DE102022119087A1 - Connecting means, battery assembly, fuel cell and method of making a connecting means - Google Patents

Abstract

Connecting means (1), in particular screw or bolt, comprising an actuation area (10), in particular a head, an elasticity area (30) and a mounting area (50), wherein the connecting means (1) extends in a longitudinal direction (L), wherein a Radial direction (R) is in particular perpendicular to the longitudinal direction (L), wherein the elasticity region (30) lies in the longitudinal direction (L) between the actuation region (10) and the mounting region (50), wherein the mounting region (50) has a thread, in particular a Internal thread, wherein the elasticity region (30) and/or the mounting region (50) are in particular hollow on the inside, wherein the elasticity region (30) has stiffness reduction structures (34), in particular in the form of recesses and/or openings, and/or wherein the elasticity region (30) has, due to its geometry, a lower elasticity than the mounting region (50) and/or than the actuation region (10) and/or wherein the elasticity region has a degressive spring characteristic.

Description

The invention relates to a connecting means, a battery arrangement, a fuel cell and a method for producing a connecting means.

Connecting means are already known from the prior art. These serve to connect different components to one another, especially reversibly. The problem, however, is that if the components to be connected expand during operation, as can be the case with fuel cells or battery arrangements, for example, an enormous load is exerted on the connecting means or on the components to be connected or the Connecting means can come.

It is therefore the object of the invention to provide a connecting means which allows even high dynamic or static expansions to be safely absorbed and/or the resulting load on the connecting means or the components to be connected can be reduced.

This object is achieved with a connecting means according to claim 1, with a battery arrangement and / or a fuel cell according to claim 9 and with a method for producing a connecting means according to claim 10. Further advantages, features and embodiments result from the subclaims, the description and the figures.

