WO2023144208A1 - Raccord de tuyau doté d'une bague de serrage - Google Patents

Raccord de tuyau doté d'une bague de serrage Download PDF

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Publication number
WO2023144208A1
WO2023144208A1 PCT/EP2023/051809 EP2023051809W WO2023144208A1 WO 2023144208 A1 WO2023144208 A1 WO 2023144208A1 EP 2023051809 W EP2023051809 W EP 2023051809W WO 2023144208 A1 WO2023144208 A1 WO 2023144208A1
Authority
WO
WIPO (PCT)
Prior art keywords
clamping ring
clamping
pipe connection
pipeline
union screw
Prior art date
Application number
PCT/EP2023/051809
Other languages
German (de)
English (en)
Inventor
Gerd Berghaus
Harald Pott
Tim GEISLER
Original Assignee
Voss Fluid Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Voss Fluid Gmbh filed Critical Voss Fluid Gmbh
Publication of WO2023144208A1 publication Critical patent/WO2023144208A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L19/00—Joints in which sealing surfaces are pressed together by means of a member, e.g. a swivel nut, screwed on or into one of the joint parts
    • F16L19/02—Pipe ends provided with collars or flanges, integral with the pipe or not, pressed together by a screwed member
    • F16L19/025—Pipe ends provided with collars or flanges, integral with the pipe or not, pressed together by a screwed member the pipe ends having integral collars or flanges
    • F16L19/028—Pipe ends provided with collars or flanges, integral with the pipe or not, pressed together by a screwed member the pipe ends having integral collars or flanges the collars or flanges being obtained by deformation of the pipe wall

Definitions

  • the invention relates to a pipe connection for connecting a pipe, in particular a metal pipe.
  • the pipe connection has a pipe with a deformed connection section which increases in the shape of a truncated cone counter to an assembly direction.
  • the connecting section forms a circumferential sealing surface on its outer peripheral surface. Adjoining the sealing surface, the connection section has a shoulder with a stop surface.
  • the pipe connection also has a connecting piece with a connecting thread and a connecting hole.
  • the connection hole decreases from its opening with a cone angle in the shape of a truncated cone.
  • the cone angle is adapted in particular to correspond to the truncated cone-shaped connecting section of the pipeline in the area of the sealing surface.
  • connection hole forms a circumferential connection surface on the inner circumference for contact with the sealing surface.
  • the pipe connection has a union screw part with a tightening thread.
  • the union screw part has a through-opening, which has a running clamping surface pointing in the assembly direction on the inner circumference.
  • the pipe connection also has a clamping ring which is arranged with an inner peripheral surface pointing towards the pipeline in the through-opening of the union screw connection part.
  • the clamping ring also has a mating surface pointing towards the stop surface of the pipeline in the assembly direction.
  • the clamping ring is arranged between the clamping surface of the union screw connection part and the stop surface of the pipeline.
  • the invention relates to a union screw part with a clamping ring and a clamping ring for such a pipe connection.
  • Pipe connections described above are used, for example, in hydraulic Systems used in machine and vehicle construction. Such pipe connections are used for pipelines with pipe pressures of up to 800 bar. In order to reliably ensure the tightness of the pipe connection at these pipe pressures, sufficiently large axial clamping forces must be transmitted through the union screw connection part to the connection section of the pipeline, in particular to the stop surface and the sealing surface, and to the connection surface of the connecting piece.
  • such a pipe connection is known from WO2014/187675 A1, in which a clamping ring is arranged between a clamping surface of the union screw connection part facing the connecting piece and the stop surface of the pipeline.
  • the clamping ring When tightened, the clamping ring has a counter-surface which bears against the stop surface of the pipeline and whose inclination is adapted to correspond to the inclination of the stop surface in such a way that force can be transmitted over the entire surface.
