Source: https://patents.google.com/patent/DE102006028537B3/en
Timestamp: 2020-01-19 01:44:27
Document Index: 455984018

Matched Legal Cases: ['art 26', 'art 26', 'arts 26', 'arts 26', 'art 28', 'art 28', 'arts 26', 'art 28', 'art 28', 'art 28', 'art 26', 'art 26', 'art 28', 'art 26', 'art 28', 'art 28', 'art 26', 'art 26', 'art 28', 'art 28', 'art 28', 'art 28', 'art 28', 'art 28', 'art 26', 'art 26', 'art 26', 'art 28', 'art 26']

DE102006028537B3 - Self-punching rivet has head outer face and shank outer face connected by conical or slightly curved chamfer below head and radius below head which merges tangentially both into chamfer and also into shank outer face - Google Patents
Self-punching rivet has head outer face and shank outer face connected by conical or slightly curved chamfer below head and radius below head which merges tangentially both into chamfer and also into shank outer face
DE102006028537B3
DE102006028537B3 DE200610028537 DE102006028537A DE102006028537B3 DE 102006028537 B3 DE102006028537 B3 DE 102006028537B3 DE 200610028537 DE200610028537 DE 200610028537 DE 102006028537 A DE102006028537 A DE 102006028537A DE 102006028537 B3 DE102006028537 B3 DE 102006028537B3
DE200610028537
Sumanjit Singh
Singh Sumanjit Dr
2006-06-21 Application filed by Singh Sumanjit Dr filed Critical Singh Sumanjit Dr
2006-06-21 Priority to DE200610028537 priority Critical patent/DE102006028537B3/en
2006-06-21 Priority claimed from DE200620013981 external-priority patent/DE202006013981U1/en
2007-05-10 Publication of DE102006028537B3 publication Critical patent/DE102006028537B3/en
2007-08-08 First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=37950189&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=DE102006028537(B3) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Described are a punch rivet and a die for producing a stamped rivet connection. The punch rivet is characterized by special rivet foot and lower head geometries. In the region of the rivet foot, the outer and inner shaft surfaces are connected by a small radially outer radius and a larger radially inner radius, which merge tangentially into one another. The angle enclosed by the common tangent with a radial plane is in the range of 10 ° + - 20 °. In the area of the rivet head, a conical lower head chamfer is provided, which encloses an angle in the range of 25 ° -15 ° with a radial plane of the punch rivet and transitions tangentially into the cylindrical outer surface of the rivet shank over a relatively small radius. The development of this rivet geometry is based on the knowledge that, in addition to the quality criteria considered so far, such as the undercut of the spread punch rivet, further quality criteria such as engagement length, support depth and thickness of the material radially surrounding the rivet base are to be taken into account in order to achieve optimal load bearing behavior. By means of the invention, the requirements for the strength and hardness of the rivet material can be reduced, the costs for producing the rivets can be reduced and the setting forces necessary for setting the punch rivets can be reduced. The punch rivet can be designed as a simple rivet or as a functional element, in particular as a punching pin or punching nut. The matrix ...
The The present invention relates to a punch rivet which is considered to be simpler Rivet or as a functional element such as a punching pin or punching nut can be formed. In particular, the Invention a punch rivet in the form of a semi-hollow punch rivet or Hollow punch rivet for producing a punched rivet connection with a or more plate-shaped joining parts (Sheets). The invention further relates to a in the production the punch rivet connection usable die. The template is preferably adapted in a special way to the geometry of the punch rivet, but can also be used in conjunction with conventional punch rivets become.
Punching as a joining method has become increasingly important in the recent past. An important parameter for the joining process as well as the connection quality of the punched rivet connection is the geometry of the punch rivet. Numerous different geometries of the punch rivet are known in the prior art, see eg EP 0 720 695 . EP 1 064 466 . EP 1 229 254 . EP 1 387 093 . DE 44 31 769 . DE 203 19 610 U1 . DE 200 01 103 U1 , US 2004/0068854 A1, JP 2001159409 A . JP 09317730 A among others
at The design of punch rivets was commonly used in the art from the so-called "pierce-and-roll" behavior of the punch rivet out. "Pierce-and-roll" means the Punch rivet possible soon after penetration (pierce) spread in the lower plate will (roll) to maximize spreading and thus the largest possible To achieve undercut of the punch rivet in the Stanznietverbindung. These considerations have rivet geometries such as those of the C rivet and corresponding matrices, for example with a mandrel.
Although the C-Rivet has proven successful in practice further improvements such as e.g. an improved bearing behavior of the punched rivet connection and improved economics of the joining process desirable.
Of the present invention is based on the object, a punch rivet for making a stamped rivet connection with one or more joining parts to create an optimization of the bearing behavior of the punched rivet connection and a particularly economical joining method, in particular by Reduction of the strength and hardness requirements of the Punch rivet material and a reduction of the setting forces required for the joining process allowed. Furthermore, a purpose for this suitable die are created, preferably to the geometry the inventively designed punch rivet adapted, but also in conjunction with other rivet geometries, can be used.
piercing rivets according to the present Invention for solution This object is defined in claims 1 and 2.
Of the formed according to the invention Punch rivet is characterized in particular by a special Nietfußgeometrie and a special lower head geometry as claimed in claims 1 and 2 result.