According to the invention is a connecting means, in particular a screw or a bolt. Advantageously, the connecting means comprises an actuation region, in particular a head, an elasticity region and preferably a mounting region, wherein the connecting means extends in a longitudinal direction, with a radial direction being in particular perpendicular to the longitudinal direction, wherein the elasticity region can lie in the longitudinal direction between the actuation region and the mounting region , wherein the mounting region has a thread, in particular an internal thread, wherein advantageously or optionally the elasticity region and/or the mounting region are or can be hollow on the inside, and/or wherein the elasticity region has a lower elasticity than the mounting region due to its geometry and/or or as the operating range. The connecting means serves in particular to connect various components to one another, in particular in a non-positive manner. This non-positive connection relates in particular to transverse forces, advantageously in the radial direction or parallel to this direction. In order to be able to establish or transmit a transverse force, in particular perpendicular to the longitudinal direction, between the components to be connected, the connecting means is advantageously designed as a non-positive connecting means. The connecting means in particular has an actuation area. The actuation area advantageously serves to be able to apply an assembly torque to the connecting means, in particular in a form-fitting manner. For this purpose, the actuation area can have actuation surfaces, in particular in the form of an external, internal hexagon, external or internal hexalobular, a multi-tooth and/or a multi-round, each advantageously as an internal and/or external actuation. The normals of the actuation surfaces expediently point in the radial direction. These actuation surfaces can be part of a head, which in turn can form the actuation area. In other words, the actuation area can be formed by or include a head. The actuation area is expediently designed in such a way that it forms a distal end of the connecting means in the longitudinal direction. The longitudinal direction in turn is in particular the direction in which the connecting means has its largest main dimension. For example, the longitudinal direction can therefore or alternatively preferably be the direction in which the length of the connecting means is measured. The center of gravity of the connecting means, the elasticity area and/or the assembly area can be in the longitudinal direction. In particular, one or the radial direction extends perpendicular to the longitudinal direction. Advantageously, the longitudinal direction, the radial direction and a circumferential direction form a cylindrical coordinate system with one another. In addition to the actuation area, the connecting means also has an elasticity area and/or an assembly area. The mounting area of the connecting means has a thread in order to form a connection with another thread, in particular a nut thread. This thread can advantageously be designed as an internal thread in order to achieve a particularly space-saving configuration. Alternatively or additionally preferably, the thread of the mounting area can also be an external thread. This allows particularly simple production to be achieved. The thread itself can be a metric or an inch thread. The mounting area is preferably limited in the longitudinal direction by the distal ends of the thread in the longitudinal direction. Advantageously, the mounting area forms a distal end of the connecting means in the longitudinal direction. The mounting area, which has the thread and/or which is formed by the thread, can limit the connecting means in the longitudinal direction. To reduce the risk of injury during assembly decorate, the mounting area can be limited in the radial direction outwards by a cylindrical surface and/or have such a surface. Seen in the longitudinal direction, the elasticity area lies between the actuation area and the assembly area. Advantageously, the length of the elasticity region in the longitudinal direction is greater than the length of the actuation region and/or the mounting region in the longitudinal direction. In particular, the lengths of all areas are measured in the longitudinal direction. The length of the elasticity region in the longitudinal direction is expediently greater than the sum of the lengths of the actuation region and the mounting region. Advantageously, at least 30%, preferably at least 60% and particularly preferably at least 70% of the length of the connecting means in the longitudinal direction is formed by the elasticity region. The elasticity area and/or the assembly area are in particular hollow on the inside in order to create or be able to provide simple assembly and/or gas passage and/or a reduction in elasticity. Due to its geometry, the elasticity region is designed such that it has a lower elasticity than the assembly region and/or, wherein the elasticity region has deformation structures and/or stiffness reduction structures, in particular in the form of deformation structures. In other words, the geometry of the elasticity area in particular is such that this results in a lower elasticity in the assembly area than the elasticity in the assembly area and/or in the actuation area. The elasticity itself is in particular the spring stiffness or the gradient of the force-path diagram. The decisive factor for the elasticity is the elasticity in the longitudinal direction. In particular, this force-path diagram or the spring stiffness is not dedimensionalized by a geometric parameter. In other words, the elasticity or spring stiffness is therefore not determined by the gradient of the stress-strain diagram but by the force actually applied to the elastic range in comparison to the resulting displacement path or the resulting deformation. The force-path diagram is therefore the force that must be applied in the longitudinal direction to separate the assembly area from the actuation area, while at the same time recording the resulting displacement path of the actuation area in the longitudinal direction from the assembly area. Advantageously, the elasticity area and the assembly area and/or the elasticity area and the actuation area are made of the same material and/or in one piece. This allows particularly good mechanical durability to be achieved. Due to the lower elasticity of the elasticity range - due to the geometry in the elasticity range and/or due to the stiffness reduction structures - a load - due to a swelling and/or static expansion of the components to be connected - can be reduced. In this way, in particular, the load on the connecting means and/or on the components to be clamped or clamped can be reduced, so that the operational reliability and longevity of the connecting means can be increased. Another advantage of such a design is that, in particular, the dynamic loads on the connecting means are reduced.

The elasticity region advantageously has one or a plurality of deformation structures which are or are subjected to bending and/or torsion when the actuation region is displaced in the longitudinal direction in relation to the mounting region. Deformation structures are in particular spirals or beam segments, which can be achieved, for example, by introducing depressions and/or openings or other stiffness reduction structures into the elasticity region, in particular in the radial direction. These deformation structures are therefore in particular not recesses but rather material areas which are mechanically stressed due to the change in length in the longitudinal direction of the elasticity area, in particular due to a displacement of the assembly area in the longitudinal direction in relation to the actuation area. This mechanical stress on the deformation structures is in particular or includes in particular a bending load and/or a torsional load. This type of loading is in particular the predominant type of loading, therefore in particular the type of loading which causes at least 30%, preferably at least 50% and particularly preferably at least 70%, of the comparison stress, in particular when applying the shape change hypothesis (von Mises) and/or the main normal stress hypothesis ( Rankine). In this way, in particular, the achievable reversible degrees of deformation of the deformation structures can be increased, so that ultimately the elasticity of the elasticity range can be reduced. In other words, the spring stiffness of the elasticity region, which can be a synonym for the elasticity, can be reduced by using deformation structures which are subjected to bending and/or torsion when the actuation region is displaced in the longitudinal direction in relation to the mounting region. In this way, a particularly advantageous design of the elasticity range can be achieved.

