Lightweight fastener with specially shaped head

Abstract

The invention relates to a fastener (1) comprising a head (10). The novelty of the invention lies in, the fastener is configured in order to be assembled using standard hexagonal driving tools (40) and to have reduced weight; wherein the fastener comprises at least two contact regions (11), each having at least one of a loosening contact surface (112) and a tightening contact surface (111) that enable the driving tool (40) to transmit torque, wherein a first curvature (12), a second curvature (13), a third curvature (14), and a fourth curvature (15) are provided respectively between the contact regions (11), wherein the first curvature (12) and the second curvature (13) have the same radius, and the third curvature (14) and the fourth curvature (15) have the same radius.

Description

[0001] SPECIFICATION

[0002] LIGHTWEIGHT FASTENER WITH SPECIALLY SHAPED HEAD

[0003] FIELD OF THE INVENTION

[0004] The invention relates to a lightweight fastener, which can be assembled using standard driving tools.

[0005] BACKGROUND OF THE INVENTION

[0006] Fasteners are mechanical components used to hold different parts together. They are widely used in many industrial fields, particularly in the automotive and construction sectors.

[0007] In order to apply tightening during the assembly of the parts, an axial rotation process is performed by applying torque to the external or internal driving surfaces of the head of the fastener, using a suitable wrench, socket, or special driving tool. The space caused by the tolerances between the contact surfaces of the tightening tools used for external and internal drive forms results in torque transmission occurring through smaller contact areas compared to the main contact area during the axial rotation in tightening and loosening processes.

[0008] The non-contacting regions on the surfaces do not serve any other functionality and remain idle under tightening and loosening conditions. The material located in these regions causes the fastener to be unnecessarily heavy, resulting in additional weight increase in the area of use due to the fastener. In weight reduction efforts for fasteners, new designs are generally developed by removing non-functional portions, and material is removed from the head form of the fastener in areas that remain idle. This situation imposes design constraints and limits the weight reduction ratio to approximately 25%.

[0009] In weight reduction studies, it is also possible for the head to be damaged in such a way that it loses its original geometry due to deformation caused by the torque applied through the tightening tool, resulting in the loss of rigidity and integrity of the head. Additionally, although the rate of weight reduction achieved through special head designs tailored for use with special driving tools may increase, the fact that tightening and loosening operations can only be performed with said special driving tool causes longer procurement processes and additional costs. In other words, in lightweight fasteners that can be driven with standard tightening tools, the reduction in weight is limited, and fasteners designed for special driving tools lead to different issues.

[0010] PCT application of WO8302983 discloses head forms for fasteners based on the principle that the outwardly-curved regions, where the tightening and loosening surfaces meet each other, located on a circle concentric with the axis of the fastener. In the forms disclosed in the invention, it is proposed that the internal angle between two adjacent torque application surfaces is alternately smaller and larger than 180°, such that the connection points between them are alternately located on an outer and an inner tangential circle. These fasteners require the use of special drivers having the same geometry as the head form.

[0011] In assembly conditions of fasteners, axial rotational forces resulting from the torque applied for tightening and loosening may cause a stripping problem due to insufficient driving contact surfaces, leading to localized plastic deformation in the regions contacted by the driving tool. When the stripping problem occurs, the axial rotational force required to tighten or loosen the fastener cannot be transmitted by the driving tool to the fastener, and the desired clamping load cannot be achieved. Consequently, the assembly operation cannot be properly completed.

[0012] To avoid the stripping problem known in the state of the art, customized driving tools for the fastener, which has a form matching the head of fastener and provide a higher ratio of driving contact area, or alternatively, the head height is increased to provide sufficient driving contact area. However, this leads to additional material usage.

[0013] In studies aimed at weight reduction, it is generally achieved by forming inward recesses in the center of the head form in known shapes such as cylindrical or spherical, or by creating inward cavities with a certain wall thickness preserved at the outer edges of the head form. Although weight reduction is achieved by designing internal driving sections in the head for the tightening and loosening of the fastener, the level of weight reduction achieved remains limited due to the size and tolerance ranges of the tools to be used.

[0014] As a result, all the abovementioned problems have made it necessary to make an improvement in the relevant technical field.

[0015] SUMMARY OF THE INVENTION The present invention relates to a lightweight fastener, developed to eliminate the disadvantages mentioned above and to introduce new advantages to the relevant technical field.

