less than half the groove width NB. The in Fig. The quantity designated by reference numeral B denotes the axial distance of the end of the groove N from the connecting end 14 of the base body 11 of the fitting 11 according to the invention. The groove width NB is thus B - X.

[0039] The cross-sectional shape of the groove N is formed in a fluid-engineeringly optimal manner by a surface composed of a triangular area DF and a quarter-circle area VK. The quarter-circle area VK does not need to be exactly curved in a circular arc; parabolic, hyperbolic, elliptical, or similar curvatures are also included under this term.

[0040] One vertex of triangle DF, which is specifically right-angled and asymmetrical, points towards the connecting end 14. The hypotenuse H of triangle DF runs radially outwards and forms the wall W of the base body 11, and the short leg K of triangle DF coincides with the radius R of the quarter-circle area VK. The unlabeled long leg runs parallel to the longitudinal axis XX.

[0041] Regarding the circumferential, uniform deformation M of the connecting section 12 in the radial direction inwards that occurs during assembly according to the invention, this is also confirmed by a comparison of the Fig. 1 and Fig. 2 on the one hand with the Fig. 3, on the other hand, clearly. This shows Fig. 1 and Fig. 2, that during assembly the front face 14 of the fitting 10 initially lies in a plane that is perpendicular to the longitudinal axis XX, which runs through the fitting 10, the connecting piece 20 and the union nut 30.

[0042] In the assembled state ( Fig.3) Instead, this end face of the fitting 10 is deformed due to a constriction and exhibits an inclination towards the corresponding inner end face of the connecting piece 20, as well as – at least in some areas – a radially inward residual distance RA from this inner end face of the connecting piece 20, wherein the inner end face of the connecting piece 20 is arranged at the end of the connecting bore 22, which is positioned at the conical angle β, and is annular in shape. After assembly, the unspaced portion of the end face 14 ideally rests against the connecting piece 20 and can thus also provide an (additional) sealing effect.

[0043] The invention is not limited to the two embodiments illustrated and described, but also encompasses all embodiments that have the same effect in the sense of the invention. It is expressly emphasized that the embodiments are not limited to all features in combination; rather, each individual feature can also have inventive significance independently of all other features.

[0044] Furthermore, the invention is not yet limited to the combination of features defined in the respective independent claim, but can also be defined by any other combination of specific features from all disclosed individual features. This means that, in principle, virtually any individual feature of the independent claims can be omitted or replaced by at least one individual feature disclosed elsewhere in the application. Therefore, the claims should be understood merely as a first attempt at formulating an invention.

[0045] Furthermore, a person skilled in the art may optionally provide additional or alternative advantageous technical measures to the optional features without departing from the scope of the invention. For example, as an alternative to the embodiments shown, the connecting thread 21 of the connecting piece 20 could also be designed as an internal thread and the clamping thread 31 of the union nut 30 as an external thread.

[0046] Regarding the fluid line connection, the expert could also obtain further details - not for the fitting, but - for the connection nozzle 20 as well as for the union nut 30 and for any seals that may be required from EP 2 872 811 B1. Reference symbol list 100 fluid line connections 10 fittings of / in 100 11 basic shapes of 10 12 Connecting section of 10 / 11 13 inner channel in 10 / 11 14 End of connection from 10 / 11 15 External perimeter area of ​​12 16 sealing surface of 12 17 Shoulder of 10 / 11 18 contact surface of 17 19 groove with 18 in 10 / 11 20 connection nozzles out of 100 21 connection threads out of 20 22 connection holes of 20 23 connection area of ​​20 for 16 30 union nut screw part out of 100 31 clamping threads out of 30 32 passage opening in 30 33 clamping surface of 30 for 18 34 groove with 33 in 30 40 ring parts between 10 and 30 A Length of the conical area of ​​22 B Distance between 14 and N (end) DB through-bore in 10 / 11 DF triangular area of ​​N F axial clamping force H Hypotenuse of DF IK inner contour of 10 / outer contour of 13 K short leg of DF N Nut from IK in 10 / 11 NB Groove width of N R radius of VK RA residual distance between 14 and 20 after installation VK quarter circle area of ​​N W constant wall thickness range of 10 X Distance between 14 and N (start) XX Longitudinal axis of 100 α Cone angle of 12 β Cone angle of 22 Δ Angular deviation Iα-βI QUOTES INCLUDED IN THE DESCRIPTION

[0000] This list of documents cited by the applicant was automatically generated and is included solely for the reader's convenience. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions. Cited patent literature

[0000] EP 2 872 811 B1 [0003, 0005, 0008, 0046]