The elasticity region is advantageously designed in such a way that it has a degressive spring characteristic. In other words, the elasticity or spring stiffness of the elasticity area - with regard to a shift of the actuation area in the longitudinal direction in relation to the assembly area - be such that the elasticity is reduced or decreases with increasing spacing of the actuation area in the longitudinal direction in relation to the assembly area. In this way, it can be achieved in particular that the dynamic loads can be further reduced as the dimensions of the components to be connected increase and the resulting (static) load increases less rapidly. Advantageously, the spring characteristic is degressive in the elastic range. In other words, a degressive spring characteristic is already achieved, especially “before” an irreversible deformation occurs. In this way, in particular, permanent relief and/or mechanical overstressing of the components to be connected and/or the connecting means can be minimized and/or reduced.

The elasticity region advantageously has one or a plurality of stiffness reduction structures, in particular depressions and/or openings, with the stiffness reduction structures forming or limiting the deformation structures. In other words, depressions and/or other stiffness reduction structures can be formed in the elasticity region, in particular in the radial direction, which each border the deformation structures. In particular, these depressions can be designed in such a way that fluid can pass through them from the environment via the recess or depression or breakthrough into the internal area or the overall internal elasticity area. In other words, the breakthrough or breakthroughs can be designed in such a way that they extend from the outside into the hollow inside region of the elasticity region.

The or an internally hollow region of the connecting means can in particular be formed by a central recess, which extends from the mounting region into the elasticity region or even into the actuation region in the longitudinal direction. By providing such a central recess, a fluid flow can also be realized between the individual areas of the connecting means in the longitudinal direction.

Advantageously, the stiffness reduction structures, in particular in the form of a depression or depressions, connect an outer wall of the elasticity region with an inner wall of the elasticity region. The outer wall of the elasticity area borders it in particular outwards in the positive radial direction and the inner wall borders the elasticity area in particular inwards towards the longitudinal direction. This inner wall can in particular border and/or partially form the central recess. As a result, a fluid flow can be achieved in a particularly effective and direct manner from the environment into the internally hollow area of the elasticity area - as already explained.

At least one stiffness reduction structure, in particular in the form of a recess, is expediently designed in such a way that its projection in the longitudinal direction overlaps itself. In other words, at least one depression can be designed in such a way that when this depression is projected onto a plane perpendicular to the longitudinal direction, the projection is closed in itself and can therefore in particular form a ring around the longitudinal direction. This allows a particularly high degree of reduction in elasticity to be achieved, resulting in a particularly advantageous elasticity range. Advantageously, however, the ends of the recess, which forms the projection, which overlaps or is closed on itself, lie at different height positions in the longitudinal direction. In other words, the depression, which can in particular be a breakthrough, is only closed in itself in the projection and not when the depression is viewed taking into account the extension in the longitudinal direction. This can in particular prevent a drastic weakening of the connecting means.

Advantageously, the elasticity region has one or more helical depressions, in particular openings, so that the elasticity region has one or more and/or multi-threaded deformation structures, which is and/or are a spiral. By providing spiral-shaped depressions, which can in particular be openings, it can be achieved in a particularly effective manner that the deformation structures are subjected to torsion. By providing deformation structures that are subjected to torsion, a particularly high degree of reversible deformation capability can be provided. By providing helical deformation structures, a particularly good torsional load can be achieved. As already stated, several helices can also be provided, so that multi-threaded deformation structures can be present in a helical form. In other words, the helical multi-start deformation structures can be designed similar to a multi-start thread.

Advantageously, a deformation structure, in particular the spiral, has a material thickness in the direction of the longitudinal direction and a material thickness in the direction of the radial direction, which can also be referred to as radial thickness, the ratio of the material thickness to the radial thickness being in a range from 0.8 to 1.2, preferably in a range from 0 .9 to 1.1, and particularly preferably in a range from 0.97 to 1.03. The material thickness is therefore the average and/or the maximum or minimum material thickness of the deformation structure measured in the longitudinal direction. The radial thickness of the deformation structure is in particular the material thickness or the material thickness in the radial direction. Advantageously, the ratio of the material thickness to the radial thickness is in a range from 0.8 to 1.2. This allows particularly simple production to be achieved. However, if the material thickness is in a range from 0.9 to 1.1, a particularly advantageous stress distribution can be achieved. However, if the ratio is in a range from 0.97 to 1.03, an approximately homogeneous stress distribution can be achieved on all edges.