  • the clamping ring ensures that material burrs, which can occur on the stop surface when the pipeline is deformed due to the high deformation pressures between the segments of the clamping element, do not dig into the union screw part, so that the pipeline does not snag when the union screw part is tightened rotates.
  • the clamping ring additionally increases, in particular, a reverse bending strength of the pipe connection.
  • the clamping ring known from the prior art has a ring profile which is radially slotted in such a way that the ring contour is completely severed at one point by a separating slot.
  • the known clamping ring can be made oversized in order to be pressed into the union screw connection part and/or to be pressed axially and radially against the pipeline during assembly.
  • the object of the invention is to provide a pipe connection which overcomes the disadvantages known from the prior art and has an improved service life and preferably an improved, in particular more uniform contact pressure.
  • the clamping ring has an annular profile that is closed in one piece, and the clamping ring has an outer circumference with radially open recesses.
  • the invention is an optimization of the known clamping ring by means of a closed ring, which can be deformed without the previous separating slot and can be pressed into the union screw connection part.
  • the ring profile which is closed in one piece, enables uniform radial compression and clamping of the pipe at the formed end of the pipe to increase the reverse bending strength.
  • the recesses are designed as radial punctures. These radial grooves expediently extend at least partially over the axial extension of the clamping ring. It has turned out to be particularly advantageous that the radial grooves preferably each extend over the complete axial extension of the clamping ring. Furthermore, it has proven to be advantageous for production if the radial recesses have a rounded groove base, so that the recesses are semicircular when viewed in a cross section of the clamping ring. According to a further embodiment of the invention, the recesses are designed as axial grooves.
  • the axial grooves are expediently formed, starting from the mating surface of the clamping ring pointing in the direction of assembly to the stop surface of the pipeline, pointing axially against the direction of assembly over a part of the axial extent of the clamping ring.
  • the axial grooves are advantageously designed in such a way that the clamping ring has radial openings in the area of the axial grooves.
  • the axial grooves in the mating surface of the clamping ring allow pronounced material deformation in the area of the grooves, so that a low pressing-in force is required, particularly when the clamping ring is pressed into the union screw connection part. Furthermore, the clamping ring can be pressed more strongly against the circumference of the pipeline due to the axial punctures and the resulting easier material deformation during assembly of the pipe connection.
  • the clamping ring is arranged pressed into the through-opening of the union screw connection part.
  • the clamping ring is expediently pressed in in such a way that the clamping ring is held in the union screw part so that it cannot be lost axially.
  • the pressed-in clamping ring reduces the assembly work on site and, in a further aspect, the error potential for incorrect assembly.
  • the clamping ring has a comparison an excess to the through-opening.
  • the clamping ring has a maximum outside diameter compared to the through-opening in an unpressed state and the maximum outside diameter of the clamping ring is in particular larger than a minimum through-opening diameter of the union screw connection part in a clamping ring bearing section.
  • the clamping ring is expediently arranged in the pressed state in the clamping ring bearing section.
  • an oversize of the clamping ring compared to the through-opening of the cap screw part can be provided by means of an angular position of the clamping ring.
  • other properties that have an advantageous effect on the press-in behavior and the deformation of the clamping ring can also result from the angular position of the clamping ring.
  • the pipe connection is designed in such a way that the clamping ring has a reduced outside diameter in a pre-assembled state, which is smaller than or equal to the maximum outside diameter.
  • the clamping ring in the installed state or in the state correctly clamped against the pipeline also has a minimum outside diameter which is smaller than or equal to the reduced outside diameter in the pre-assembled state.
  • the outer diameter of the clamping ring steadily decreases from its uncompressed state through its pre-assembled state to its correctly clamped state.
  • a preferred angular positioning of the clamping ring is expediently achieved in that the outer circumference of the clamping ring and in particular an inner circumferential surface of the clamping ring are designed in the shape of a truncated cone with a cone angle in a range from 10° to 40°, in particular 15° to 30°, preferably 20°.
