Bolt nut, method for producing same, plug insert of the bolt nut, and corresponding setting method

Abstract

The invention relates to a bolt nut for securing a ceiling structure, having the following features: a. a tube with a first open tube end, a second open tube end, and a through-channel which connects the tube ends, b. a nut thread which is arranged on the radial inner face adjacently to the first tube end, c. a connecting bolt, preferably a threaded bolt, comprising a shaft and a head which is held adjacently to the second tube end in a form-fitting manner and in a rotatable manner in the through-channel, and d. a first spring which is arranged between the head of the connecting bolt and the nut thread adjacently to the first tube end in the through-channel in order to axially pre-tension the connecting bolt in the direction of the second tube end.

Description

[0001] A bolt nut, a manufacturing process therefor as well as a bolt nut insert and a corresponding setting process

[0002] 1 , Field of the invention

[0003] The present invention relates to a bolt nut for fastening a suspended ceiling construction. Furthermore, the present invention relates to a manufacturing method for the bolt nut, a plug-in insert used therein, and a method for inserting the plug-in insert into a pipe.

[0004] 2. Background of the invention

[0005] Suspended ceiling structures are known in the art for equipping buildings. Such suspended ceiling structures include, for example, ventilation systems or general ducts for moving air masses or other media within the building. Such ducts are attached using threaded rods, turnbuckles, and similar devices, which allow for height adjustment of the ducts to be attached.

[0006] Known designs have the disadvantage that a change, for example in the inclination of a duct system, can only be realized with a large amount of material and time.

[0007] A summary of various systems mentioned above is provided in European patent application EP 1 616 121 A1. Threaded pipes are used to secure duct sections, as described, for example, in JP 071 193 37 A. These consist of a hollow tube with an internal thread arranged at each of its open ends using a threaded insert.

[0008] A similar construction is described in US 4,081,219. This document describes a hollow tube with an internal thread so that hollow cylindrical elements can be screwed into both ends of the tube. For example, one hollow cylindrical element forms an internal thread because it provides another thread on its radial inner side. The other screwed-in hollow cylindrical element forms a bushing so that a threaded rod with a support piece can support itself from the inside at this point. Such constructions are complex, both in the manufacture of their individual components and in their assembly. In addition, they require the threads to be coordinated with one another and are very labor-intensive to install in order to achieve a suitable height adjustment for a suspended ceiling construction.

[0009] In order to provide an internal thread in a hollow tube, a variety of insert designs were developed years ago. For example, EP 1 873 406 A1 describes such an insert which, when installed, consists of two telescopically interlocking conical sleeve sections. These sleeve sections are firmly connected to one another, and this connection can be released during installation using a predetermined breaking point. While one sleeve, specifically the inner sleeve, provides an internal thread, the conical outer contours of both sleeves ensure that the insert insert is frictionally pressed into place, for example in a metal tube. The double-conical design of the telescopically interlocking sleeves poses the risk of deformation of the threaded sleeve. This negatively impacts the running properties of the threaded connection.

[0010] DE 26 30 344 and DE 33 27 751 each describe an insert consisting of a conical threaded sleeve connected by a predetermined breaking point and an adjoining hollow cylindrical fastening sleeve. The telescopic connection of the two sleeves has the disadvantage that an integral connection with a predetermined breaking point is provided at the direct contact between the two sleeves. The direct connection has the disadvantage that the intended predetermined breaking point does not cleanly separate the connection between the two sleeves during installation. This causes damage to the sleeves in their transition area, or material residues from the sleeve connection are dragged into the space between the two sleeves. Such material residues lead to deformation of the interlocking sleeves or block the telescopic sliding of the two sleeves onto one another.In this way, the setting process of such an insert does not run smoothly, so that the threaded sleeve is placed inaccurately in the pipe end.

[0011] The object of the present invention is therefore to propose an additional fastening option for a suspended ceiling construction that complements the prior art. In the course of this, alternative thread solutions that can be used in such a fastening alternative are also to be described.

[0012] 3. Summary of the invention

[0013] The above object is achieved by a bolt nut for fastening a suspended ceiling construction according to independent patent claim 1. Furthermore, the above object is achieved by a manufacturing method for such a bolt nut according to independent patent claim 10. Independent patent claim 13 defines an insert for producing the bolt nut, while independent patent claims 18 and 19 each describe a setting method for such an insert in a pipe, e.g., for producing a bolt nut. Independent patent claim 17 is directed to a pipe in combination with an insert as an intermediate product in the production of the bolt nut. Advantageous embodiments and further developments will become apparent from the following description, the accompanying drawings, and the appended patent claims.

[0014] A bolt nut for fastening a suspended ceiling construction, comprising the following features: a pipe with a first open pipe end and a second open pipe end, as well as a through-channel connecting the pipe ends, a nut thread arranged on a radial inner side adjacent to the first pipe end, a connecting bolt, preferably a threaded bolt, with a shaft and a head, which is held in a form-fitting and rotatable manner in the through-channel adjacent to the second pipe end, and a friction means which, in adapted cooperation with a relative rotation of the connecting bolt, generates a friction moment which counteracts the rotation of the connecting bolt. The bolt nut according to the invention represents an effective and alternative fastening option with regard to known fastening means.This bolt nut is preferably designed, for example, to fasten pipe clamps in suspended ceiling structures. For this purpose, the connecting bolt is attached to the pipe clamp. The connecting bolt preferably has the configuration of a threaded bolt that can be screwed into a receiving thread of the pipe clamp. Likewise, it is also preferred to manufacture the connecting bolt on its shaft with a bayonet lock or a snap-in connection or a similar alternative for establishing a frictional and / or force-locking connection to the pipe clamp or a similar structure. According to a preferred embodiment of the present invention, the connecting bolt is equipped as a threaded bolt with a standard thread on its shaft.

[0015] At least one friction means according to the invention is provided and adapted to impede rotation of the connecting bolt about its longitudinal axis. For this purpose, the friction occurring between the underside of the head and a contact surface of the pipe is preferably increased. According to various preferred embodiments, a ring made of elastic material is preferably used for this purpose. This ring is arranged between the underside of the head and the interior of the pipe and increases the friction upon rotation of the connecting bolt (see below).

[0016] Also preferably, a spring is positioned in the through-channel, which pushes the connecting bolt toward the connecting shaft. This additional force also increases the friction between the underside of the head and a surface engaging it.