Advantageously, at least one depression, preferably a plurality of depressions, is elongated hole-shaped. Preferably, the or at least one, preferably at least a predominant part, and particularly preferably all of the depressions, which are elongated hole-shaped, are designed as openings. A recess is to be considered to be elongated hole-shaped in particular if it has a larger dimension in its main direction of extension than perpendicular to it. In other words, an elongated hole-shaped depression or an elongated hole-shaped opening can therefore be present if the length in the circumferential direction of the opening is greater than the length of the opening in the longitudinal direction. The length of the opening and/or the depression in the radial direction is particularly irrelevant. In other words, only the contour that the depression and/or the breakthrough leaves on an outer wall of the elasticity region can be decisive, particularly for the elongated hole shape. The extent of the elongated hole-shaped opening or the elongated hole-shaped depression, in particular in the circumferential direction, is expediently larger than in the longitudinal direction. Advantageously, the extent in the circumferential direction is at least 10%, preferably at least 20% and particularly preferably at least 30% larger in the longitudinal direction in order to be defined as elongated hole-shaped. Advantageously, the distal end regions of the elongated hole-shaped opening or the elongated hole-shaped recess are formed by a curve. In this way, the material stress increase or the stress increase factor that occurs can be reduced.

The projections of the slot-shaped depressions or stiffness reduction structures in the longitudinal direction preferably form a closed circle, in particular in the longitudinal direction. In other words, the projections of the elongated hole-shaped depression, which could in particular be openings, can be designed in such a way that when viewed in the longitudinal direction, they overlap in such a way that a complete circle or a self-contained ring is formed, in particular the center of gravity this ring lies in the longitudinal direction and/or the ring surrounds the longitudinal direction. In this way, a particularly advantageous reduction in elasticity of the elasticity range can be achieved.

Preferably, at least one depression, which is elongated hole-shaped, has a variable width in the longitudinal direction. The width is in particular the complaint of the walls opposite one another in the longitudinal direction. In particular, the elongated hole, or the elongated hole-shaped depression, is oriented in such a way that it extends perpendicular to the longitudinal direction. In other words, the main extension direction is oriented perpendicular to the longitudinal direction in a projection in the radial direction. In particular, a defined stress distribution can be achieved due to the variable width in the longitudinal direction. Advantageously, the width of the opening or depression, which is elongated hole-shaped, decreases towards the center of the depression or opening. In other words, the width of the depression can initially decrease starting from a distal end of the opening or the depression towards the other distal end of the depression and can increase again after the middle between the distal ends of the depression has been exceeded. In this way, a particularly advantageous anticipation of the mechanical tension that occurs can be achieved. In other words, a particularly voltage-adapted course can be achieved in this way.

Advantageously, a deformation structure, in particular a deformation structure arranged between two slot-shaped openings, has a material thickness, in particular a maximum material thickness, in the direction of the longitudinal direction and a, in particular maximum, material thickness in the direction of the radial direction, which - as already explained - can be referred to as radial thickness, on, the ratio of the material thickness to the radial thickness being in a range from 0.7 to 1.3, preferably in a range from 0.85 to 1.15, and particularly preferably in a range from 0.9 to 1.1 , lies. The material thickness is - as already explained - in particular the average and/or the maximum or minimum material thickness of the ver forming structure measured in the longitudinal direction. The radial strength of the deformation structure is - as already explained - in particular the material thickness or the material thickness in the radial direction. Advantageously, the ratio of the material thickness to the radial thickness is in a range from 0.7 to 1.3. In this way, particularly cost-effective production can be achieved, especially if the deformation structure is at least partially limited in the longitudinal direction by slot-shaped openings. However, if the material thickness is in a range from 0.85 to 1.15, a particularly low local stress concentration can be achieved, especially if the deformation structure is at least partially limited in the longitudinal direction by slot-shaped openings. However, if the ratio is in a range from 0.9 to 1.1, a particularly good increase in elasticity can be achieved.