  • the inner peripheral surface is expediently designed in the shape of a truncated cone in such a way that in an uncompressed state of the clamping ring, an inner diameter increases pointing in the assembly direction or, in particular, an outer diameter increases pointing in the assembly direction.
  • the inner peripheral surface of the ferrule is formed into a truncated cone shape, it is easier to insert a pipe through the sleeve fitting with the ferrule pressed.
  • the clamping ring has a contact surface pointing to the clamping surface of the union screw connection part, which contact surface is designed perpendicularly to the assembly direction.
  • the vertical contact surface reduces power losses that can occur due to radial power deflections and the resulting frictional forces.
  • the mating surface of the clamping ring can advantageously be formed perpendicularly to the direction of assembly in an assembled state.
  • the clamping ring has a contact surface pointing to the clamping surface, which increases at a cone angle pointing in the direction of assembly is trained.
  • the radially and axially acting force components can expediently be set via the cone angle, particularly advantageous results being obtained if the cone angle is in a range from 50° to 130°, in particular 70° to 110°, preferably 90°.
  • the counter-surface of the clamping ring can expediently be designed according to an alternative or supplementary variant of the invention pointing in the assembly direction and enclosing a cone angle.
  • the cone angle is also formed in a range from 50° to 130°, in particular 70° to 110°, preferably 90°.
  • an advantageous variant of the invention consists in that the stop surface of the pipeline and/or the clamping surface of the union screw connection part are designed to correspond to their respective contact surfaces.
  • the Stop surface of the pipeline corresponding to the mating surface of the clamping ring formed extending parallel.
  • the clamping surface of the union screw connection part can also be designed to extend parallel to the contact surface of the clamping ring. The parallel, mutually facing surfaces result in a particularly large contact area and even power transmission.
  • the clamping ring expediently has an insertion surface.
  • the insertion surface adjoins the inner peripheral surface, in particular pointing counter to the assembly direction.
  • the insertion surface is angled radially outwards from the inner peripheral surface in the manner of a truncated cone.
  • the insertion bevel can in particular be designed in such a way that the pipeline can be guided more easily through the through-opening or can be arranged more easily in the clamping ring.
  • the truncated cone-shaped insertion bevel can in particular be designed in such a way that the pipeline automatically centers itself relative to the clamping ring when it is inserted in the assembly direction, so that when it is clamped in particular the radial clamping force is distributed evenly over the circumference of the pipeline.
  • the clamping ring is made of free-cutting steel, in particular 11 SMnPb30+C according to DIN EN 10277.
  • the clamping ring can be manufactured from these steels particularly well using machining processes, in particular on automatic machine tools.
  • the union screw part is expediently designed as a screw nut with an external tool attachment, in particular as a hexagonal nut.
  • the nut is versatile and easy to assemble and disassemble.
  • the object on which the invention is based can also be achieved by a union screw part with a clamping ring for a pipe connection according to one of the aforementioned versions in that the clamping ring and the Union screw part having the features of the clamping ring and the union screw part according to claim 1.
  • a union screw part with a clamping ring can expediently have the features of the clamping ring and/or the union screw part of at least one of the aforementioned versions, so that the corresponding advantageous effects are achieved.
  • a clamping ring for a pipe connection according to one of the aforementioned embodiments.
  • this clamping ring has at least the features of the clamping ring according to claim 1 .
  • Advantageous designs of the clamping ring have the features of the clamping ring according to at least one of the aforementioned designs described for the pipe connection.
  • FIG. 1 is a plan view of a pipe connection according to the invention in an unstressed state
  • Fig. 2 is a sectional view along a mounting direction on the
  • Fig. 4 is a sectional view along a mounting direction on the
  • 5 shows a perspective view of a first clamping ring according to the invention
  • 6 is a sectional view along AA through the invention
  • Figure 7 is a sectional view along B-B through the invention
  • Fig. 8 is an enlarged view of the sectional area C according to Fig. 7,
  • FIG. 9 shows a perspective representation of a further clamping ring according to the invention.