According to the solution of claim 1, the shaft outer surface and shank inner surface are connected at the rivet head end by a radially outer first radius R 1 and a radially inner second radius R 2 , which merge tangentially into each other. The common tangent of R 1 and R 2 forms an angle α of 10 ° ± 20 ° with a radial plane of the punch rivet. The first radius R 1 , which merges tangentially into the shaft outer surface or is replaced by a chamfer of corresponding length, is 0.3 ± 0.2 mm, and the second radius R 2 , which merges tangentially into the shaft inner surface, is (0.7 to 1.2) (d N - di) / 2, esp. (0.8 to 1.0) (d N - d i ) / 2. The factor (0.7 to 1.2) or (0.8 to 1.0) is preferably chosen to be increasingly larger as the R 1 increases.
If, with radii R 1 and R 2 selected within the given ranges of values, it is found that no second radius R 2 can be found, which affects both the first radius R 1 and the shaft inner surface, then according to the alternative solution of claim 2 between the second Radius R 2 and the shaft inner surface a third radius R 3 is provided, which merges tangentially into both the second radius R 2 as well as in the inner shaft surface and is 0.8 ± 0.4 mm. The angle α between the common tangent of R 1 , R 2 and a radial plane of the punch rivet is then in the range of 10 ° ± 5 ° to choose.
The under head geometry of the rivet head is characterized in both solutions in that the head outer surface and the stem outer surface are joined by a conical or slightly curved lower head bevel and a lower head radius of which the underhead radius tangentially merges into both the lower head chase and the shank outer surface. In the case of a conical Unterkopffase the Unterkopffase includes with a radial plane of the punch rivet an angle β of 25 ° ± 10 °, in particular 25 ° ± 7 °. In the case of a slightly curved Unterkopffase applies to the radius of curvature R 7 ≥ 2.0 mm.
The Punch rivet geometry according to the invention means a departure from the above-described "pierce-and-roll" behavior of the punch rivet.
As will be explained in more detail with reference to the figures, the present invention is based on the finding that, in addition to the quality criteria of the undercut of the spread Stanznietabschnittes and the axial minimum thickness of the die-side joining part (plates) on Nietfuß further quality criteria of the Stanznietverbindung to achieve optimum load-bearing behavior are. This is, as will be explained in more detail with reference to the figures, the so-called engagement length L (engagement between the outer surface of the Nietfußes and the die-side joining part), the so-called support depth T (axial component of the engagement length L) and the radial thickness t NF of the rivet foot enclosing mattress-side joining part.
The rivet geometry was chosen according to the invention so that the engagement length L, the support depth T and the thickness t NF of the punched rivet connection are maximized. The consideration here is that the carrying behavior of the punched rivet connection can be improved if a maximization of the undercut of the spread punch rivet section is abandoned in favor of an improved "frictional connection" between the rivet shank and the die-side joining part (sheet metal) Increasing the engaged cross-sections and outer surfaces of the punch rivet on the one hand and the joining parts on the other hand, whereby the specific load of the force-transmitting areas is minimized. This also leads to a reduction in the radial compressive stresses, so that the size of the total stresses resulting from the overlay remains limited under external loading of the punched-rivet joint. Due to the achieved by the invention maximization of the engagement length L, the support depth T and the thickness t NF with sufficient undercut of the spread Stanznietabschnittes and minimal axial joint thickness tmin the surface pressure between punch rivet and joining parts is reduced, which in turn improves the stiffness and fatigue strength of the punched rivet. The Nietfußgeometrie according to the present invention also leads to the fact that in the joining process of the punch rivet penetrates the punch-side joining part substantially in a cutting operation and that the rivet shank is only spread when a penetrate into the matrizenseitige joining part. This results in a lower-resistance sliding of the Nietfußes along the Fügeteile. This situation leads to a minimization of the required setting force, which in turn has the consequence that the requirements for the hardness and strength of the punch rivet material significantly reduced and the production and processing of the punch rivets are simpler and considerably cheaper.
In a further embodiment of the invention, a specially dimensioned die is provided for the punch rivet designed according to the invention. An inventively designed die is defined in claim 19. Hereafter applies to the die diameter D M = d N + (0.8 to 1.5) 2t M , esp. d N + (0.7 to 1.2) 2t M for joining parts made of a material with good deformability, in particular of a wrought alloy, and D M ≤ 2.2 d N ; for joining parts made of a cast material or other material of low deformability, where d N is the shank outer diameter of the rivet shank and t M is the thickness of the die-side joining part. The depth T M for joining parts made of a material with good deformability is preferably in the range T M = (1.0 to 2.5) t M , inbes. T M = (1.1 to 2.2) t M. The depth T M for joining parts made of low-deformation materials is preferably ≦ 0.15 D M.
From these formulas it follows that the die diameter is smaller than in the prior art. The smaller die diameter in turn be favored the desired reduction of the spreading of the rivet shank.
According to claim 20 is an inventively designed Matrix characterized in that the die on Matrizenboden having a central recess, which during the joining process as pressure relief during the joining process provides.
Of the formed according to the invention Punch rivet is particularly suitable for joining parts of higher strength steels, especially AHSS steels and metastable austenitic steels such as e.g. H400. Basically the punch rivet, however, for joining of parts to be joined Made of any materials including plastic. The punch rivet can be made of conventional Materials, however, as mentioned, hardness and strength of the material can be significantly lower than in the prior art. The enabled by the invention Reduction of the required setting forces and the considerable improvement allow the carrying behavior For example, that with the claimed rivet geometry even Rivets of aluminum alloys, e.g. AlMgSil T6 / T7 for riveting Semi-finished aluminum are suitable.