Advantageously, the ratio of the average height or the maximum height of the openings, in particular the openings which are elongated hole-shaped, in the longitudinal direction to the diameter of the elasticity range is in a ratio of 0.045 to 0.125, preferably in a range of 0.055 to 0.0834, particularly preferred in a range of 0.06 to 0.75. The average height or the maximum height of the openings in the longitudinal direction is the width of the opening in the longitudinal direction, in particular between two walls opposite one another in the longitudinal direction. The average height, on the other hand, is the height of the breakthrough in the longitudinal direction averaged in the direction of the breakthrough between one distal end and the other distal end. The diameter of the elasticity region, on the other hand, is the diameter of the smallest possible circle, which lies in a plane perpendicular to the longitudinal direction and which can just surround the elasticity region. If the ratio is in a range from 0.045 to 0.125, a particularly effective reduction in elasticity can be achieved. However, if the ratio is in a range from 0.055 to 0.0834, particularly simple production can be achieved.

The connecting means is advantageously designed in one piece. A one-piece design means in particular that the material of the connecting means was connected to one another in a single original molding process. In other words, the connecting means may have been further processed after this original forming process, in particular by separating or separating processes, such as laser cutting and/or thread cutting and/or milling or turning, but no further elements were added to the connecting means, for example by welding. Advantageously, however, only the actuation area, the elasticity area and the mounting area are formed in one piece with one another. Alternatively or additionally preferably, the connecting means can also result from cohesive joining of further components to one another, in particular by cohesive joining of the actuation area with the elasticity area and the assembly area. Furthermore, with this cohesive connection, further elements can also be mounted on the connecting means, so that ultimately a connecting means results whose actuation area, its elasticity area and its assembly area have been joined together by cohesive joining, although further elements are force-fitting and/or form-fitting and/or or can be attached to the connecting means in a materially bonded manner. Cohesive joining is particularly advantageous in terms of production costs. The one-piece design of the connecting means and/or the actuation area with the elasticity area and the assembly area, on the other hand, results in a particularly mechanically advantageous design.

Advantageously, the actuation area is hollow, in particular hollow. In this way, in particular, a fluid flow can take place in the hollow area of the actuation area through the elasticity area and/or through the assembly area. As a result, the connecting means presented here can be used particularly advantageously in a fuel cell. Hollow means in particular that the entire actuation area can be hollow in the longitudinal direction.

The actuation area advantageously has a gas connection. This makes it particularly easy to realize a gas flow from and/or into the actuation area. The gas connection can in particular have or form a gas-tight thread and/or a hose connection.

A central recess is advantageously present, which extends in the longitudinal direction from the actuation area over the elasticity area and can extend to the assembly area. This central recess advantageously extends from the distal end of the mounting area to a distal end of the actuation area. In other words, a central recess can extend through the connecting means in the longitudinal direction, in order in particular to be able to realize a fluid flow through the connecting means.

This central recess advantageously has a constant diameter in the actuation area, in the elasticity area and/or in the assembly area. This makes it possible to achieve particularly simple and cost-effective production, which also has mechanically advantageous properties.

The actuation area expediently has actuation surfaces, the actuation surfaces in particular having a normal in the radial direction. As a result, a torque, in particular a form-fitting torque, in particular in the longitudinal direction, can be easily exerted on the connecting means for assembling the fastening means. By providing that the normals of the actuation surfaces point in the radial direction, a particularly cost-effective production can be achieved, which can also be easily actuated.

Advantageously, one or a plurality of depressions and/or openings, in particular depressions and/or openings which form spirals and/or are designed in the form of elongated holes, are laser cut. This results in particularly cost-effective and precise production, so that local (unwanted) stress concentrations can be avoided and/or reduced.

A further aspect of the invention may relate to a battery arrangement and/or a fuel cell, wherein the battery arrangement or the fuel cell has a connecting means as described above and/or below.