[0016] An object of the invention is to provide a fastener that enables connections in which the desired torque and / or clamping load can be achieved during assembly without encountering the stripping problem, thus allowing for effective fastening.

[0017] Another object of the invention is to provide a fastener that can be used with conventional wrenches having a standard hexagonal head portion, without requiring a special driving tool for tightening and loosening operations under assembly conditions.

[0018] Another object of the invention is to provide a fastener having a specially designed head form that differs from conventional fasteners and serves the use of lightweight and high- strength components, which is one of today’s industrial trends.

[0019] Another objective of the invention is to provide a solution to the stripping problem, which occurs when the wrench contact areas affected by the axial rotational force generated by the application of tightening and loosening torque are insufficient, leading to negative effects in terms of assembly performance. A fastener is provided that ensures sufficient wrench contact areas through fewer contact points compared to conventional fasteners with a hexagonal head portion, without causing the stripping problem.

[0020] Another objective of the invention is to provide a lightweight fastener as a result of a significant reduction in the material of the head form, achieved by connecting the contact regions with concave curvatures.

[0021] Another object of the invention is to prevent damage to the head form in a way that would cause the loss of the driving geometry, which may occur due to deformation resulting from material reduction in the head form during tightening and loosening operations. Thus, by preserving the rigidity of the head form, the recess formed at the center of the head is carried out with reference to the characteristic main boundaries of the head form, unlike conventional recess shapes. Accordingly, a fastener is provided having a head form comprising a quadrangle cavity, achieving significantly higher weight reduction.

[0022] Another object of the invention is to provide a fastener that is suitable for forming production methods applied within the scope of cold forging processes. The present invention relates to a fastener comprising a head in order to achieve all the objectives mentioned above and those that will emerge from the detailed description below. The novelty of the invention lies in, the fastener is configured in order to be assembled using standard hexagonal driving tools and to have reduced weight; wherein the fastener comprises at least two contact regions, each having at least one of a loosening contact surface and a tightening contact surface that enable the driving tool to transmit torque, wherein a first curvature, a second curvature, a third curvature, and a fourth curvature are provided respectively between the contact regions, wherein the first curvature and the second curvature have the same radius, and the third curvature and the fourth curvature have the same radius. Thus, while maintaining the strength of the fastener and preserving the head form in a manner that does not require special driving tools, the weight can be significantly reduced and the cost can be lowered.

[0023] A possible embodiment of the invention is that the number of contact regions is four. Thus, optimal contact for torque transmission is provided and the weight of the fastener is reduced without compromising strength.

[0024] A possible embodiment of the invention is that each contact region comprises a loosening contact surface and a tightening contact surface, enabling torque transmission.

[0025] A possible embodiment of the invention is that the radius value of the first curvature and the second curvature is greater than the radius value of the third curvature and the fourth curvature.

[0026] A possible embodiment of the invention is that it comprises at least one recess formed by removing material from a region remaining between the first curvature, the second curvature, the third curvature, and the fourth curvature, and the driving tool, after the driving tool is engaged onto the head. Thus, unnecessary material is removed, thereby reducing the weight of the fastener.

[0027] A possible embodiment of the invention is that it comprises at least one cavity in a region between the contact regions. Thus, the weight can be further reduced without decreasing the strength of the head.

[0028] A possible embodiment of the invention is that at least one of the first curvature, the second curvature, the third curvature, and the fourth curvature is a concave arc. Thus, a recess can be formed without changing strength and the weight is reduced. Furthermore, since the amount of material used is decreased, the costs are also reduced.

[0029] A possible embodiment of the invention is that it comprises at least one flange. Thus, slipping and loosening during assembly are prevented, thereby improving the integrity of the connection.

[0030] A possible embodiment of the invention is that the flange comprises, respectively between the contact regions connected by the first curvature and the second curvature, a linear transition surface, a curved transition surface, and a second linear transition surface, and between the contact regions connected by the third curvature and the fourth curvature, a linear transition surface. Thus, while maintaining strength, material can be removed from the flange so that the weight can be reduced.

[0031] A possible embodiment of the invention is that the fastener is a bolt and comprises a shaft, and the shaft preferably has helical threads extending along its outer surface. Thus, assembly with female fasteners can be performed.