Of the formed according to the invention Punch rivet may be a semi-hollow punch rivet (in which the central shaft bore a blind hole is) or a hollow punch rivet (in which the central Shaft bore is a through hole). In the punch rivet can it is a pure rivet or a functional element, in particular a punch or a punch nut act.
Of the Rivet shaft may have a cylindrical shaft outer surface or an axially grooved shaft outer surface. The axial corrugation serves as anti-rotation during the joining process, in particular when the punch rivet is designed as a functional element is. The axial corrugation of the shaft outer surface requires no additional Joining forces. This is an advantage over stellate Corrugations under the rivet head, as known in the art are.
If the punch rivet is designed as a functional element, he can also used in conjunction with a single joining part (sheet metal).
Of the Rivet head is preferably designed as a countersunk head. Depending on the application However, a flat head can also be used.
Further advantageous embodiments and refinements of the invention are in the dependent claims Are defined.
Based The drawings are further details of the invention as well preferred embodiments of the invention explained. It shows:
1 an axial section of a punch rivet formed according to the invention;
2 a half axial section through a finished punch rivet connection to illustrate certain quality criteria of the punched rivet;
3 to 6 schematic representations of a Stanznietvorganges in different phases of operation;
7 a sectional view of a portion of a modified die;
8th an axial section through a modified embodiment of the punch rivet;
9 a cross section in the direction of arrows IX-IX in 8th ,
The punch rivet 2 is formed with respect to a central axis X rotationally symmetrical and consists of a rivet head 4 and a rivet 6 with a central shaft bore 8th , which is designed as a blind hole. The rivet head 4 has a flat top 10 and a cylindrical head outer surface 12 , The head outer surface 12 has a diameter d K and an axial height H K.
The rivet shaft 6 has a cylindrical shaft outer surface 14 and a cylindrical inner shaft surface 16 , which the shaft bore 8th limited. The cylindrical shaft outer surface 14 has a shaft outer diameter d N , and the cylindrical shaft inner surface has a shaft inner diameter d i .
The head outer surface 12 is with the shaft outer surface 14 via a subheading chamfer 18 and a radius R 4 connected. (In the present context, the term "radius" is understood to mean an annular surface which has the shape of a circular arc with the radius R in an axial section.)
The radius R 4 extends tangentially into both the lower head chamfer 18 as well as in the shaft outer surface 14 while the subheading chamfer 18 on the head outer surface 12 (eg over a radius or a sharp edge) immediately adjacent. The subheading chamfer 18 closes with a radial plane of the punching tes 2 an angle β.
At Nietfußende is the shaft outer surface 14 with the inner surface of the shaft 16 connected via a first radius R 1 to the center M1 and a second radius R 2 to the center M2 and possibly via a third radius R 3 . The radius R 1 is tangential both in the shaft outer surface 14 as well as in the second radius R 2 over. The second radius R 2 is tangential either directly into the shaft inner surface 16 or in the third radius R 3 via, which in turn tangentially into the shaft inner surface 16 passes.
As in 1 can be clearly seen, the radius R1 is much smaller than the radius R2. The common tangent Tan of the radii R1 and R2, which is perpendicular to the joining of the centers M1 and M2, closes with a radial plane E of the punch rivet 2 an angle α.
The shaft bore 8th has a conical bottom surface at the rivet head end 24 a cone angle γ, through an outer Schaftbohrungsradius R5 with the shaft inner surface 16 is connected and ends in the region of the central axis X in a radius R 6 . The shaft bore 8th has a shank bore depth t B , which is measured from the Nietfußende to the point at which the imaginary extensions of the conical bottom surface 24 and the inner surface of the shaft 16 intersect each other. The thickness of the rivet head 12 on the central axis X is denoted by D K.
Before discussing the specific value ranges of the variables determining the geometry of the punch rivet according to the invention, reference will be made to FIG 2 outlines the basic considerations that led to the present invention. As already explained at the outset, the undercut H of the spread rivet shaft section and, secondly, the axial minimum thickness t min of the die-side joining part (sheet) were used as a quality criterion in the prior art in the assessment of a finished punch rivet connection. Basically, the aim was to make the undercut H and the minimum thickness t min as large as possible.
In contrast, the present invention is based on the consideration that, in addition to the undercut H and the minimum thickness t min, the engagement length L, the support depth T and the radial thickness t NF of the joining part (sheet metal) surrounding the rivet foot are essential quality criteria of the stamped rivet connection. How out 2 it can be seen that the engagement length L is the length of the engagement between the outside of the rivet shank 6 and the matrizenseitigen joining part 26 , and the support depth T is the axial component of the engagement length L. The radial thickness t NF of the nietfuß enclosing the die-side joining part 26 is measured at the radially outermost point of the rivet foot.
In accordance with the teachings of the present invention, it is generally desirable to maximize the engagement length L, the support depth T and the radial thickness t NF . As has been determined on the basis of extensive investigations, it is possible in this way to improve and optimize the bearing behavior of the punched-rivet connection, as will be explained in more detail below.
Further underlying the invention considerations concern the design of the rivet head, the rivet shank and the die used to make the riveted joint as follows also explained in more detail becomes.