  • Figure 10 is a sectional view along D-D through the invention
  • Figure 11 is a sectional view along E-E through the invention
  • Fig. 12 is a sectional view of a nut designed as a cap
  • Screw connection part with an inserted clamping ring Screw connection part with an inserted clamping ring.
  • FIG. 1 to 4 show a pipe connection 1 for connecting a pipe 2, in particular a metal pipe.
  • the pipe connection has a pipe 2 with a deformed connection section 4 .
  • the connecting section 4 increases counter to a mounting direction M in the shape of a truncated cone and forms a circumferential sealing surface 6 there on its outer peripheral surface.
  • the pipe connection 1 has a connecting piece 10 with a connecting thread 12 and a connecting hole 14 .
  • the connecting piece 10 is shown in particular in FIGS.
  • the connection bore 14 of the connecting piece 10 decreases from its opening with a cone angle corresponding to the truncated cone-shaped connecting section 4 of the pipeline 2 in the region of the sealing surface 6 in the form of a truncated cone.
  • the cone angle is 24°.
  • the connection bore 14 forms there on the inner circumference a continuous connection surface 16 for contact with the sealing surface 6.
  • the pipe connection 1 also has a union screw part 18 with a tightening thread 20 and a through-opening 22 .
  • the union screw part 18 has a circumferential clamping surface 24 pointing in the assembly direction M on the inner circumference.
  • the pipe connection 1 has a clamping ring 26 .
  • the clamping ring 26 is shown in a first variant in particular in FIGS. 2, 4 and 5 to 8 and in a further advantageous variant in FIGS. 9 to 11.
  • the clamping ring 26 also has a mating surface 28 pointing in the assembly direction M to the stop surface 8 of the pipeline 2 .
  • the mating surface 28 is used to rest against the stop surface 8 of the connecting section 4 of the pipeline 2.
  • the clamping ring 26 with an inner peripheral surface facing the pipeline 2 is in the through opening 22 of the union screw part 18 between the clamping surface 24 of the union screw part 18 and the Stop surface 8 of the pipeline 2 arranged.
  • the clamping ring 26 also has a contact surface 30 for contact with the clamping surface 24 of the union screw part 18 .
  • the pipe connection 1 is designed such that at the latest in a shown in Figs. 3 and 4 clamped state of the pipe connection 1, the clamping surface 24 of the union screw part 18 against the contact surface 30 of the clamping ring 26 and the Mating surface 28 of the clamping ring 26 is braced against the stop surface 8 of the pipeline 2 .
  • the pipeline 2 is expediently braced with its sealing surface 6 pointing in the assembly direction M against the connection surface 16 of the connecting piece 10 .
  • the connecting piece 10 can be part of a connector which, as shown in FIGS. Furthermore, the connecting piece 10 can also be part of a collecting tank or a unit or another element of a line system.
  • the clamping ring 26 has an annular profile that is closed in one piece.
  • FIGS. 5 to 11 show embodiments of the clamping ring 26 according to the invention.
  • the clamping ring 26 according to the invention has, as shown in particular in FIGS 32a, 32b. Due to the closed ring profile and the particularly uniformly arranged recesses 32a, 32b, during final assembly of the pipeline 2, see the clamped state of the pipe connection 1 in FIG Connection section 4 guaranteed. In the clamped state, the pipe connection 1 expediently has an advantageous firm and secure radial clamping of the pipe 2 behind the formed connection section 4 for absorbing alternating bending loads.
  • the recesses 32a, 32b are designed as radial recesses 32a, which extend at least partially over the axial extension of the clamping ring 26.
  • the radial recesses 32a extend over the entire axial extent of the clamping ring 26. This expediently generates an elastic and plastic deformation of the clamping ring 26 that can be achieved with little force, in particular in the form of a narrowing of the inner diameter.