• • Vorteilhafterweise Bereitstellen eines Rohlings;
• • Ausformen eines Betätigungsbereichs, insbesondere eines Kopfs, vorteilhafterweise durch Umformen;
• • Ausformen eines, insbesondere hohlen, Montagebereichs, insbesondere mittels Umformen;
• • Ausformen eines Elastizitätsbereichs, insbesondere durch Einbringung von Steifigkeitsreduktionsstrukturen, vorteilhafterweise in der Form von Vertiefungen und/oder Durchbrüchen, in Längsrichtung zwischen dem Betätigungsbereich und dem Montagebereich.

A further aspect of the invention may relate to a method for producing a connecting means, in particular as described above and below. The procedure includes in particular the steps:

• • Advantageously providing a blank;
• • Forming an actuation area, in particular a head, advantageously by forming;
• • Forming an assembly area, in particular a hollow one, in particular by means of forming;
• • Forming an elasticity area, in particular by introducing stiffness reduction structures, advantageously in the form of depressions and/or openings, in the longitudinal direction between the actuation area and the assembly area.

The stiffness reduction structures can be introduced in particular by means of a laser, therefore for example by laser cutting. The connecting means provided by the manufacturing method can in particular have the features, configurations, embodiments and advantages set out above and below. In particular, the shaping of the actuation area and/or the shaping of the elasticity area and/or the shaping of the assembly area is carried out by a forming process in order to achieve a particularly mechanically resilient and yet cost-effective design of a connecting means. The connecting means can in particular be a screw and/or a bolt.

• 1 eine Seitenansicht eines Verbindungsmittels mit Steifigkeitsreduktionsstrukturen in Langlochförmiger Form;
• 2 ebenfalls ein Verbindungsmittel mit Steifigkeitsreduktionsstrukturen als Ausnehmung, wobei die Briete der Steifigkeitsreduktionsstrukturen zur Mitte hin abnehmend ist;
• 3 eine Teilansicht eines Verbindungsmittels in einer Brennstoffzelle;
• 4 eine Vielzahl von Verbindungsmitteln in einer Brennstoffzelle;
• 5 eine Seiten und Schnittansicht eines Verbindungsmittels; und
• 6 ein Verbindungsmittel mit einer Verformungsstruktur, welche eine Spirale ist.

Further advantages and features of the present invention emerge from the following description with reference to the figures. Individual features of the illustrated embodiments can also be used in other embodiments, unless this has been expressly excluded. Show it:

• 1 a side view of a connecting means with stiffness reduction structures in the shape of an elongated hole;
• 2 also a connecting means with stiffness reduction structures as a recess, the width of the stiffness reduction structures decreasing towards the center;
• 3 a partial view of a connection means in a fuel cell;
• 4 a variety of connecting means in a fuel cell;
• 5 a side and sectional view of a connecting means; and
• 6 a fastener with a deformation structure which is a spiral.

In 1 a connecting means 1 is shown, which has an actuation area 10 in the form of a head. The actuation area 10 has a connection thread for a gas connection. In addition, the connecting means 1 also has a mounting region 50, wherein the fastening region 10 and the mounting region 50 form distally opposite end regions of the fastening means 1 in the longitudinal direction L. The elasticity area 30 is located between the fastening area 10 and the mounting area 50. Due to its geometry, the elasticity area 30 has a lower elasticity than the mounting area 50 and than the actuation area 10 and the elasticity area 30 has a degressive spring characteristic. These stiffness characteristics of the elasticity region 30 are determined by the slot-shaped stiffness reduction structures are achieved, which are designed as a breakthrough.

In 2 is a similar fastener 1 compared to that 1 shown. However, the actuation area 10 has an external hexagon with actuation surfaces 12. In the mounting area 50, which is hollow on the inside, there is an internal thread for assembly. The radial direction R points radially from the longitudinal direction L. The deformation structures 32 present in the elasticity region 30 are designed in such a way that they have a variable width in the longitudinal direction L, the width decreasing towards the center of the recess.

In 3 a detailed view of a mounted connecting means 1 can be seen in a fuel point. Both the actuation area 10, which has actuation surfaces 12 in its interior, and the elasticity area 30 are provided with a central recess 60, so that an internally hollow area results in both the elasticity area 30 and in the actuation area 10. The stiffness reduction structures are designed in the shape of an elongated hole. The stiffness reduction structures 34 form the deformation structures 32, the deformation structures 32 having a radial strength RS in the radial direction R.