[0032] A possible embodiment of the invention is that the cavity is in a quadrangle form. Thus, a symmetrical form is obtained, and as a result, manufacturing by cold forming is facilitated, and additionally, the weight can be significantly reduced without loss of strength.

[0033] A possible embodiment of the invention is that the fastener is a nut and the cavity is a hole having a circular cross-section, and the hole preferably has helical threads extending along its inner surface. Thus, assembly with male fasteners can be performed.

[0034] BRIEF DESCRIPTION OF THE FIGURES

[0035] Figures 1-2 show isometric views of the fastener of the invention from various perspectives.

[0036] Figures 3-6 show isometric views of the flanged version of the fastener of the invention from various perspectives.

[0037] Figure 7 shows a top view of the flanged version of the fastener of the invention. Figure 8 shows a side view and a side sectional view of the flanged version of the fastener of the invention.

[0038] Figure 9 shows an isometric view of the fastener of the invention and a standard hexagonal driving tool.

[0039] Figure 10 shows a side view of the driving tool engaged with the head portion of the fastener of the invention.

[0040] Figure 11 shows a top sectional view of the fastener of the invention engaged with the driving tool, where the torque applied in the tightening direction is transmitted via the tightening contact surfaces.

[0041] Figure 12 shows a top sectional view of the fastener of the invention engaged with the driving tool, where the torque applied in the loosening direction is transmitted via the loosening contact surfaces.

[0042] Figures 13 and 14 show isometric views of the fastener of the invention configured as a nut.

[0043] Figures 15 and 16 show views of the fastener of the invention configured as a flanged nut.

[0044] Figure 17 shows a top view of the fastener of the invention in its flanged nut configuration.

[0045] Figures 18-19 show isometric views of an alternative flanged configuration of the fastener of the invention.

[0046] Figure 20 shows a top view of the alternative flanged configuration of the fastener of the invention.

[0047] DETAILED DESCRIPTION OF THE INVENTION

[0048] In this detailed description, the fastener (1 ) subject to the invention is explained solely by way of examples that do not have any limiting effect and are intended only to facilitate understanding of the subject. Figures 1 to 6 show representative isometric views of the fastener (1 ) of the invention. The present invention relates to a new-generation fastener (1) with a specially designed head (10), developed as an alternative to lightweight and high-strength fasteners (1), which is one of the industrial trends, and which overcomes the disadvantages described in the known state of the art. The fastener (1) may be either a male or a female type comprising said head (10).

[0049] The fastener (1 ) comprises at least one cavity (17) on the head (10). The cavity (17) has a quadrangle shape located between the contact regions (11 ). The top and bottom corners of the quadrangle-shaped cavity, namely the intersection points of its top and bottom edges, are positioned on the central axis (M), as seen in Figure 7. In the preferred embodiment, only one pair of opposing sides of the cavity (17) are equal to each other. However, in an alternative embodiment, it may be a rhombus shape where all opposing sides are equal. In this case, as seen in Figure 7, the cavity (17) is symmetrical with respect to the central axis (M) passing through the center of the head (10). Essentially, the cavity (17) is a groove portion with a certain depth on the head (10). The cavity (17) provides a significant weight reduction compared to the head forms of conventional hexagonal fasteners. The corners of the cavity (17) may include radiused transitions.

[0050] In the case where the fastener is a male fastener, preferably a bolt, the cavity (17) is a groove with a quadrangle shape on the head and a certain depth extending toward the flange (20), as previously defined. This configuration is shown in the sectional view provided in Figure 8. In this case, the fastener (1) also comprises at least one shaft (30). The shaft (30) has a helical thread extending along its outer surface.

[0051] In the case where the fastener (1) is a female fastener, preferably a nut, the cavity (17) is a hole extending through the center of the fastener (1). In other words, as shown in Figures 13 and 14, it is a through hole with a circular cross-section open at both ends. The wall thickness of the hole is determined so as not to compromise mechanical performance. Additionally, the hole is preferably internally threaded to allow connection with male fasteners such as bolts.