[0017] Other preferred and optional friction agents are explained in more detail below.

[0018] While the connecting bolt is held positively and rotatably inside the bolt nut, the end of the pipe opposite the connecting bolt has an internal nut thread. A threaded rod or bolt, for example, can be screwed into this nut thread to further fasten the bolt nut. Since the nut thread is preferably located adjacent to the entrance to the pipe's through-channel, the through-channel forms a receiving space for a threaded rod or the like, adjoining the nut thread. In this way, the combination of the nut thread and the adjoining through-channel provides a flexible compensation option when using the bolt nut. For example, to adjust the height of a pipe clamp attached to a ceiling structure, a threaded rod can be screwed into the through-channel to different depths.

[0019] In addition to its function as a receiving space for a threaded rod or similar device, the through-channel also serves as a means of accessing the connecting bolt. For this purpose, the head of the connecting bolt has a drive feature that allows a tool to be inserted through the nut thread and the through-channel.

[0020] According to a preferred embodiment of the present invention, the nut thread is provided by a blind rivet nut or a nut threaded insert attached to the first pipe end.

[0021] To provide the nut thread arranged at the first pipe end, various design alternatives are preferred. The simplest alternative is to machine the nut thread directly into the radial inner wall of the pipe. However, to ensure greater flexibility in adjusting the size and type of nut thread, according to further preferred embodiments of the present invention, a blind rivet nut or a plug-in insert with a nut thread is fastened in or adjacent to the first pipe opening. A blind rivet nut or such a plug-in insert has the advantage that, depending on the practical situation and regardless of the inner diameter of the pipe, a suitable internal thread can be realized in the through-channel of the pipe with the aid of the blind rivet nut or the plug-in insert.

[0022] Furthermore, the use of a blind rivet nut or insert preferably results in a free inner diameter of the pipe's receiving space being larger than the nominal diameter of the nut thread of the insert or blind rivet nut. This ensures that the screw-in torque when screwing, for example, a threaded rod into the nut thread remains constant regardless of the screw-in depth of the threaded rod, since the threaded rod being screwed in is not slowed down by frictional torque on an inner pipe wall or by an elongating thread engagement.

[0023] According to various preferred embodiments of the present invention, the pipe wall is deformed when the blind rivet nut or the insert is inserted at the first pipe end. This deformation results in the blind rivet nut or insert being held in the pipe of the bolt nut in a frictionally and positively locking manner adjacent to or adjacent to the first pipe end.

[0024] Also preferably, the nut thread introduced into the bolt nut in this way has the same pitch direction as a thread of a threaded bolt arranged at the second pipe end.

[0025] Preferably, the pipe has a constriction of the through-channel adjacent to the second pipe end, so that an inner diameter of the constriction is smaller than an outer diameter of the head in order to hold the connecting bolt in a form-fitting manner in the through-channel.

[0026] The preferred connecting bolt or the preferred threaded bolt is attached adjacent to the second pipe end in various ways. Since the head of the connecting bolt extends radially beyond the outer diameter of the connecting bolt's shank, a positive connection at the second pipe end is sufficient to hold the connecting bolt within the through-channel, allowing it to rotate about its longitudinal axis. Despite this positive attachment, the shank of the connecting bolt protrudes through the second pipe opening out of the tube of the bolt nut to establish a corresponding connection.

[0027] According to a preferred embodiment of the present invention, a constriction of the through-channel is provided adjacent to the second pipe end, at which the head of the connecting bolt is positively prevented from leaving the through-channel.

[0028] Preferably, the constriction is provided by a socket insert or a plug-in insert without a nut thread or by a compression of the pipe.

[0029] In order to hold the connecting bolt positively within the through-channel via its head, various design alternatives are preferred. One alternative is to reduce the inner diameter of the bolt nut tube by pressing it in such a way that the head of the connecting bolt is held rotatably in the through-channel. Alternatively, a bushing insert can be placed adjacent to the second tube end within the through-channel. Such a bushing insert preferably represents a hollow cylindrical taper of the interior of the through-channel, against which the underside of the head of the connecting bolt can rest.

[0030] A further preferred embodiment of the present invention provides for the insertion of an insert, explained in more detail below, into the second tube end of the bolt nut. Such an insert preferably consists of a combination of a hollow cylindrical and a conical section, which are telescoped into one another during a fitting process. The associated widening of the tube end leads to a frictional and positive fastening of the insert in the tube of the bolt nut. Since an insert inserted in this way also reduces the inner diameter of the tube of the bolt nut, the head of the connecting bolt rests positively against it and is held inside the through-channel.

[0031] The advantage of the insert according to the invention lies in the flexibility of adjusting the continuous inner diameter at the second pipe end of the bolt nut. This is because the dimensions of the insert can be matched to the dimensions of the selected connecting bolt, ensuring not only smooth running but also a reliable hold of the connecting bolt in the bolt nut. Furthermore, the use of the insert offers the preferred flexibility of allowing a worker to adjust the length of the bolt nut pipe, for example, on a construction site. The insert is then preferably inserted on-site using a suitable hand-held device, while simultaneously positioning the connecting bolt inside the through-channel, thus providing a bolt nut that can be adapted to the structural situation.

[0032] Preferably, the insert is connected to the pipe in a force-locking and form-locking manner.

[0033] According to a preferred embodiment of the bolt nut, a first spring is provided as a friction means, which is arranged in the through-channel between the head of the connecting bolt and the nut thread adjacent to the first pipe end in order to axially preload the connecting bolt in the direction of the second pipe end.

[0034] Also preferably, a ring made of elastic material is arranged between the head of the connecting bolt and the second pipe end as a further friction means to increase friction between the head and the bushing insert or plug-in insert or compression during relative rotation. Relative rotation in this context means that either the connecting bolt, in particular the threaded bolt, is rotated within the pipe, or that the pipe with the bushing insert or plug-in insert or the like is rotated while the threaded bolt is at rest.

[0035] Based on the spring arranged in the bolt nut, the connecting bolt is preferably pressed with the underside of its head against the constriction or the socket insert or the plug-in insert at the second pipe end. This frictional contact forms the basis for the connecting bolt, preferably a threaded bolt, to be screwed into a receiving thread simply by turning the tube of the bolt nut. Thus, it is not always necessary to connect a tool through the first pipe end to the drive means of the threaded bolt head in order to turn it.