Design of the rivet foot
The geometry of the rivet foot according to the illustrated embodiment of the present invention is determined by the following value ranges: R 1 = 0.3 ± 0.2 mm R 2 = (0.7 to 1.2) (i.e. N - d i ) / 2, esp. R 2 = (0.8 to 1.0) (i.e. N - d i ) / 2 α = 10 ° ± 20 °.
The radius R 1 can be replaced by a bevel, for example, 45 °, as long as the length of the chamfer is not greater than the corresponding secant of the radius R 1 .
These ranges of values apply to the case where the radius R 2 is directly tangential to the inner surface of the shaft 16 passes. When you can not find the radius R 2 is within the specified value range, both the Ra dius R 1 as well as the shank interior 16 tangent, the radius R 2 is to be connected via a further radius R 3 with the shaft inner surface. For R 3 and the angle α, the following value ranges are to be selected: α = 5 ° ± 10 ° R 3 = 0.8 ± 0.4 mm.
If the radius R 1 is less than or equal to 0.2 mm, the angle is expediently α = 5 ° ± 10 °. With a larger radius R 1 (up to 0.4 mm), the angle α = 10 ° ± 20 °.
An essential parameter of the geometry of the rivet base is the angle α, which is the common tangent Tan of the radii R 1 and R 2 with the radial Bene E of the punch rivet includes. As shown and resulting from the specified value ranges, the angle α is very small and may even be negative. This makes it clear that the rivet foot, in contrast to the prior art, is somewhat blunt, ie has no sharp-edged cutting edge in the narrower sense. This situation has a significant influence on the punch riveting process and the formation of the punched rivet connection, as illustrated by the example of a punched rivet connection between two parts to be joined (sheets) with reference to FIGS 3 to 6 explains:
When punching rivets are known to be joined joining parts 26 . 28 between the top of a die 30 and the bottom of a hold-down 32 held. The matrix 30 has a cavity 34 that of a floor surface 36 , preferably in the form of a projection (mandrel) and a cylindrical peripheral surface 38 is limited. During the joining process the punch rivet becomes 2 from a stamp (not shown) in the parts to be joined 26 . 28 pressed, and here are deformed portions of the joining parts 26 . 28 in the cavity 34 the matrix 30 into deformed. The punch rivet pierces the punch side joining part 28 , separates a slug here 28a from the joining part 28 from, and deforms the matrizenseitige joining part without punching this. As a result, a kind of "closing head" is formed, so that the two joining parts 26 . 28 between the rivet head 4 and the "closing head" are held together form fit.
The above-defined geometry of the Nietfußes has the following effects on the joining process and the formation of the punched rivet:
a) In the first part of the joining process, the rivet foot pierces the punch-side joining part 28 without excessive deformation of the part to be joined 28 , It is therefore largely a pure punching or cutting process.
b) Since in this punching the Nietfuß the punch side joining part 28 penetrates substantially in a cutting process, the Nietfuß and the rivet shank undergo no major deformation. This is done by the 4 and 5 illustrated. The result is that for punching the punch-side joining part 28 required setting force is comparatively low.
c) The rivet foot now presses the punched slug 28a together with the matrizenseitigen joining part 26 down into the cavity 34 the matrix 30 until the lower joining part 26 on a floor surface 36 the matrix 30 is applied.
d) If the rivet foot is the punch-side joining part 28 pierced, the rivet "glides" on the surface of the grout 28a radially outward and axially downwards, so that the material of Butzens 28a within the shaft bore 8th Extruded radially inward and the matrizenseitige adherend 26 deformed radially outwards and axially towards the die bottom ( 5 . 6 ). In this case, the undercut H ( 2 ). The matrizenseitige joining part 26 encloses the Nietfuß without the die-side joining part radially and axially thinned too much or even cut.
In short, thus, the joining process is characterized in that the punch-side joining part 28 is largely punched in a pure cutting process, without the rivet shank 6 and the stamp-side joining part 28 Be deformed excessively, and that the expansion (spreading) of the rivet shank 6 only when penetrating into the matrizenseitige joining part 26 he follows. This ensures that the engagement length L, the support depth T and the radial thickness t NF of the rivet foot enclosing the die-side joining part 26 be maximized.
The consequence is that the adhesion (frictional engagement) between the rivet shank 6 and the parts to be joined 26 . 28 makes a significant contribution to the carrying behavior. In particular, this is the specific load of the force-transmitting areas between the punch rivet 2 and the parts to be joined 26 . 28 minimized. In addition, there is a reduction of the radial compressive stresses within the punched rivet joint, so that remains at an external load of the punched rivet, the sum of external and internal stresses within reasonable limits. Furthermore, by maximizing L, T and t NF with sufficient undercut H and minimum thickness t min, the surface pressure between the punch rivet becomes 2 and the parts to be joined 26 . 28 reduces, thereby improving the rigidity and fatigue strength of the punched rivet joint.
One Another important advantage of this embodiment of the punched rivet connection exists, as already mentioned, in a significant reduction in the production of the riveted joint required setting force. This not only benefits on the design and operation of the setting tool, but leads In particular, the requirements for the hardness and strength of the punch rivet clearly be reduced. So can for producing a punched rivet connection between joining parts specified materials punch rivets are used, their hardness and Strength significantly lower than in the prior art. For example can be rivets made of conventional Aluminum alloys such as e.g. AlMgSil for the riveting of aluminum semi-finished products use.