  • FIG. 10 shows a section through two opposing radial recesses 32a, it being particularly advantageously shown that the clamping ring 26 is not completely radially perforated, even in the region of the recesses 32a.
  • FIG. 9 An advantageous variant can also be seen in particular in FIG. 9, according to which the radial recesses 32a have a rounded groove base, so that the recesses 32a are semicircular when viewed in a cross section of the clamping ring 26 .
  • FIGS. 1 to 4 A particularly advantageous embodiment of the clamping ring 26 is shown in particular in FIGS. This embodiment is also shown as an example in the embodiments shown in FIGS. 1 to 4 in order to clarify the states of the pipe connection 1.
  • the recesses 32b are designed as axial recesses 32b.
  • the axial grooves 32b extend, as shown in particular in FIGS. 5 to 7, from the mating surface 28 of the clamping ring 26 pointing in the mounting direction M to the stop surface 8 of the pipeline 2, starting axially against the mounting direction M over a part of the axial extent of the clamping ring 26.
  • the axial grooves 32b are expediently designed in such a way that the clamping ring 26 has radial openings in the region of the axial grooves 32b.
  • the clamping ring 26 is therefore perforated radially in the region of the axial recesses 32b.
  • the axial recesses 32b do not extend over the entire axial extension of the clamping ring 26, but rather form a circumferentially closed annular collar 34 at an end pointing against the assembly direction M. It is particularly advantageous for the pipe connection 1 or the clamping ring 26 to have twelve to four, in particular ten to six, evenly distributed recesses 32a, 32b over the circumference of the clamping ring 26 . As shown in FIGS. 5 and 9, the clamping ring 26 expediently has eight recesses 32a, 32b, which are designed to be evenly distributed.
  • the clamping ring 26 is arranged pressed into the through-opening 22 of the union screw connection part 18, as shown in particular in FIG.
  • the clamping ring 26 is pressed axially against the assembly direction M with the contact surface 30 against the clamping surface 24 .
  • the clamping ring 26 is held axially in the union screw connection part 18 so that it cannot be lost.
  • the clamping ring 26 expediently has an oversize in comparison to the through-opening 22 of the union screw connection part 18 .
  • the clamping ring 26 particularly advantageously has a maximum outer diameter 36 in an unpressed state.
  • This maximum outer diameter 36 of the clamping ring 26 is expediently larger than a minimum through-opening diameter 38 of the union screw connection part 18 in a clamping ring bearing section 40 in which the clamping ring 26 is arranged, in particular in the pressed state.
  • the design which has a defined oversize, is particularly advantageous for arranging the clamping ring 26 in the through-opening 22 of the union screw part 18 in a pre-assembly step, as described above.
  • a contact pressure force and a holding force of the clamping ring 26 in the clamping ring bearing section 40 can be adjusted by adjusting the oversize.
  • the pipe connection 1 is designed in such a way that the clamping ring 26 has a reduced outside diameter in a pre-assembled state, which is smaller than or equal to the maximum outside diameter 36.
  • the clamping ring 26 expediently has the Pipeline 2 correctly assembled state still has a minimum outer diameter, which is smaller than or equal to the reduced outer diameter in the pre-assembled state.
  • the outer circumference of the clamping ring 26 and in particular an inner circumferential surface 44 of the clamping ring 26 is expediently designed in the shape of a truncated cone with a cone angle a44 in a range from 10° to 40°, in particular 15° to 30°.
  • FIG. 8 shows a preferred embodiment according to which the cone angle a44 is 20°.
  • the outer diameter 36 and in particular an inner diameter of the clamping ring 26 increases pointing in the assembly direction M.
  • the clamping ring 26 can easily rest against the inner circumference of the through-opening 22 and, in particular, be slightly deformed. Such an angular adjustment of the ring contour is particularly useful in order to generate a defined oversize for pressing the clamping ring 26 into the union screw part 18 .