[0036] To enhance this frictional contact, a ring made of elastic material is arranged between the head and the constriction, preferably the socket insert or the insert. This allows the connecting bolt to rotate along with the tube of the bolt nut, reducing the effort required to use a tool and thus the overall installation effort for the bolt nut.

[0037] A further preferred embodiment of the present invention provides that a second spring is arranged between the head of the connecting bolt and the second pipe end in order to increase friction between the head and the pipe.

[0038] According to a further preferred embodiment of the present invention, a second spring is arranged between the underside of the head of the connecting bolt, in particular of the preferred threaded bolt, and the constriction adjacent to the second pipe end. In a similar way to the elastic ring described above between the underside of the head and the constriction, the second spring also creates increased friction between the threaded bolt and the pipe of the bolt nut. Furthermore, the preferred second spring opens up the possibility of ensuring an increase in friction between the threaded bolt and the pipe even with a less controlled inner surface at the second pipe end compared to a socket insert or a plug-in insert. According to a further preferred embodiment of the present invention, the nut thread and a thread of a threaded bolt as a connecting bolt have the same direction of rotation.

[0039] This preferred structural design is advantageous, for example, when the threaded bolt of the bolt nut is fastened overhead in a ceiling structure. The subsequent screwing of, for example, a threaded rod into the nut thread, which has the same direction of rotation as the threaded bolt, would use the same direction of rotation as the threaded bolt to tighten or screw in the threaded rod. Thus, installing the threaded rod, for example, would not result in a loosening of the threaded bolt, but would instead tighten it further.

[0040] The present invention also discloses and comprises a method of manufacturing a bolt nut, in particular a bolt nut according to one of the embodiments described above, which method comprises the following steps: providing a cylindrical tube with a first and a second open tube end and a through-channel connecting the tube ends, narrowing the second tube end by pressing the second tube end or inserting a plug-in insert without a nut thread or a socket insert, inserting a connecting bolt with a head and a shaft into the through-channel such that the shaft protrudes from the through-channel at the second tube end, and arranging a friction means in the through-channel which, in adapted cooperation with a relative rotation of the connecting bolt with respect to the tube, generates a friction torque which counteracts the rotation of the connecting bolt.

[0041] According to a further preferred method design, a further step is provided: arranging a spring in the through-channel for axially pre-tensioning the connecting bolt and preferably then pressing in an insert with a nut thread into the first pipe end to hold the spring.

[0042] To preferably further increase friction between the head of the connecting bolt, in particular a threaded bolt, it is provided: arranging a ring of elastic material as a friction means between the head of the connecting bolt and the second pipe end or generally the pipe of the bolt nut.The present invention further discloses an insert which is adapted to be formed in a form-fitting and force-fitting manner into a pipe end which is thereby radially expanding, on the basis of its own radially expanding deformation, and which has the following features: a hollow-cylindrical radial compensating sleeve and a conical threaded sleeve with a conical outer contour and a nut thread arranged radially within the conical outer contour or a conical sleeve with a conical outer contour and a cylindrical through-channel arranged radially within the conical outer contour, which ends at a tapered axial end in a threadless hollow-cylindrical connecting shaft which engages in a frictionally locking manner in the hollow-cylindrical compensating sleeve or which is integrally connected to the compensating sleeve via a predetermined breaking point at an axial end facing the compensating sleeve.

[0043] The present invention additionally discloses an insert that is used at least to produce the internal structure of a pipe end of the bolt nut. Due to its preferred design alternatives, the insert can be inserted into a pipe as a nut thread, i.e. as a threaded insert, or as a socket insert without a nut thread. Due to its structural design, the fastening and thus the use of the insert insert is based on the receiving pipe being made of a deformable material, such as metal. This is because the telescopically sliding conical sleeve and the hollow cylindrical sleeve are pressed into place, the pipe is deformed radially outward when the insert insert is received, and the insert insert is held in a pressed configuration within the pipe.In this way, a preferred force-locking, i.e. frictional, and a form-locking connection is formed between the inserted insert within the pipe and the pipe.

[0044] Regardless of the internal design of the insert, i.e. with or without a nut thread, the insert generally consists of a conical section with a hollow cylindrical connecting shaft and a hollow cylindrical section. During the setting process of the insert, the conical section is pressed into the hollow cylindrical section. The hollow cylindrical connecting shaft at the end of the conical section preferably ensures a controlled entry of the conical section into the hollow cylindrical section of the insert. Starting from this controlled entry of the conical section into the hollow cylindrical section, the telescopic press connection is continuously built up and preferably increased in its force-locking cohesion with regard to the acting radial force between the two sections.

[0045] With regard to the preferred design alternative of a one-piece insert with a predetermined breaking point, the hollow cylindrical connecting shaft ensures that the material tear-off between the two sections occurs in a controlled manner, despite the predetermined breaking point breaking open during the installation process. Furthermore, the hollow cylindrical connecting shaft ensures that any disruptive material tear-off during the installation process has only a negligible impact on the configuration of the installed insert.

[0046] Preferably, its connecting shaft has an outer diameter that is less than or equal to the inner diameter of the compensating sleeve. This geometrically ensures that the conical threaded sleeve or sleeve can be pressed into the hollow cylindrical compensating sleeve in a controlled, telescopic manner.

[0047] Likewise preferably, the connecting shaft has an axial extension in the range of 5% to 30%, preferably 5% to 15%, of a total axial length of the insert insert. According to various preferred embodiments of the insert insert according to the invention, the hollow cylindrical connecting shaft has an outer diameter at the transition between the conical sleeve and the hollow cylindrical sleeve that is adapted to the inner diameter of the compensating sleeve, i.e. the hollow cylindrical sleeve. Based on this configuration, it is preferably ensured that the conical section and the hollow cylindrical section of the insert insert merge into one another without blockages during the setting process. In addition, this preferably prevents the two telescopically interlocking sections of the insert insert from becoming jammed during the setting process.

[0048] According to a further preferred embodiment, the axial length of the connecting shaft is configured such that it ensures the telescopic intermeshing of the conical section and the hollow cylindrical section of the insert. For this purpose, the hollow cylindrical connecting shaft has the above-mentioned preferred length, which is based on the overall axial length of the insert. According to a preferred embodiment of the present invention, the conical threaded sleeve and / or the conical sleeve without an internal thread has a cone ratio K in the range of 1:12≤K≤1:4, preferably 1:10≤K≤1:6.