[0052] As can be seen in Figures 3 and 18, the fastener (1) may further comprise at least one flange (20). The flange (20) is located below the head (10), and its circumference has a larger diameter than the head (10), similar to conventional hexagonal flanged fasteners (1 ). Additionally, with regard to the flange (20), the flange angle in the region on the head (10) is between 3° and 10°. Preferably, the flange angle is between 5° and 7°. Moreover, the flange angle in the region of the flange (20) and the head (10) is lower than the flange angles found in conventional hexagonal flanged fasteners (1). In this way, an optimal flange (20) angle is achieved to allow easier adjustment of the head (10) height for ease of production in the cold forming process.

[0053] The head (10) comprises at least two contact regions (11) which allow a driving tool (40) to apply torque to the fastener (1). In the preferred embodiment, the number of contact regions (11 ) is four. The contact regions (11 ) are formed so as not to be deformed under the axial rotational force. The driving tool (40) applies torque to the head (10) through the contact regions (11), thereby rotating the fastener (1 ) in a tightening direction (I) or in a loosening direction (II). The driving tool (40) may be a standard wrench.

[0054] The contact regions (11) comprise at least one tightening contact surface (111) that is in contact with the surfaces of the driving tool (40), i.e., a standard hexagonal tightening tool, and that enables the axial rotational force generated by the torque applied in the tightening direction (I) by means of the driving tool (40) to be transmitted to the fastener (1). In the preferred embodiment, a tightening contact surface (111) is located in each contact region (11 ), resulting in four tightening contact surfaces (111 ) in total.

[0055] The dimensional measurements of the tightening contact surfaces (111) are determined according to meet the strength values of the grade 12.9 with the highest strength of the fastener defined in the main fastener standard “ISO 898-1 - Mechanical properties of fasteners made of carbon steel and alloy steel — Part 1 : Bolts, screws and studs with specified property classes — Coarse thread and fine pitch thread” and the sufficient contact areas providing the minimum breaking torques given in “ISO 898-7 - Mechanical properties of fasteners — Part 7: Torsional test and minimum torques for bolts and screws with nominal diameters 1 mm to 10 mm”.

[0056] In order to achieve the clamping load, which is one of the most important parameters affecting the performance of fasteners (1) under assembly conditions, the magnitude of the axial rotational force generated at the contact regions (11) by applying torque during the tightening process is crucial. The contact regions (11 ) on the head (10) are optimized to provide resistance against stripping in the contact regions (11 ) even when axial rotational forces generated at the highest torque values, which may cause the fastener (1) to lose functionality, are applied during tightening. In the contact region (11 ), there is at least one loosening contact surface (112) that is in contact with the surfaces of the standard hexagonal tightening tool and that enables the axial rotational force generated by the torque applied in the loosening direction (II) to be transmitted to the fastener (1 ). The loosening contact surface (112) is also present in each contact region (11), totaling four.

[0057] The fastener (1) comprises at least one recess (16) on the head (10). The recess (16), when viewed in the top sectional views as in Figures 11 and 12, corresponds to regions of the head (10) in which material is reduced in areas that are not in contact with the wrench, without affecting the assembly performance of the fastener (1). These recesses (16) are gaps between two contact regions (11 ), bounded by concave arcs and the driving tool.

[0058] The height of the recesses (16) are equal to the wrench grip height of the fastener (1 ) in the present invention. In other words, they are at the same height as the tightening and loosening contact surfaces (112). As shown in Figures 11 and 12, the recess (16) is formed between the head (10) and the driving tool (40) after the driving tool (40) is engaged onto the head (10). To clarify, the recess (16) is created by removing material in such a way that it does not compromise the rigidity and strength of the head (10) of the fastener (1), thereby enabling a reduction in the weight of the head (10).

[0059] As a result of the recesses (16) created, the head (10) comprises a first curvature (12), a second curvature (13), a third curvature (14), and a fourth curvature (15). That is, the four contact regions (11 ) are respectively connected by the first curvature (12), second curvature (13), third curvature (14), and fourth curvature (15). Therefore, the aforementioned curvatures (referring to the first curvature (12), second curvature (13), third curvature (14), and fourth curvature (15)) are located between two contact regions (11). These curvatures are in the form of concave arcs and have a radius value. Since there are four curvatures, there are also four recesses (16). The concavity of the curvature means that it curves inward toward the center of the head (10).