Claims

Fitting (10) for a fluid line connection (100), wherein the fluid line connection (100) comprises: - the fitting (10), optionally with a pipe connected thereto and with a base body (11) which has a connecting section (12) having an inner channel (13), which radially increases in a frustoconical shape from its connection end (14) at a conical angle (α) and forms a circumferential sealing surface (16) on its outer circumferential surface (15) and has a shoulder (17) with a stop surface (18) adjoining the outer circumferential surface (15), and - a connecting spigot (20) with a connecting thread (21) and with a connecting bore (22) which decreases in a frustoconical shape from its opening at a conical angle (β) adapted to the conical angle (α) of the sealing surface (16) and forms a circumferential connecting surface (23) on its inner circumference for bearing against the sealing surface (16),as well as a union nut (30) with a clamping thread (31) and with a through-opening (32) which has a circumferential clamping surface for interaction with the stop surface (18), characterized in that the base body (11) is formed by primary forming and / or machining, wherein the base body (11) has an inner contour (IK) produced by primary forming and / or machining from its connecting end (14) which deviates at least partially from a smooth through-bore (DB) in the inner channel (13) such that when the base body (11) is pressed axially (XX) into the connecting stub (20) during assembly by means of screwing by the union nut (30),a deformation of the connecting section (12) due to an angular deviation (Δ) between the cone angle (α) of the connecting section (12) and the cone angle (β) of the connecting bore (22) results in a circumferentially uniform deformation (M) of the connecting section (12) in the radial direction inwards. Fitting (10) according to claim 1, characterized in that the contour (IK) of the inner channel (13) runs in areas substantially parallel to the radially outer outer contour (15) which is at the cone angle (α) at ​​the connection end (14). Fitting (10) according to claim 1 or 2, characterized in that the contour (IK) of the inner channel (13), in particular in the vicinity of the connection end (14), has a circumferential groove (N) which extends radially outwards from a through bore (DB) forming the basic shape of the inner channel (13). Fitting (10) according to claim 3, characterized in that a distance (X) of the start of the groove (N) - seen from the connection end (14) - is smaller than one and a half times the groove width (NB), preferably smaller than the groove width (NB), and particularly preferably smaller than half the groove width (NB). Fitting (10) according to claim 3 or 4, characterized in that the shape of the cross-section of the groove (N) is formed by a surface composed of a triangular area (DF) and a quarter-circle area (VK), wherein one apex of the, in particular right-angled, asymmetrical triangle (DF) points towards the connection end (14). Fitting (10) according to claim 5, characterized in that the hypotenuse (H) of the triangle (DF) extends radially outwards and the short leg (K) of the triangle (DF) coincides with the radius (R) of the quarter circle area (VK). Fitting (10) according to one of claims 1 to 6, characterized in that the base body (11) is made of a metallic material, in particular steel, copper, brass or stainless steel. Fluid line connection (100) having the features of one of claims 1 to 7 . Fluid line connection (100) according to claim 8, characterized in that the cone angle (α) of the connection section (12) in the area of ​​the sealing surface (16) and the cone angle (β) of the connection bore (22) in the area of ​​the connection surface (23) is 30° to 50°. Fluid line connection (100) according to claim 8 or 9, characterized in that the cone angle (α) of the connection section (12) in the area of ​​the sealing surface (16) and the cone angle (β) of the connection bore (22) in the area of ​​the connection surface (23) are each 37°. Fluid line connection (100) according to one of claims 8 to 10, characterized in that during assembly an end face (14) of the fitting (10) lies in a plane that is perpendicular to the longitudinal axis (XX) that runs through the fitting (10), the connecting nozzle (20) and the union nut (30). Fluid line connection (100) according to claims 8 to 11, characterized in that in the assembly state an end face (14) of the fitting (10) is deformed and has an inclination towards an inner end face of the connection nozzle (20) and - at least in some areas - a residual distance from this inner end face of the connection nozzle (20), wherein the inner end face of the connection nozzle (20) is arranged at the end of the connection bore (22) which is at the angle of the cone (β) and is formed in an annular shape. Fluid line connection (100) according to one of claims 8 to 12, characterized in that the union screw part (30) is designed as a union nut (10a), wherein the connection thread (21) of the connection nozzle (20) is designed as an external thread on the outer circumference of the connection nozzle (20), and the clamping thread (31) is designed as an internal thread on the inner circumference of the through opening (32) of the union nut (10a). Fluid line connection (100) according to one of claims 8 to 13, characterized in that the shoulder (17) with the stop surface (18) on the connection section (12) is arranged in a radially outer circumferential groove (19) axially spaced from the sealing surface (16) for indirect interaction with the circumferential clamping surface (33) of the union screw part (30), wherein the circumferential clamping surface (33) of the union screw part (30) is in turn arranged in a radially inner groove (34) complementary to the groove (19) in the base body (11), and that the interaction of the stop surface (18) of the shoulder (17) with the circumferential clamping surface (33) of the union screw part (30) is effected indirectly via a ring part (40) held in the two complementary grooves (19, 34).

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