[0049] In order to support the telescopic engagement of the conical sleeve and the hollow cylindrical sleeve and at the same time to ensure a resilient connection and a resilient fastening of the insert within a pipe, the conical threaded sleeve has a preferred cone ratio K.

[0050] The present invention also discloses a cylindrical tube having a first open tube end and a second open tube end, into which an insert according to at least one of the embodiments described above is placed at at least one of the tube ends.

[0051] The present invention further discloses a setting method of an insert according to at least one of the embodiments described above, which comprises the following steps: inserting the insert into a pipe so that the hollow cylindrical compensating sleeve is arranged adjacent to a first pipe end, screwing a tension spindle into the nut thread of the conical sleeve, moving the first pipe end into contact with a counter bearing, axially displacing the tension spindle and the counter bearing relative to one another so that the conical threaded sleeve is moved into the compensating sleeve, and unscrewing the tension spindle from the nut thread.

[0052] In addition, the present invention discloses a method for setting an insert according to at least one of the above-described embodiments, comprising the following steps: inserting the insert with a connecting bolt arranged therein into a pipe, wherein the head of the connecting bolt is arranged in the connecting channel and the shaft protrudes from the insert, screwing the shaft of the connecting bolt into a threaded tension sleeve, moving the first pipe end into contact with a counterbearing, axially displacing the threaded tension sleeve and the counterbearing relative to one another so that the conical threaded sleeve is moved into the compensating sleeve, and unscrewing the shaft from the threaded tension sleeve. 4. Brief Summary of the Drawings

[0053] The present invention is described in detail below with reference to the drawings. Like reference numerals in the drawings denote like components and / or elements. They show:

[0054] Figure 1 is a schematic side view of a bolt nut that fastens a pipe using a

[0055] Pipe clamp attached to a suspended ceiling construction,

[0056] Figure 2 is an axial sectional view of a preferred embodiment of a bolt nut,

[0057] Figure 3 is an enlarged view of a pipe end of the bolt nut in section with a blind rivet nut,

[0058] Figure 4 is an enlarged view of a preferred pipe end of the bolt nut in a sectional view with a blind rivet nut,

[0059] Figure 5 preferred radial sectional views of the tube of the bolt nut with different circumferential profiles of the tube of the bolt nut,

[0060] Figure 6 a shows a preferred embodiment of an axial end of the bolt nut in which the connecting bolt is held in the tube,

[0061] Figure 6 b shows a preferred embodiment of an axial end of the bolt nut with a compression and a truncated cone-shaped ring in which the connecting bolt is held in the pipe,

[0062] Figure 7a is an enlarged partial sectional view of a preferred one-piece insert with a conical threaded sleeve and a predetermined breaking point according to the present invention, Figure 7b is an enlarged partial sectional view of a preferred one-piece insert with a conical sleeve and a predetermined breaking point according to the present invention,

[0063] Figure 8 is an enlarged view of another preferred embodiment of the plug-in insert according to the invention in a partial sectional view,

[0064] Figure 9 is an enlarged view of another preferred embodiment of the

[0065] Insert in a partial sectional view,

[0066] Figures 10-12 are a schematic representation of the three successive phases of the setting process of the internally threaded insert in a pipe end,

[0067] Figure 13-15 is a preferred representation of the three phases of a setting process of the insert without nut thread in the end of a pipe by means of a connecting bolt arranged therein,

[0068] Figure 16 is a flow chart of a preferred embodiment of the bolt nut manufacturing method,

[0069] Figure 17 is a flow chart of a preferred embodiment of the setting process of the insert with internal thread and

[0070] Figure 18 is a flow chart of a preferred embodiment of the setting method of the insert without nut thread.

[0071] 5. Detailed description of the preferred embodiments

[0072] While Figure 2 shows a longitudinal section through a preferred embodiment of the bolt nut 1 according to the invention, Figure 1 shows, by way of example, a pipe clamp 3 with the bolt nut 1 fastened in a suspended ceiling construction. For this purpose, a threaded rod G was anchored in a ceiling D, onto which the bolt nut 1 is screwed. The connecting bolt of the bolt nut 1 connects the pipe clamp 3, which supports a pipe R, to the bolt nut 1 and thus to the ceiling D.

[0073] Preferably, the tube 10 is made of metal or plastic.

[0074] More preferably, the tube 10 is made of metal. The metal has an elongation at break A in a range of 8%≤A≤50%, in particular 15%≤A≤50%. The preferred elongation at break forms the material-technical basis for setting and elastic-plastic fastening of the plug-in insert 60, which is preferred according to the invention, in the tube 10.

[0075] The elongation at break A is determined according to EN ISO 68921 : 2019: Metallic materials - Tensile testing - Part 1 : Method of test at room temperature.

[0076] According to a preferred embodiment of the present invention, the pipe is made of stainless steel. Due to its material properties, stainless steel has the advantage of being corrosion-resistant, temperature-resistant, more robust against environmental influences, and thus more hygienic than steel. This is especially true when it is made of rust-proof stainless steel, since its surface is also less susceptible to contamination than, for example, steel.

[0077] More preferably, the tube has a wall thickness t (see Fig. 5) in the range of 0.2 mm≤t≤5 mm, in particular 0.3 mm≤t≤2 mm.

[0078] This wall thickness range is particularly preferred in combination with stainless steel as pipe material.

[0079] The preferred embodiment of the bolt nut 1 in Figure 2 comprises a tube 10 with a first 12 and a second open tube end 14. The two tube ends 12, 14 are connected to each other via a free through-channel 16 inside the tube 10.

[0080] Adjacent to the first open pipe end 12, a nut thread 30 is arranged inside the pipe 10, i.e. on a radial inner side.

[0081] According to various preferred embodiments of the present invention, the female thread 30 is provided by a male insert 50, as explained in more detail below. According to another preferred embodiment (not shown) of the present invention, the female thread 30 is cut or grooved into the radial inner wall of the tube 10.

[0082] According to a further preferred embodiment of the present invention, a threaded insert with a nut thread 30 (not shown) is fastened in the first pipe end 12. Such fastening is achieved, for example, by gluing or welding.

[0083] Also preferred and described in detail below, a nut thread 30 is provided by setting a blind rivet nut in the first pipe end 12. A setting method for blind rivet nuts is known in the art.