In 4 A fuel cell is shown which has a large number of connecting means 1. The connecting means 1 penetrate the fuel cell completely in the longitudinal direction L.

In 5 a side view is shown in the lower area and a sectional view through a connecting means 1 is shown in the upper area. The connecting means 1 extends in the longitudinal direction L. In the elasticity region 32, plate spring-like deformation structures 32 connected in series are formed. Due to this geometric design, the elasticity area 30 has a degressive spring characteristic. The radial strength RS in the elasticity range can be seen. Both the mounting area 50 and the elasticity area 30 are hollow on the inside and therefore each have a section of the central recess 60. In order to achieve assembly of the connecting means 1, the mounting area 50 has an internal thread.

In 6 a connecting means 1 is shown. The connecting means 1 has a deformation structure 32, which is a spiral. In other words, the elasticity region 30 has a helical depression which forms the deformation structure 32. The deformation structure 32 has a material thickness MS in the longitudinal direction L. Alternatively, instead of a helical depression, a plurality of helical depressions can also be provided, so that a multi-threaded deformation structure or deformation structures in the form of a spiral result. The mounting area 50 also has a metric internal thread.

List of reference symbols:

1

lanyard

10

Area of operation, especially head

12

Operating surface

30

Elasticity range

32

deformation structures

34

Stiffness reduction structures, depressions, especially openings

50

Assembly area

60

Central recess

L

Longitudinal direction

MS

Material thickness

R

Radial direction

RS

Radial strength

U

Circumferential direction

Claims (10)

Connecting means (1), in particular screw or bolt, comprising an actuation area (10), in particular a head, an elasticity area (30) and a mounting area (50), wherein the connecting means (1) extends in a longitudinal direction (L), wherein a radial direction (R) is in particular perpendicular to the longitudinal direction (L), wherein the elasticity region (30) lies in the longitudinal direction (L) between the actuation region (10) and the mounting region (50), wherein the mounting area (50) has a thread, in particular an internal thread, wherein the elasticity area (30) and/or the mounting area (50) are hollow, in particular on the inside, wherein the elasticity region (30) has stiffness reduction structures (34), in particular in the form of recesses and/or openings, and/or wherein the elasticity region (30) has, due to its geometry, a lower elasticity than the mounting region (50) and/or than the actuation region (10) and/or wherein the elasticity range has a degressive spring characteristic. Connecting means (1) according to Claim 1 , wherein the elasticity region (30) has one or a plurality of deformation structures (32) which are subjected to bending and/or torsion when the actuation region (10) is displaced in the longitudinal direction (L) in relation to the mounting region (50). Connecting means (1) according to one of the preceding claims, wherein the elasticity region (30) has a degressive spring characteristic. Connecting means (1) according to one of the preceding claims, wherein the elasticity region (30) has one or more helical depressions (34), so that the elasticity region (30) has one or more and/or multi-threaded deformation structures (32), which are a spiral. Connecting means (1) according to one of the preceding claims, wherein at least one depression (34), preferably a plurality of depressions (34), is/are elongated hole-shaped. Connecting means (1) according to one of the preceding claims, wherein the projections of the slot-shaped depressions (34) in the direction of the longitudinal direction (L) form a closed circle, in particular around the longitudinal direction (L). Connecting means (1) according to one of the preceding claims, wherein at least one depression (34), which is elongated hole-shaped, has a variable width in the longitudinal direction (L). Connecting means (1) according to one of the preceding claims, wherein a central recess (60) is present, which extends in the longitudinal direction (L) from the actuation area (10) via the elasticity area (30) to the mounting area (50), in particular to the distal end the assembly area (50), extends. Battery arrangement or fuel cell comprising a connecting means (1) according to one of the preceding claims. Method for producing a connecting means (1), in particular according to one of Claims 1 until 8th , comprising the steps: • In particular providing a blank; • Forming an actuation area (10), in particular a head, advantageously by forming; • Forming a hollow assembly area (50), in particular by means of forming; • Forming an elasticity area (30), in particular by introducing stiffness reduction structures (34), advantageously in the form of depressions and/or openings, in the longitudinal direction (L) between the actuation area (10) and the mounting area (50).

Images