Another advantage of the described design of the punched rivet connection is that gaps between the punch rivet, on the one hand, and the joining parts, on the other hand, as well as between the joining parts, are avoided or at least minimized. This affects, along with the üb properties of the rivet connection, advantageous to the load-bearing behavior and in particular the vibration resistance behavior of the punched rivet connection.
layout of the rivet head
The Design of the rivet foot is in connection with the design of the remaining punch rivet, in particular of the rivet head, the rivet shank and the shaft bore.
In the illustrated embodiment, the rivet head 4 as a countersunk head with a conical lower head chamfer 18 formed with the shaft outer surface 14 is connected by the radius R 4 and the cylindrical head outer surface 12 cuts.
For the head diameter d K of the rivet head designed as a rivet head 4 applies: d K = (1.3 to 1.8) d N , esp. d K = (1.4 to 1.65) d N
For the axial length H K of the head outer surface 12 applies: H K = (0.025 to 0.2) d N , especially H K = (0.025 to 0.12) d N ,
With increasing head diameter d K , H K is to be selected larger. The specified ranges apply in particular to outer shank diameter d N ≦ 6 mm.
The angle β, the Unterkopffase 18 with a radial plane is in the range of 25 ° ± 10 °, esp. 25 ° ± 7 °. The radius R 4 is 0.6 ± 0.4 mm, in particular 0.5 ± 0.2 mm.
The Unterkopffase can, as on the right side of the 1 indicated by dashed lines, are also formed slightly curved, wherein the curvature deviate only slightly from the conical surface and the radius of curvature R 7 should be ≥ 2.0 mm.
The angle β or the radius R 7 and the radius R 4 are in this case selected so that the force for closing the gap between the rivet head 4 and the stamp-side joining part 28 ( 2 and 6 ) and thus the setting force is as low as possible. The size of the setting force is determined by the difference between the angle β and the radius R 7 of the Unterkopffase 18 and the corresponding angle of the top of the punched punch-side joining part 28 and influenced by the size of the radius R 4 .
If the angle β is too large or the radius R 7 too small, a very high setting force is required to the gap between the top of the head and stamp-side joining part 28 close. If the angle β is too small, a gap arises between the punch rivet 2 and the stamp-side joining part 28 in the area of the radius R 4 . The rivet head 4 is then subjected to bending and can easily break off when trying to close this gap by a correspondingly large setting force.
If the radius R 4 chosen too large (as is the case in the prior art, for example, the so-called C-rivet), so the punch rivet in the region of the radius R 4, the adjacent corner of the punched punch-side joining part 28 deform accordingly and this material of the punch-side joining part 28 partially displace radially outward. For this purpose, a very high force is required, which in turn increases the size of the required setting force. If the radius R 4 is too small, the notch effect caused thereby can lead to breakage of the rivet head 4 to lead.
The described, designed as a countersunk rivet head, in particular the above-defined lower head geometry, is quite generally suitable for riveting parts to be joined from all metallic materials and possibly also other materials. When joining plastics, especially fiber-reinforced plastics, even flat rivet heads, so-called flat heads, with small transition radii to the rivet head may be appropriate. In these cases, the head diameter d K is generally selected to be larger than in the countersunk rivets in order to reduce the specific surface load between the Nietkopfunterseite and the top of the punch-side joining part. The size of the rivet head diameter is then outside the range defined above.
Design of rivet shank with shaft bore
In the prior art, the shank outer diameter d N of semi-hollow rivets is usually between 3 and 8 mm, and the wall thickness of the rivet shank is usually between 0.5 and 2.0 mm. The total length of the punch rivet is rarely greater than 10 mm. Semi-hollow punch rivets used in automobile technology for connecting body parts often have a shank outer diameter d N of 5.3 mm or 3.2 mm.
Also for punch rivets according to the present invention, the shaft outer diameter d N can be selected in these areas. Preferably, the shank outer diameter d N is in the range of 5.0 to 6.0 mm. As will be explained in more detail, however, in punch rivets according to the present invention, the shaft outer diameter d N can basically be chosen slightly larger than in the prior art, since the present invention formed punch rivets require lower setting forces.
The shaft inside diameter d i is preferably from (0.5 to 0.8) d N. For the variables R 5 , R 6 , γ, T B and D K preferably the following value ranges apply: R 5 = 0.7 ± 0.5 mm, esp. R 5 = 0.8 ± 0.3 mm R 6 = 0.9 ± 0.5 mm, esp. R 6 = 0.8 ± 0.3 mm γ = 110 ° to 140 °, esp. γ = 110 ° to 130 ° t B ≥ 0.2 d N , especially t B ≥ 0.3 d N D K ≥ 0.15 d N ,
The specified value ranges for the sizes determining the shaft geometry ensure that the rivet shank 6 sufficient pressure stability (no impermissible upsetting during the joining process), sufficient buckling and buckling resistance (no buckling and / or buckling of the rivet shank during the joining process) and sufficient bending and compression strength (targeted deformation during the joining process) can be awarded in each application.
The illustrated geometry and in particular the angle γ of the shaft bore have been chosen to facilitate the manufacture of the shaft bore. It should be noted, however, that the geometry of the shaft bore can also be chosen differently. For example, the bottom of the shaft bore dome-shaped, that is in the form of a circular arc with a transition to the shaft inner surface 16 over the radii R 5 , are formed. Other bore geometries are possible.