[0084] The aforementioned nut thread 30 preferably serves to receive a threaded rod or a threaded bolt. To assist in securing the threaded rod or bolt in the nut thread 30, the nut thread 30, in a preferred embodiment, has an anti-twist feature. This makes it difficult for a screwed-in threaded rod or bolt to accidentally come loose, for example due to vibrations.

[0085] A connecting bolt 40 is arranged adjacent to the second pipe end 14 and protruding beyond the second pipe end 14 from the interior of the pipe. The connecting bolt has a head 42 and a shaft 44 connected thereto. The shaft 44 is preferably smaller in outer diameter than the head 42, so that the connecting bolt 40 can be arranged and fastened in a form-fitting manner within the interior of the pipe 10.

[0086] According to a preferred embodiment of the present invention, the shaft 44 has an external thread 46.

[0087] According to another preferred embodiment of the connecting bolt 40, a bayonet lock or a locking structure or a steep thread (not shown) is provided on the shaft 44 to enable a connection between the connecting bolt 40 and, for example, a pipe clamp 3 or another attachment. According to a further preferred embodiment of the present invention, the head 42 has a drive means 48, such as a slot, a cross, or a Torx opening, on its side facing away from the shaft 44.

[0088] Preferably, the free inner diameter of the nut thread 30 is dimensioned such that a tool (not shown) can be inserted through the first open pipe end 12 and the through-channel 16 into the drive means 48 in order to transmit a torque to the connecting bolt 40. This torque can preferably be used to screw the external thread 46 into the pipe clamp 3 or another receiving thread.

[0089] Likewise, the inner circumferential profile and inner diameter of the nut thread are preferably adapted to the shape of an inserted tool, such as an Allen key or socket wrench. This inner through-opening of the nut thread 30, which is shaped complementarily to the tool, allows the tool to engage in rotation. This allows the bolt nut to be rotated about its longitudinal axis by the tool without this shape impairing the functionality of the nut thread.

[0090] A spring 50 is arranged in the through-channel 16. The spring 50 is preferably supported on the head 42 of the connecting bolt 40 and adjacent to the first pipe end 12 in order to spring-load the connecting bolt 40, preferably a threaded bolt, toward the second pipe end 14.

[0091] As can be seen from Figure 2, the spring 50 exerts an axial spring preload on the connecting bolt 40. This causes a head underside 43, which faces the shaft 44, to be pressed against the constriction 18 at the second tube end 14. According to the embodiment in Figure 2, the constriction 18 of the tube 10 forms the insert 60 (see below).

[0092] It is also preferred to realize the constriction 18 by a hollow cylindrical bushing insert or a compression of the tube 10 to reduce the free inner diameter of the tube 10.

[0093] The spring preload acting in the direction of the constriction 18 generates a frictional moment between an upper side 41 of the head 42, which is facing away from the shaft 44, and the spring 50. More preferably, a frictional moment is also generated between the underside 43 of the head and the constriction 18.

[0094] This frictional moment(s) helps ensure that the connecting bolt 40 rotates frictionally when the pipe 10 rotates. This positive effect supports the installation of the connecting bolt 40 in a nut thread, for example, a pipe clamp 3.

[0095] If the constriction 18 is formed by a plug-in insert 60, the additional friction torque preferably arises between the head underside 43 and the plug-in insert 60.

[0096] If the constriction 18 is created by pressing the pipe 10, the additional frictional moment between the connecting bolt 40 and the pipe 10 is preferably created by a frictional engagement between the head underside 43 and an inner surface of the pipe 10 (not shown) contacting it.

[0097] In order to increase the frictional moment between the head underside 43 and a surface opposite it, for example, the plug-in insert 60 or the constriction 18 in the form of the compression 20, according to a preferred embodiment of the present invention, a ring 52 made of elastic material is provided at this point. The ring 52, preferably an elastic O-ring or a ring of hollow cylindrical shape, counteracts relative rotation between the head underside 43 and the ring 52 and / or between the plug-in insert 60 and the ring 52 due to its elastic material properties. This also supports the rotation of the connecting bolt 40 when the pipe 10 is rotated, assisting the worker during installation.

[0098] If, with reference to the schematic representation in Figure 6a, the pipe 10 has a compression 20 as a constriction 18, the compression 20 reduces the inner diameter of the pipe 10. The surface of the pipe 10 opposite the head underside 43 due to the compression 20 for the preferential generation of an additional frictional moment between the connecting bolt 40 and the pipe 10 is not optimally suited for an elastic hollow cylindrical ring 52. Therefore, in this preferred embodiment, according to a schematic representation in Figure 6b, a truncated cone-shaped ring 52' is inserted between the head underside 43 and the compression 20. While the shaft 44 passes through the truncated cone-shaped ring, the annular surface of the truncated cone-shaped ring rests against the head underside 43. A lateral surface of the frustoconical ring preferably rests against a radially inner surface of the compression 20 or the constriction 18.In this constructive manner, the truncated cone-shaped ring generates a preferred frictional moment between the connecting bolt 40 and the pipe 10.

[0099] According to a further preferred embodiment of the present invention, as shown in Figure 6, a second spring 55 is arranged between the connecting bolt 40 and the compression 20. The second spring 55 is preferably supported on the head underside 43 and a radial inner side 22 of the compression 20. Since the second spring 55 is spring-loaded between the head underside 43 and the inner side 22 of the compression 20, an additional frictional moment is created between the connecting bolt 40 and the inner side 22 of the pipe 10. This also supports the installation or deinstallation of the connecting bolt 40 simply by turning the pipe 10 by the worker.

[0100] The connecting bolt 40 is rotatably mounted in the pipe 10. This has the preferred advantage that an attachment, such as the pipe clamp 3, can first be attached to the shaft 44, preferably on the thread 46.

[0101] Since the attachment is preferably attached to or on the shaft 44, for example, with the aid of a lock nut on the thread 46, the shaft 44 with the head 42 of the connecting bolt 40 remains freely rotatable inside the tube 10. Thus, the connection with the nut thread 30 can be established, changed, or released without impairing the connection between the connecting bolt 40 and the attachment.

[0102] If a high torque is required for the installation or deinstallation of the bolt nut 1, this torque is preferably transferred to the pipe 10 using a tool. For this purpose, the pipe 10 has the shape of a square or hexagon on its outside, at least in parts of its length, as shown by way of example in Figure 5. The polygon is also preferably used, using a tool such as an open-end wrench or the like, to adjust the distance between the objects fastened to the opposite ends of the bolt nut 1, such as a pipe clamp 3 and a ceiling structure.