  • the outer circumference of the clamping ring 26 is preferably tapered with the angle a44 pointing in the mounting direction M and increasing in such a way that in the uncompressed state the clamping ring 26 is at a transition from the counter surface 28 to the outer circumference of the clamping ring 26 has a maximum outer diameter 36, which is larger than a core diameter of the clamping thread 20 of the union screw part 18.
  • Clamping ring 26 at least in the unpressed state, has a cylindrical shape Outer circumference with a maximum outer diameter 36 that is constant over the axial extension of the outer circumferential surface up to the contact surface 30.
  • this constant outer diameter 36 is larger in the uncompressed state than the core diameter of the core diameter of the clamping thread 20 of the union screw connection part 18.
  • An advantageous variant of the invention provides that the mating surface 28 of the clamping ring 26 is formed perpendicularly to the mounting direction M in an assembled state in an alternative or supplementary embodiment.
  • the clamping ring 26 has the contact surface 30 pointing to the clamping surface 24 designed in such a way that that the contact surface 30 is formed pointing upwards at a cone angle a30 in the mounting direction M.
  • This embodiment is shown as an example in FIGS. 6 to 8, 10 and 11.
  • the pipe connection 1 with such a clamping ring 26 is shown in FIGS. 2 and 4 as an example.
  • the radially and axially acting force components can be adjusted via the cone angle a30, with particularly advantageous results being obtained if the cone angle a30 is in a range from 50° to 130°, in particular 70° to 110°, preferably 90°.
  • the examples shown are shown with a contact surface 30 which has a preferred cone angle a30 of 90°.
  • the mating surface 28 facing the stop surface 8 of the pipeline 2 encloses a cone angle pointing in the assembly direction M, which for an advantageous distribution of force according to the aforementioned embodiment is in particular in a range from 50° to 130°. in particular 70° to 110°, preferably 90°.
  • an improved embodiment of the invention consists in that the stop surface 8 of the pipeline 2 and/or the clamping surface 24 of the union screw connection part 18 corresponds to their respective contact surfaces are formed.
  • the stop surface 8 of the pipeline 2 is designed to correspond to the vertical mating surface 28 of the clamping ring 26, in particular in the compressed state, and the clamping surface 24 of the union screw connection part 18 is angled, corresponding to the contact surface 30 of the clamping ring 26, in particular with a cone angle a24 formed by 90°.
  • the cone angle a30 of the contact surface 30 of the clamping ring 26, in particular in the embodiment of the clamping ring 26 shown in Fig. 7, is designed to increase in the direction of assembly M such that the cone angle a30 of the contact surface 30 is greater than the cone angle a24 in an unpressed state the clamping surface 24 of the union screw connection part 18.
  • the clamping ring 26 is pressed during pre-assembly into the through-opening 22 of the union screw connection part 18 in such a way that the clamping ring 26 tilts radially inwards and is deformed.
  • the outer diameter 36 is expediently reduced in the process.
  • the outer diameter 30 is reduced at the transition from the mating surface 28 to the outer circumference of the clamping ring 26 and adapts to the core diameter of the clamping thread 20 in such a way that the compression provides a holding function for the clamping ring 26 in the through-opening 22 of the cap screw part 18 is generated.
  • the cone angle a30 of the contact surface 30 is reduced in the preassembled state compared to the cone angle a30 of the contact surface 30 in the unpressed state.
  • the cone angle a30 of the contact surface 30 approaches the cone angle a24 of the clamping surface 24, preferably 90°.
  • the clamping ring 26 moves further radially out of the preassembled state internally tilted and deformed.
  • the outer diameter of the clamping ring 26 is further reduced compared to the outer diameter of the clamping ring 26 in the pre-assembled state.
  • the clamping ring 26 is tilted and deformed radially inwards until, in the clamped state, the cone angle a30 of the contact surface 30 is adjusted to the cone angle a24 of the clamping surface 24, expediently 90°.