Production of the punch rivet
As already mentioned, the punch rivets according to the present invention allow significantly reduced setting forces compared to the prior art. Investigations have shown that the setting forces required to make the riveted joint are 20% lower on the order of magnitude. This in turn makes it possible to make the shank outer diameter d N and thus also the shank inner diameter d i larger than in the prior art, without jeopardizing the pressure stability, buckling and buckling strength as well as the bending and crushing strength of the punch rivet.
An enlargement of the shank outer diameter d N of the punch rivet enables a technologically facilitated and more economical production of the punch rivet:
In the production of stamped rivets by cold forming the shaft bore is formed by means of a so-called pins. The smaller the cross section of the shaft bore 16 and thus the pin is, the more difficult is the production of the punch rivet.
in this connection is taken into account, that the cost of the rivet production depend substantially on the cost of the production tools, wherein the life of the manufacturing tools plays a crucial role. An enlargement of the Cross-section of the shaft bore and thus of the pin leads to a significant Facilitating the production and beyond - because of the improved leadership of the pin - to a Improvement of the manufacturing accuracy of the shaft bore. hereby the service life of the production tools is extended disproportionately, so that the cost of the rivet production are reduced accordingly.
It should also be borne in mind in these considerations that a smaller change in the outer shaft diameter d N can result in a greater change in the inner shaft diameter d i without adversely affecting the stability of the punch rivet. A change of the shaft outer diameter d N by 0.3 mm, for example, allows a change of the inner shaft diameter d i by 0.4 mm, without the pressure stability of the rivet shank is impaired. A 0.3 mm change in internal shaft diameter d i = 2.9 mm results in a 33% cross-sectional enlargement of the pin, and a 0.4 mm change in 41% cross-sectional enlargement of the pin.
Out These numerical examples show that the inventively designed Punch rivets can be made much more economical than Punch rivets of the prior art.
Design of the die
A significant influence on the joining process and the formation of the punched rivet connection has the die used in the production 30 , in particular the volume or the diameter D M of the cylindrical peripheral surface 38 of the cavity 34 the matrix 30 , please refer 2 to 6 ,
For the diameter D M is preferably: D M = [d N + (0.6 to 1.5)] t M , especially D M = [d N + (0.7 to 1.2)] t M for joining parts made of materials with good deformability, in particular wrought alloys. In this case, t M is the thickness of the die-side joining part 26 , Thus, the diameter D M of the die increases 30 with the thickness of the die-side joining part 26 to. Conveniently, the depth T M of the cavity should also 34 the matrix 30 with the thickness of the die-side joining part 26 be chosen larger. Preferably: T M = (1.0 to 2.5) t M , especially T M = (1.1 to 2.2) t M ,
The specified value ranges result in the diameter D M of the peripheral surface 38 the matrices, which are small compared to the prior art. This reduction of the cavity of the die, in particular of the diameter D M , reduces the so-called "cutting gap", ie the gap between the shank outer diameter d N and the inner die diameter, ie the diameter D M. This in turn favors the connection with the design of the Nietfußes In particular, thereby the punching of the punch-side joining part 28 in a "cutting process", the deformation of the die-side joining part 26 as well as the corresponding movements and deformations of the rivet shank 6 favored.
For joining parts made of cast materials as well as other materials of low formability or low elongation at break, such as magnesium, the following applies preferably: D M ≤ 2.2 d N . T M ≤ 0.15 D M
In the embodiment of the 3 to 6 is the floor area 36 the matrix 30 provided in a conventional manner with an upwardly projecting mandrel. 7 shows an embodiment of a template according to the invention 30 ' in which the floor area 36 ' with a central depression 40 is provided. In the illustrated embodiment, the recess 40 cylindrically shaped and has a diameter D EB ≤ 0.5 D M and a depth T EB ≥ 0.3 d N. For the radius R EB : R EB ≥ 0.3 mm, in particular 0.4 to 1.0 mm.
The depression 40 ensures pressure relief during the joining process, which avoids excessive radial stresses in the riveted joint and reduces the risk of cracking.
The 8th and 9 show a modified embodiment of a punch rivet 2 ' , While in the embodiment of the 1 to 6 the shaft outer surface 14 is cylindrical, is the shaft outer surface of the modified punch rivet 2 ' with an axial corrugation 42 Mistake. The axial corrugation 42 forms an anti-rotation during the joining process, which is particularly advantageous if the punch rivet is designed as a functional element (not shown) with a bolt or nut-shaped approach to the rivet head. The axial corrugation 42 also ensures good guidance of the punch rivet 2 ' without thereby increasing the required joining force.
Punch rivet with a rivet head ( 4 ) and a rivet ( 6 ) with a central shaft bore ( 8th ), which have a common central axis X, wherein the rivet head ( 4 ) a substantially cylindrical head outer surface ( 12 ) of a given head diameter d K , the rivet shank ( 6 ) a shaft outer surface ( 14 ) of a predetermined outer shaft diameter d N and a central shaft bore ( 8th ) limiting inner surface of the shaft ( 16 ) of a predetermined internal shaft diameter d i , the head outer surface ( 12 ) and the shaft outer surface ( 14 ) by a conical or slightly curved Unterkopffase ( 18 ; 18 ' ) and a sub-head radius R 4 which tangentially into both the Unterkopffase ( 18 ; 18 ' ) as well as in the shaft outer surface ( 14 ), and the shaft outer surface ( 14 ) and the inner surface of the shaft ( 16 ) are connected at the Nietfußende via a radially outer first radius R 1 and a radially inner second radius R 2 , which merge tangentially into each other, wherein the common tangent Tan with a radial plane of the punch rivet forms an angle α, wherein the first radius R 1 tangentially in the shaft outer surface ( 14 ) or is replaced by a chamfer of corresponding length, and the second radius R 2 tangentially into the shaft inner surface ( 16 ), and wherein the following value ranges apply to the first radius R 1 , the second radius R 2 and the angle α: R 1 = 0.3 ± 0.2 mm R 2 = (0.7 to 1.2) (i.e. N - d i ) / 2 α = 10 ° ± 20 °.