[0103] The nut thread 30 is provided on a radial inner side of the first open pipe end 12. According to a first preferred embodiment of the present invention, the nut thread 30 is provided by an insert 60, explained in more detail below (see Figure 2).

[0104] According to a further preferred embodiment, a blind rivet nut 80 is secured in the first pipe end 12. The blind rivet nut 80 has, in a known manner, a circumferential, radially outwardly projecting collar 82, a threadless shank 84, and a shank portion 86 with an internal thread 88.

[0105] In order to secure the blind rivet nut 80 in the first pipe end 12, the outer diameter of the blind rivet nut 80 is preferably adapted to the inner diameter of the pipe 10. Small tolerances between the outer diameter of the blind rivet nut 80 and the inner diameter of the pipe 10 ensure that the blind rivet nut 80 is inserted into the first pipe end 12 with almost no play.

[0106] The insertion of the blind rivet nut 80 creates an annular bulge 83 in a known manner. To accommodate the annular bulge 83, a radially inner concave annular bulge 13 is preferably provided in a first preferred embodiment of the tube 10. When the blind rivet nut 80 is inserted into the first tube end 12, the radially outward-pushing annular bulge 83 preferably forms the annular bulge 13. The tube 10 adjacent to the annular bulge 13, i.e., between the collar 82 and the annular bulge 13, as well as adjacent to the annular bulge 13 and radially next to the threaded shaft 86, is further arranged directly adjacent, preferably abutting, the radial outer side of the shaft 84, 86. As a result, the annular bulge 83 preferably creates a radial frictional fastening in the annular bulge 13, as well as an axial positive fastening between the blind rivet nut 80 and the tube 10.Should the pipe 10 not be able to be expanded by the forming annular bead 83 due to its wall thickness t, the first pipe end 12 tapers off in a constriction 11 in the direction facing away from the second pipe end 14 according to a further preferred embodiment of the present invention, which is shown in Figure 4. The first pipe end 12 is preferably adapted in its inner diameter to a radial outer diameter of the annular bead 83. During the setting of the blind rivet nut 80, the annular bead 83 is expanded to such an extent that its outer diameter is approximately equal to the inner diameter of the pipe 10 at the first pipe end 12. By forming the annular bead 83 during the setting of the blind rivet nut 80 in the first pipe end 12, the constriction 11 is preferably fastened in a form-fitting and force-fitting manner between the annular bead 83 and an underside of the collar 82 of the blind rivet nut 80.It is understood that the inner diameter of the constriction 11 is equal to or slightly larger than the outer diameter of the shaft 84, 86 of the blind rivet nut 80 so that the blind rivet nut 80 can be inserted through the constriction 11 into the through-channel 16 of the pipe 10 before being set.

[0107] To provide the first pipe end 12 with the nut thread 30 and the second pipe end 14 with the constriction 18, the plug-in insert 60 of different configurations is preferably used. Figures 7 to 9 show different preferred embodiments of the plug-in insert 60.

[0108] The insert 60 is divided into a hollow cylindrical radial compensating sleeve 62 and a conical threaded sleeve 64 (see Figures 7 and 8) or a conical sleeve 66 (see Figure 9) without nut thread 30. The conical threaded sleeve 64 and the conical sleeve 66 run out at a tapered axial end in a hollow cylindrical threadless connecting shaft 68.

[0109] According to a first preferred embodiment of the present invention, the connecting shaft 68 is integrally connected to the conical threaded sleeve 64 or the conical sleeve 66. Figure 7a shows the embodiment with the conical threaded sleeve 64, while Figure 7b shows the embodiment with the conical sleeve 66. Furthermore, the connecting shaft 68 is firmly connected to the compensating sleeve 62 via a predetermined breaking point S.

[0110] The connection between the compensating sleeve 62 and the conical threaded sleeve 64 or the conical sleeve 66 provides the preferred option of manufacturing the one-piece insert 60 as a turned part. "Turned part" means that the insert 60 can be manufactured and machined using the machining process of turning.

[0111] As will become clear from the setting process of the insert insert 60 explained below, the conical threaded sleeve 64 or the conical sleeve 66 is each moved onto the compensating sleeve 62 in order to fasten the insert insert 60 in the pipe 10. During this setting process, the conical threaded sleeve 64 or the conical sleeve 66 radially plastically expands the pipe 10. This preferably results in a positive connection between the pipe 10 and the insert insert 60 in the axial direction of the pipe 10. A remaining residual component of an elastic deformation of the pipe 10 due to the setting of the insert insert 60 preferably ensures a frictional hold of the insert insert 60 in the pipe 10. During the radial expansion, the conical sleeve 66 and the conical threaded sleeve 64 must preferably remain dimensionally stable.The preferred dimensional stability guarantees an unchanged thread geometry as well as an unchanged bushing geometry after completion of the setting process of the insert 60. This applies to both the one-piece and the two-piece insert 60.

[0112] To ensure dimensional stability, a diameter ratio of an inner diameter d N to the minimum outer diameter d Amin of the conical threaded sleeve 64 and the conical sleeve 66 at least 4 / 5, preferably 8 / 11. For the conical threaded sleeve 64, the inner diameter d N the nominal diameter of the thread.

[0113] The inserts 60 shown in Figures 8 and 9 each have the compensating sleeve 62 and the conical threaded sleeve 64 or the conical sleeve 66, which are not permanently connected to one another. Rather, the compensating sleeve 62 and the conical threaded sleeve 64 or the conical sleeve 66 are inserted into one another via the connecting shaft 68 and thus plugged together, so that they are detachable as individual parts but firmly connected to one another. This offers the advantage that the two-part insert 60 of Figures 8 and 9 can be processed in the same way as the one-part insert 60 of Figure 7.

[0114] The two-part design of the insert 60 has the advantage that the compensating sleeve 62 and the conical threaded sleeve 64 or the conical sleeve 66 can each be manufactured using a cold-forming process. The insert 60 is intended to be secured in a pipe 10 to provide a female thread 30 or a bushing. In this setting process, which is explained in more detail below, the compensating sleeve 62 compensates for a gap between a radial inner side of the pipe 10 and a radial outer side of the conical threaded sleeve 64 or the conical sleeve 66.