  • the clamping ring 26 is deformed radially inwards until, in the compressed state, the inner peripheral surface 44 of the clamping ring 26 rests against the pipeline 2 without a gap. The desired radial clamping of the pipeline 2 by the clamping ring 26 is thereby advantageously achieved.
  • a further variant in particular in the embodiment of the clamping ring 26 shown in Fig. 10, provides that the cone angle a30 of the contact surface 30 of the clamping ring 26 in the unpressed state is equal to the cone angle a24 of the clamping surface 24 of the union screw part 18.
  • the clamping ring 26 is pressed during pre-assembly into the through-opening 22 of the union screw connection part 18 in such a way that the clamping ring 26 deforms and the outer diameter 36 expands over the axial extent of the Outer peripheral surface is constantly reduced up to the contact surface 30 and the core diameter of the clamping thread 20 adapts.
  • the retaining function of the clamping ring 26 in the through-opening 22 of the union screw connection part 18 is advantageously produced by means of this compression.
  • the cone angle a30 of the contact surface 30 in the preassembled state remains the same as the cone angle a30 of the contact surface 30 in the unpressed state, in particular 90°.
  • the clamping ring 26 is pressed when the clamping ring 26 between the stop surface 8 of the pipeline 2 and the clamping surface 24 of the union screw part 18 via the clamping surface 24 of the union screw part 18 so far radially inwards until, in the compressed state, the inner peripheral surface 44 of the clamping ring 26 rests without a gap on the pipeline 2.
  • the stop surface 8 of the pipeline 2 is designed to extend parallel to the mating surface 28 of the clamping ring 26 .
  • the clamping surface 24 of the cap screw part 18 can be designed to extend parallel to the contact surface 30 of the clamping ring 26, as shown in particular in FIGS.
  • the parallel, mutually facing surfaces have a particularly large contact surface and thus result in even power transmission.
  • the clamping ring 26 has an insertion surface 42 .
  • This insertion surface 42 is marked in particular in FIG. 8 and expediently serves to facilitate the passage and centering of the pipeline 2 in the assembly direction M through the clamping ring 26 .
  • the insertion surface 42 adjoins the inner peripheral surface 44 , pointing counter to the assembly direction M, and is expediently designed in the manner of a truncated cone, angled radially outwards from the inner peripheral surface 44 .
  • a variant of the invention, according to which the clamping ring 26 is made of free-cutting steel, in particular 11 SMnPb30+C according to DIN EN 10277, has proven advantageous for optimizing the production process.
  • the union screw part 18 is designed as a screw nut, as shown in FIGS. 12 and 13, with an external tool attachment, in particular as a hexagonal nut.
  • a union screw part 18 according to the invention is shown with a clamping ring 26 for a pipe connection 1 previously described.
  • the clamping ring 26 and the union screw part 18 have the inventive features of the clamping ring 26 and the union screw part 18 according to the aforementioned pipe connection 1 according to the invention.
  • the union screw part 18 according to the invention with the clamping ring 26 is in particular designed in such a way that it can be integrated as a retrofit kit into existing pipe connections, known for example from the prior art such as WO2014/187675 A1.
  • clamping rings according to the invention for a pipe connection 1 of the above type.
  • the clamping rings are also suitable for retrofitting in known pipe connections 1, with the clamping ring 26 having at least the features according to the invention of the clamping ring 26 of the pipeline 2 according to the invention.
  • the clamping ring 26 can likewise be optimized by the advantageous features of the clamping ring 26 according to at least one advantageous embodiment of the pipe connection 1 .
  • the following description claims that the invention is not limited to the exemplary embodiments and not to all or more features of the combinations of features described, rather each individual partial feature of the/each exemplary embodiment is also detached from all other partial features described in connection with it also in combination with any features of another embodiment of importance for the subject matter of the invention.