Punch rivet with a rivet head ( 4 ) and a rivet ( 6 ) with a central shaft bore ( 8th ), which have a common central axis X, wherein the rivet head ( 4 ) a substantially cylindrical head outer surface ( 12 ) of a given head diameter d K , the rivet shank ( 6 ) a substantially cylindrical shaft outer surface ( 14 ) of a predetermined outer shaft diameter d N and a central shaft bore ( 8th ) limiting, substantially cylindrical inner shaft surface ( 16 ) of a predetermined internal shaft diameter d i , the head outer surface ( 12 ) and the shaft outer surface ( 14 ) by a conical or slightly curved Unterkopffase ( 18 ; 18 ' ) and a sub-head radius R 4 which tangentially into both the Unterkopffase ( 18 ; 18 ' ) as well as in the Schaftaußenflä che ( 14 ), and the shaft outer surface ( 14 ) and the inner surface of the shaft ( 16 ) are connected at the Nietfußende via a radially outer first radius R 1 and a radially inner second radius R 2 , which merge tangentially into each other, wherein the common tangent Tan with a radial plane of the punch rivet forms an angle α, wherein the first radius R 1 tangentially in the shaft outer surface ( 14 ) or is replaced by a chamfer of appropriate length, and the second radius R 2 with the shank inner surface ( 16 ) is connected by a third radius R 3 , the tangential both in the second radius R 2 as in the inner shaft surface ( 16 ), and wherein the following value ranges apply to the first radius R 1 , the second radius R 2 , the third radius R 3 and the angle α: R 1 = 0.3 ± 0.2 mm R 2 = (0.7 to 1.2) (i.e. N - d i ) / 2 R 3 = 0.8 ± 0.4 mm α = 5 ° ± 10 °.
Punch rivet according to claim 1 or 2, characterized in that for the second radius R 2 : R 2 = (0.8 to 1.0) (i.e. N - d i ) / 2
Punch rivet according to one of claims 1 to 3, characterized in that the conical lower head bevel ( 18 ) encloses an angle β = 25 ° ± 10 °, in particular 25 ° ± 7 ° with a radial plane of the punch rivet.
Punch rivet according to one of claims 1 to 3, characterized in that the slightly curved Unterkopffase ( 18 ' ) has a radius R 7 ≥ 2.0 mm.
Punch rivet according to one of the preceding claims, characterized in that the following applies for the under-head radius R 4 : R 4 = 0.6 ± 0.4 mm, esp. R 4 = 0.5 ± 0.2 mm.
Punch rivet according to one of the preceding claims, characterized in that for the shank inner diameter d i : d i = (0.5 to 0.8) d N ,
Punch rivet according to one of the preceding claims, characterized in that for the head diameter d K of the rivet head ( 4 ) applies: d K = (1.3 to 1.8) d N , esp. d K = (1.4 to 1.65) d N ,
Punch rivet according to one of the preceding claims, characterized in that for the axial length H K of the head outer surface ( 12 ) applies: H K = (0.025 to 0.2) d N , especially H K = (0.025 to 0.12) d N ,
Punch rivet according to one of the preceding claims, wherein the rivet head end of the shaft bore ( 8th ) is closed, characterized in that the closed end of the shaft bore ( 8th ) a conical bottom surface ( 24 ) has an outer shaft bore radius R 5 in the inner shaft surface ( 16 ) and ends in the region of the central axis X in an inner shaft bore radius R 6 .
Punch rivet according to claim 8, characterized in that the cone angle γ of the conical bottom surface ( 24 ) Is 110 ° to 140 °, in particular 110 ° to 130 °.
Punch rivet according to claim 8 or 9, characterized in that the following applies to the outer shank bore radius R 5 : R 5 = 0.7 ± 0.5 mm, esp. R 5 = 0.8 ± 0.3 mm.
Punch rivet according to one of claims 10 to 12, characterized in that for the inner shaft bore radius R 6 : R 6 = 0.9 ± 0.5 mm, esp. R 6 = 0.8 ± 0.3 mm.
Punch rivet according to one of claims 10 to 13, characterized in that for the depth t B of the shaft bore ( 8th ) from the bottom of the rivet to the point at which imaginary extensions of the conical bottom surface ( 24 ) and the inner surface of the shaft ( 16 ), the following applies: t B ≥ 0.2 d N , in particular t B ≥ 0.3 d N
Punch rivet according to one of claims 10 to 14, characterized in that for the thickness D K of the rivet head ( 4 ) on the central axis X: D K ≥ 0.15 d N
Punch rivet according to one of claims 1 to 9, characterized the shaft bore is open at the rivet head end.
Punch rivet according to one of the preceding claims, characterized in that it is used as a functional element, in particular as a punching bolt or Punch nut, is formed.