[0115] In a first step S1, the insert 60 is inserted into the pipe 10 with the conical threaded sleeve 64 in front. Thus, the compensating sleeve 62 is preferably arranged adjacent to the free end of the first pipe end 12.

[0116] Subsequently, a setting or pulling spindle 90 is screwed into the nut thread 30 of the conical threaded sleeve 64 (step S2).

[0117] Thereafter, a counter bearing 92 and the pipe 10 are offset relative to each other so that the hollow cylindrical compensating sleeve 62 and preferably the pipe 10 are supported on the counter bearing 92 (step S3, Figure 11).

[0118] As soon as the hollow cylindrical compensating sleeve 62 is supported on the counter bearing 92, the pull spindle 90 and the counter bearing 92 are displaced relative to each other in such a way that the conical threaded sleeve 64 is pulled into the compensating sleeve 62 (see Figures 11 and 12).

[0119] Preferably, the conical threaded sleeve 64 is pulled into the hollow cylindrical compensating sleeve 62 until both sleeves 64, 62 are aligned with each other or rest together on the counter bearing 92.

[0120] According to a further preferred embodiment of the present invention, the conical threaded sleeve 64 is only partially drawn into the hollow cylindrical compensating sleeve 62, so that a sufficient hold of the plug-in insert 60 is achieved.

[0121] As the conical threaded sleeve 64 is axially displaced into the compensating sleeve 62, the tube 10 is radially expanded. This results in a positive and a force-locking or frictional fastening of the insert 60 in the tube 10. The positive fastening of the insert 60 in the tube 10 is particularly evident in the fact that the diameter of the tube 10 is expanded by 1% to 15% in the area where the insert 60 is formed by the conical threaded sleeve 64. The positive connection between the tube 10 and the insert 60 is evident by a bead adjacent to the second opening of the tube 10.

[0122] During the axial displacement of the conical threaded sleeve 64 into the compensating sleeve 62, the hollow cylindrical connecting shaft 68 ensures preferential entry of the conical threaded sleeve 64 into the compensating sleeve 62. This applies equally to the one-piece (see Figure 7) and the two-piece insert 60 (see Figures 8 and 9). This is because even if a disruptive burr should arise between the compensating sleeve 62 and the conical threaded sleeve 64 when using the predetermined breaking point S, the hollow cylindrical connecting shaft 68 continues to ensure the smooth entry of the conical threaded sleeve 64 into the compensating sleeve 62.

[0123] After the insert 60 has been set, the pull spindle 90 is removed from the nut thread 30 in step S6.

[0124] In order to be able to set the insert 60 with the conical sleeve 66, the threaded bolt 40 is inserted head first into the pipe 10 together with the insert 60. In the same way as in the previously described setting method, the compensating sleeve 62 preferably ends together with the pipe 10. The head underside 43 rests against the conical sleeve 66 (step S1').

[0125] The thread 46 of the connecting bolt 40 is then screwed into a tension nut or similar device (not shown), and the counterbearing 92 is brought into contact with the compensating sleeve 62, or preferably into contact with the compensating sleeve 62 and the tube 10 (step S3'). The tension nut and the counterbearing 92 are then displaced relative to one another so that the head 42 of the connecting bolt 40 pushes the conical sleeve 66 into the compensating sleeve 62 (step S4', Figure 14).

[0126] The setting process is preferably completed when the compensating sleeve 62 and the conical sleeve 66 are aligned with each other or are jointly supported on the counter-bearing 92. According to a further preferred embodiment of the present invention, the conical sleeve 66 is only partially drawn into the hollow cylindrical compensating sleeve 62, so that a sufficient hold of the insert 60 is achieved. The setting process is then completed.

[0127] The connecting bolt 40 is then unscrewed from the tension nut.

[0128] As can be seen from the setting process of the insert 60 in Figures 10 to 12 and 13 to 15, the pipe 10 is radially expanded in order to anchor the nested conical threaded sleeves 64, or the conical sleeve 66 and the compensating sleeve 62, in the pipe 10 in a form-fitting and friction-locking manner. This results in the same deformation properties as described above with respect to the insert 60 with an internal thread.

[0129] Since the tube 10, based on its elastically plastically deformable material, preferably stainless steel, yields to the internal pressure of the conical threaded sleeve 64 or the conical sleeve 66, the geometry of the nut thread 30 is preferably retained despite the setting process.

[0130] To assist in securing the insert insert 60 in the tube 10, the conical threaded sleeve 64 and the conical sleeve 66 preferably have a cone ratio K in the range of 1:12≤K≤1:4, preferably 1:10≤K≤1:6. The cone ratio K technically characterizes the cone shape. For this purpose, the difference between the maximum and minimum outer diameters of the conical threaded sleeve 64 or the conical sleeve 66 is divided by the axial distance between the two outer diameters.

[0131] 6, List of reference symbols

[0132] 1 bolt nut

[0133] 3 pipe clamps

[0134] 10 pipe

[0135] 11 Narrowing at the first pipe end

[0136] 12 first open pipe end

[0137] 13 Ring curvature

[0138] 14 second open pipe 16 through channel

[0139] 18 Constriction

[0140] 20 grouting

[0141] 30 nut threads

[0142] 40 connecting bolts

[0143] 41 Top of the head

[0144] 42 head

[0145] 43 Underside of the head

[0146] 44 shaft

[0147] 46 external threads

[0148] 48 propulsion means

[0149] 50 springs

[0150] 52 ring made of elastic material

[0151] 55 spring

[0152] 60 insert

[0153] 62 compensating sleeve

[0154] 64 conical threaded sleeve

[0155] 66 conical sleeve without nut thread

[0156] 68 hollow cylindrical connecting shaft

[0157] 80 blind rivet nuts

[0158] 82 collar

[0159] 83 Annular bead

[0160] 84 threadless shaft

[0161] 86 shaft area

[0162] 88 internal thread

[0163] 90 setting / pull spindle

[0164] 92 Counter bearing

[0165] G threaded rod

[0166] D Ceiling

[0167] R pipe

[0168] S predetermined breaking point

Claims

Patent claims 1. A bolt nut (1) for fastening a suspended ceiling construction, comprising the following features: a. a pipe (10) with a first open pipe end (12) and a second open pipe end (14), as well as a through-channel (16) connecting the pipe ends (12, 14), b. a nut thread (30) arranged on a radial inner side adjacent to the first pipe end (12), c. a connecting bolt (40), preferably a threaded bolt, with a shaft (44) and a head (42), which is held in a form-fitting and rotatable manner in the through-channel (16) adjacent to the second pipe end (14), and d. a friction means which, in adapted cooperation with a relative rotation of the connecting bolt, generates a friction torque which counteracts the rotation of the connecting bolt. 2.The bolt nut (1) according to claim 1, in which the nut thread (30) is provided by a blind rivet nut (80) fastened to the first pipe end (12) or a plug-in insert (60) with a nut thread (30).