  • the invention is not limited to the exemplary embodiments shown and described, but also includes all embodiments that have the same effect within the meaning of the invention. It is expressly emphasized that the exemplary embodiments are not limited to all features in combination; rather, each individual partial feature can also have an inventive significance independently of all other partial features. Furthermore, the invention has not yet been limited to the combination of features defined in claim 1, but can also be defined by any other combination of specific features of all the individual features disclosed overall. This means that in principle practically every individual feature of claim 1 can be omitted or replaced by at least one individual feature disclosed elsewhere in the application.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Joints With Pressure Members (AREA)
  • Clamps And Clips (AREA)

Abstract

La présente invention concerne un raccord de tuyau (1) comprenant : une conduite (2) ayant une partie de raccordement façonnée (4) qui augmente à la manière d'un cône tronqué à l'encontre d'une direction de montage (M) et forme, sur sa surface circonférentielle externe, une surface d'étanchéité continue (6) et présente, de manière adjacente à celle-ci, un épaulement doté d'une surface d'arrêt (8) ; et une pièce de raccordement (10) ayant un filetage de raccordement (12) et un trou de raccordement (14) qui, à partir de son ouverture, diminue à la manière d'un cône tronqué selon un angle de cône adapté pour correspondre à la partie de raccordement en forme de cône tronqué (4) de la conduite (2) dans la région de la surface d'étanchéité (6) et forme, sur la circonférence interne, une surface de raccordement continue (16) pour venir en butée contre la surface d'étanchéité (6) ; et une partie raccord (18) ayant un filetage de serrage et une ouverture traversante (22) qui présente, sur la circonférence interne, une surface de serrage continue (24) dans la direction de montage (M) ; et une bague de serrage (26) qui présente une contre-surface (28) faisant face à la surface de butée (8) de la conduite (2) dans la direction de montage (M) et qui est agencée, avec une surface circonférentielle interne (44) faisant face à la conduite (2), dans l'ouverture traversante (22) de la partie raccord (18) entre la surface de serrage (24) de la partie raccord (18) et la surface de butée (8) de la conduite (2). La bague de serrage (26) présente un profil annulaire fermé d'un seul tenant et une circonférence externe dotée d'évidements ouverts radialement (32a, 32b).
PCT/EP2023/051809 2022-01-27 2023-01-25 Raccord de tuyau doté d'une bague de serrage WO2023144208A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102022101924.1 2022-01-27
DE102022101924.1A DE102022101924A1 (de) 2022-01-27 2022-01-27 Rohrverbindung mit Klemmring

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WO2023144208A1 true WO2023144208A1 (fr) 2023-08-03

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PCT/EP2023/051809 WO2023144208A1 (fr) 2022-01-27 2023-01-25 Raccord de tuyau doté d'une bague de serrage

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE463201C (de) * 1928-07-28 Benton & Stone Ltd Rohranschlussverbindung
US7000953B2 (en) * 2001-05-22 2006-02-21 Voss Fluid Gmbh & Co. Kg Pipe screw-connection
US20070145744A1 (en) * 2005-11-25 2007-06-28 I F M Electronic Gmbh Electrical connector and electrical plug and socket connection
WO2014187675A1 (fr) 2013-05-23 2014-11-27 Voss Fluid Gmbh Raccord de tuyauterie

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001020830A (ja) 1999-07-09 2001-01-23 Usui Internatl Ind Co Ltd ディーゼル機関用高圧燃料噴射管

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE463201C (de) * 1928-07-28 Benton & Stone Ltd Rohranschlussverbindung
US7000953B2 (en) * 2001-05-22 2006-02-21 Voss Fluid Gmbh & Co. Kg Pipe screw-connection
US20070145744A1 (en) * 2005-11-25 2007-06-28 I F M Electronic Gmbh Electrical connector and electrical plug and socket connection
WO2014187675A1 (fr) 2013-05-23 2014-11-27 Voss Fluid Gmbh Raccord de tuyauterie

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