[0060] As a result, the contact regions (11) are not connected by a straight line as in the prior art but are connected by curvatures. In order to reduce material usage in the head (10), material is removed from the head (10) to form said curvatures, thereby creating the recesses (16) described above. In other words, the recesses (16) are material-free areas between the concave curved surface extending between these contact regions (11 ) and the boundary lines obtained by imaginatively extending, in a straight line, the directions of the tightening and loosening contact surfaces (112) of two adjacent contact regions, i.e., the boundary lines of the imaginary hexagon corresponding to the standard hexagonal head form taken as a reference for the head (10).

[0061] The radius of the first curvature (12) and the second curvature (13) are equal. Similarly, the radius of the third curvature (14) and the fourth curvature (15) are also equal. As a result, a symmetrical structure is obtained with respect to the central axis (M) passing through the center of the fastener (1), as seen in Figure 7. Therefore, there is an equal number of tightening contact surfaces (111 ) and loosening contact surfaces (112). As a result, a more uniform torque distribution is achieved, and consistency is ensured in the results obtained with different metrics of the fastener (1). The central axis (M) is the axis passing through the intersection points of the tightening contact surface (111) and the loosening contact surface (112) located in two opposing contact regions (11).

[0062] Considering the outline of the recess shape, transitions are made with concave arcs to avoid sharp edges. In addition, the material amount between the recesses (16) and the cavity (17), which defines the inner and outer boundaries of the head (10) geometry, is optimized to prevent the stripping problem during tightening and loosening operations. The depth of the recess (16) and the cavity (17) is determined according to the desired metric of the fastener (1) to achieve the highest possible material savings from the weight of the head (10).

[0063] The dimensions of the head (10) can be revised according to the preferred wrench width for different metrics. To increase the usability of the fastener (1 ), each geometric feature and dimension of the head (10) has been proportioned according to a specific coefficient based on the wrench width. The flange (20) diameter of the fastener (1 ) is determined according to the desired area of the bearing surface beneath the head (10). Thus, by reducing the risk of loosening of the fastener (1 ), the reliability of the connection is increased.

[0064] The characteristic form of the head (10) of the fastener (1 ) is determined to be compatible with the forming techniques applied in the cold forging process, which is the main manufacturing method of fasteners (1). Thus, lightweight fasteners (1) can be quickly and easily produced in large volumes where needed.

[0065] In an alternative embodiment of the invention shown in Figures 18 to 20, the flange (20) comprises, between the contact regions (11 ) connected by the first curvature (12) and the second curvature (13), respectively, a linear transition surface, a curved transition surface following it, and a second linear transition surface. Between the contact regions (11) connected by the third curvature (14) and the fourth curvature (15), the flange (20) comprises only a linear transition surface.

[0066] In this embodiment, the peripheral contour of the flange (20), as seen particularly in Figure 20, is connected to the contact regions (11 ) such that it is tangential to the tightening contact surfaces (111 ) and loosening contact surfaces (112) in the respective contact regions (11 ). In this way, unnecessary material is removed around the flange (20), and further weight reduction is achieved. In other words, the outer diameter of the flange (20) can essentially be determined to be equal to the diameter of the imaginary circle that defines the outer boundary of the head (10) and passes through the outermost points of the tightening and loosening contact surfaces (112) in the contact regions (11).

[0067] In light of all the above explanations, the invention operates as follows: the fastener (1 ) is engaged by a standard hexagonal driving tool (40) through the contact regions (11 ) located on the head (10) (see Figures 9 and 10) and can be rotated for assembly and disassembly via the equal number of tightening contact surfaces (111 ) and loosening contact surfaces (112) in these contact regions (11). Additionally, in the regions connecting the contact regions (11) without compromising strength, the head (10) comprises four recesses (16), which respectively form the first curvature (12), second curvature (13), third curvature (14), and fourth curvature (15). Due to the recesses (16), material is reduced, and the weight is decreased.

[0068] Finally, in the case where the fastener (1) is a bolt, the cavity (17) (essentially another recess), in a quadrangular form, symmetrical with respect to the central axis (M) passing through the center of the head (10), allows material reduction while maintaining rigidity and strength. During assembly, the driving tool (40) can be rotated in the tightening direction (I) to tighten by applying force to the tightening contact surfaces (111) as shown in Figure 11 , and can be rotated in the loosening direction (II) to loosen by applying force to the loosening contact surfaces (112) as shown in Figure 12.