3. The bolt nut (1) according to claim 1 or 2, in which the tube (10) has a constriction (18) of the through-channel (16) adjacent to the second tube end (14), such that an inner diameter of the constriction (18) is smaller than an outer diameter of the head (42) in order to hold the connecting bolt (40) in a form-fitting manner in the through-channel (16).

4. The bolt nut (1) according to claim 3, in which the constriction (18) is provided by a socket insert or a plug-in insert (60) without a nut thread (30) or by a compression (20) of the tube (10).

5. The bolt nut (1) according to claim 2 or 3 in combination with 2 or 4, in which the insert (60) is connected to the pipe (10) in a force-locking and form-locking manner.

6. The bolt nut (1) according to claim 4, in which a ring (52) made of elastic material is arranged between the head (42) of the connecting bolt (40) and the second pipe end (14) as a first friction means in order to increase friction between the head (42) and the socket insert or plug-in insert (60) or compression during relative rotation.

7. The bolt nut (1) according to at least one of the preceding claims, in which a second friction means is provided by a first spring (50) which is arranged in the through-channel (16) between the head (42) of the connecting bolt (40) and the nut thread (30) adjacent to the first pipe end (12) in order to axially preload the connecting bolt (40) towards the second pipe end (14).

8. The bolt nut (1) according to at least one of the preceding claims 1 to 5, in which a second spring (55) is arranged between the head (42) of the connecting bolt (40) and the second pipe end (14) in order to increase friction between the head (42) and the pipe (10).

9. The bolt nut (1) according to at least one of the preceding claims, in which the nut thread (30) and a thread of a threaded bolt (40) as a connecting bolt have the same direction of rotation.

10. A manufacturing method of a bolt nut (1), in particular a bolt nut (1) according to one of the preceding claims, comprising the following steps: a. Providing (H 1 ) a cylindrical tube (10) with a first (12) and a second open tube end (14) and a through-channel (16) connecting the tube ends (12, 14), b. Narrowing (H 2 ) the second tube end (14) by pressing the second tube end (14) or inserting a plug-in insert (60) without nut thread (30) or a socket insert, c. Inserting (H3) a connecting bolt (40) with a head (42) and a shaft (44) into the through-channel (16) such that the shaft (44) protrudes from the through-channel (16) at the second pipe end, and d. Arranging a friction means in the through-channel which, in adapted cooperation with a relative rotation of the connecting bolt with respect to the pipe (10), generates a friction torque which counteracts the rotation of the connecting bolt and e. Pressing (H5) an insert (60) with a nut thread (30) into the first pipe end (12).

11. The manufacturing method of a bolt nut (1) according to claim 10, with the further step: arranging (H4) a first spring (50) in the through-channel (16) for axially pre-tensioning the connecting bolt (40).

12. The manufacturing method according to claim 10 or 11, further comprising: disposing a ring (52) of elastic material as a friction means between the head (42) of the connecting bolt (40) and the second pipe end (14).

13. An insert (60) which is adapted to be formed into a pipe end (12, 14) in a form-fitting and force-fitting manner based on its own radially expanding deformation, and which has the following features: a. a hollow-cylindrical radial compensating sleeve (62) and b1. a conical threaded sleeve (64) with a conical outer contour and a nut thread (30) arranged radially within the conical outer contour or b2. a conical sleeve (66) with a conical outer contour and a cylindrical through-channel arranged radially within the conical outer contour, c. which terminates at a tapered axial end in a threadless hollow cylindrical connecting shaft (68) which engages in a frictionally locking manner in the hollow cylindrical compensating sleeve (62) or which is integrally connected to the compensating sleeve (62) at an axial end facing the compensating sleeve (62) via a predetermined breaking point (S).

14. The plug-in insert (60) according to claim 13, the connecting shaft (68) of which has an outer diameter which is less than or equal to an inner diameter of the compensating sleeve (62).

15. The plug-in insert (60) according to claim 13 or 14, in which the connecting shaft (68) has an axial extension in the range of 5% to 30%, preferably 5% to 15%, of a total axial length of the plug-in insert (60).

16. The insert (60) according to at least one of claims 13 to 15, in which the conical threaded sleeve (64) has a cone ratio K in the range of 1:12≤K≤1:4, preferably 1:10≤K≤1:

6.

17. A cylindrical tube (10) having a first open tube end (12) and a second open tube end (14), in which an insert (60) according to at least one of the preceding claims 13 to 15 is placed at at least one of the tube ends (12, 14).

18. A method for setting an insert (60) according to at least one of claims 13 to 16, comprising the following steps: a. Inserting (S1) the insert (60) into a pipe (10) such that the hollow cylindrical compensating sleeve (62) is arranged adjacent to or adjacent to a first pipe end (12), b. Screwing (S2) a tension spindle into the nut thread (30) of the conical threaded sleeve (64), c. Displacing (S3) the first pipe end (12) such that the hollow cylindrical compensating sleeve (62) is in contact with a counter bearing (92), d. axial displacement (S4) of the pull spindle and the counter bearing (92) relative to each other so that the conical threaded sleeve (64) is displaced into the compensating sleeve (62), and e. unscrewing (S5) the pull spindle from the nut thread (30).

19. A method for setting an insert (60) according to at least one of claims 13 to 16, comprising the following steps: a. inserting (S1') the insert (60) with a connecting bolt (40) arranged therein into a pipe, the head (42) of the connecting bolt (40) being arranged in the connecting channel and the shaft (44) protruding from the insert (60), b. screwing (S2') the shaft (44) of the connecting bolt (40) into a threaded tension sleeve, c. displacing (S3') the first pipe end (12) so that the hollow cylindrical compensating sleeve (62) bears against a counter bearing (92), d. axial displacement (S4') of the threaded tension sleeve and the counter bearing (92) relative to each other so that the conical threaded sleeve (64) is displaced into the compensating sleeve (62), and e. unscrewing (S5') the shaft (44) from the threaded tension sleeve.

Images