Punch rivet according to one of the preceding claims, characterized in that the rivet shank ( 6 ; 6 ' ) a substantially cylindrical shaft outer surface 14 or one with an axial corrugation ( 42 ) has provided shaft outer surface.
Die for producing a punched-rivet connection by means of a punch rivet, in particular according to one of the preceding claims, with a die cavity ( 34 ) coming from a die base ( 36 ) and a cylindrical peripheral surface ( 38 ) is limited, characterized in that for the diameter D M and the depth T M of the Matrizenhohlraumes ( 34 ) applies: D M = [d N + (0.6 to 1.5)] t M , esp. [d N + (0.7 to 1.2)] t M T M = (1.0 to 2.5) t M , especially T M = (1.1 to 2.2) t M , for joining parts made of materials with good deformability, in particular for wrought alloys, where d N is the shank outer diameter of the rivet shank ( 6 ) of the punch rivet ( 2 ) and t M is the thickness of the die-side joining part ( 26 ) is and: D M ≤ 2.2 d N T M ≤ 0.15 D M for joining parts made of cast materials and other materials of low forming ability.
Die for producing a punched-rivet connection by means of a punch rivet, in particular according to one of the preceding claims, with a die cavity ( 34 ) coming from a die base ( 36 ) and a cylindrical peripheral surface ( 38 ), characterized in that the die ( 30 ' ) at the matrix bottom a central recess ( 40 ), which provides pressure relief during the joining process.
Die according to claim 20, characterized in that the central recess ( 40 ) has a diameter of D EB ≤ 0.5 D M and a depth T EB ≥ 0.2 d N , esp. T EB ≥ 0.3 d N.
DE200610028537 2006-06-21 2006-06-21 Self-punching rivet has head outer face and shank outer face connected by conical or slightly curved chamfer below head and radius below head which merges tangentially both into chamfer and also into shank outer face Expired - Fee Related DE102006028537B3 (en)
DE200610028537 DE102006028537B3 (en) 2006-06-21 2006-06-21 Self-punching rivet has head outer face and shank outer face connected by conical or slightly curved chamfer below head and radius below head which merges tangentially both into chamfer and also into shank outer face
DE200620013981 DE202006013981U1 (en) 2006-06-21 2006-06-21 Punch rivet has hollow shaft whose outer surface and inner surface are connected by radial outer radius and radial inner radius which connect tangentially at angle to radial plane
ES07785829T ES2335247T3 (en) 2006-06-21 2007-06-19 Autoperforant beach and matrix.
JP2009515756A JP5660560B2 (en) 2006-06-21 2007-06-19 Punching rivet, die and method
CN201210446097.XA CN103008523B (en) 2006-06-21 2007-06-19 Punch die
US12/305,821 US8506228B2 (en) 2006-06-21 2007-06-19 Punch rivet and die
RU2009101815/02A RU2448285C2 (en) 2006-06-21 2007-06-19 Push-down rivet (versions) and matrix for push-down riveted connection (versions), and method for obtaining push-down riveted connection (versions)
PCT/EP2007/005376 WO2007147551A1 (en) 2006-06-21 2007-06-19 Punch rivet and die
CN 200780023105 CN101472690B (en) 2006-06-21 2007-06-19 Punch rivet and die
DE200750001811 DE502007001811D1 (en) 2006-06-21 2007-06-19 Stanzniet and matrize
AT07785829T AT446151T (en) 2006-06-21 2007-06-19 Stanzniet and matrize
BRPI0713581-5A BRPI0713581A2 (en) 2006-06-21 2007-06-19 puncture and die rivet
EP20070785829 EP2032282B1 (en) 2006-06-21 2007-06-19 Punch rivet and die
KR1020097001224A KR101474477B1 (en) 2006-06-21 2007-06-19 Punch rivet and die
US13/935,256 US9091290B2 (en) 2006-06-21 2013-07-03 Punch rivet and die
DE102006028537B3 true DE102006028537B3 (en) 2007-05-10
ID=37950189
DE200610028537 Expired - Fee Related DE102006028537B3 (en) 2006-06-21 2006-06-21 Self-punching rivet has head outer face and shank outer face connected by conical or slightly curved chamfer below head and radius below head which merges tangentially both into chamfer and also into shank outer face
DE200750001811 Active DE502007001811D1 (en) 2006-06-21 2007-06-19 Stanzniet and matrize
US (2) US8506228B2 (en)
EP (1) EP2032282B1 (en)
JP (1) JP5660560B2 (en)
KR (1) KR101474477B1 (en)
CN (2) CN103008523B (en)
AT (1) AT446151T (en)
BR (1) BRPI0713581A2 (en)
DE (2) DE102006028537B3 (en)
ES (1) ES2335247T3 (en)
RU (1) RU2448285C2 (en)
WO (1) WO2007147551A1 (en)
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2007-06-19 EP EP20070785829 patent/EP2032282B1/en active Active
2007-06-19 AT AT07785829T patent/AT446151T/en unknown
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2007-06-19 BR BRPI0713581-5A patent/BRPI0713581A2/en active Search and Examination
2007-06-19 RU RU2009101815/02A patent/RU2448285C2/en active
2007-06-19 JP JP2009515756A patent/JP5660560B2/en active Active
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2007-06-19 CN CN201210446097.XA patent/CN103008523B/en active IP Right Grant
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