[0069] In the case where the fastener (1 ) is a nut, the cavity (17) becomes a hole that allows connection with a male fastener. This configuration can be seen in Figures 13-14 in its non-flanged version and in Figures 15-17 in its flanged version.

[0070] Accordingly, the fastener (1 ), with its cavity (17), recesses (16), and four contact regions (11 ) on the head (10), allows sufficient torque transmission and mechanical strength to be maintained while using less material in the head region compared to conventional hexagonal fasteners. Thanks to the four tightening and four loosening contact surfaces (112) located on the four contact regions (11), the torque applied during tightening and loosening is distributed more evenly, and the risk of stripping and local deformation on the head (10), particularly during repeated assembly-disassembly for maintenance purposes, is reduced. In this way, unnecessary material used in the head (10) is eliminated, significantly reducing the overall weight of the fastener (1) and contributing to cost reduction through less raw material consumption.

[0071] Furthermore, performing the tightening and loosening operations through the same number of contact regions (11 ) and designing the head (10) to be balanced about the driving axis facilitates consistently achieving the desired mechanical performance for each metric size when scaling the fastener (1) to different metric dimensions, and helps ensure more uniform stress distributions in the die during cold forming production.

[0072] As a result, a fastener (1) that can be assembled using standard hexagonal driving tools and whose weight is significantly reduced without compromising strength has been provided.

[0073] The scope of protection of the invention is defined in the claims provided in the annex and shall by no means be limited to the embodiments described in this detailed description for illustrative purposes. It is evident that a person skilled in the art may develop similar configurations in light of the above explanations without departing from the main concept of the invention.

[0074] REFERENCE NUMBERS THAT GIVEN IN THE FIGURE

[0075] 1 Fastener

[0076] 10 Head

[0077] 11 Contact Region

[0078] 111 Tightening Contact Surface

[0079] 112 Loosening Contact Surface

[0080] 12 First Curvature

[0081] 13 Second Curvature

[0082] 14 Third Curvature

[0083] 15 Fourth Curvature

[0084] 16 Recess

[0085] 17 Cavity

[0086] 20 Flange

[0087] 30 Shaft

[0088] 40 Driving Tool

[0089] (I) Tightening Direction

[0090] (II) Loosening Direction

[0091] (M) Central Axis

Claims

CLAIMS1. A fastener (1 ) comprising a head (10), characterized in that the fastener is configured in order to be assembled using standard hexagonal driving tools (40) and to have reduced weight; wherein the fastener comprises at least two contact regions (11), each having at least one of a loosening contact surface (112) and a tightening contact surface (111 ) that enable the driving tool (40) to transmit torque, wherein a first curvature (12), a second curvature (13), a third curvature (14), and a fourth curvature (15) are provided respectively between the contact regions (11), wherein the first curvature (12) and the second curvature (13) have the same radius, and the third curvature (14) and the fourth curvature (15) have the same radius.

2. The fastener (1) according to claim 1 , characterized in that the number of contact regions (11) is four.

3. The fastener (1 ) according to claim 1 , characterized in that each contact region(I I ) comprises a loosening contact surface (112) and a tightening contact surface(I I I ), enabling torque transmission.

4. The fastener (1 ) according to claim 1 , characterized in that the radius of the first curvature (12) and the second curvature (13) is greater than the radius of the third curvature (14) and the fourth curvature (15).

5. The fastener (1) according to claim 1 , characterized in that it comprises at least one cavity (17) in a region between the contact regions (11).

6. The fastener (1 ) according to claim 1 , characterized in that at least one of the first curvature (12), the second curvature (13), the third curvature (14), and the fourth curvature (15) is a concave arc.

7. The fastener (1) according to claim 1 , characterized in that it comprises at least one recess (16) formed by removing material from a region between the first curvature (12), the second curvature (13), the third curvature (14) and the fourth curvature (15) and the driving tool (40), after the driving tool (40) is engaged onto the head (10).

8. The fastener (1) according to claim 1 , characterized in that it comprises at least one flange (20).

9. The fastener (1 ) according to claim 1 , characterized in that the fastener (1) is a bolt and comprises a shaft (30).

10. The fastener (1) according to claim 5, characterized in that the cavity (17) is in a quadrangle form.

11. The fastener (1) according to claim 1 , characterized in that the fastener (1) is a nut and the cavity (17) is a hole having a circular cross-section.

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