DE1625467A1 - Industrial items, especially screws, nuts and the like. as well as tools for driving the same and tools for making these articles - Google Patents

Description

Patent attorneys Dipl.-Ing. E Weickmann, Dr.

Dipl.-Ing. H.Weickmann, Dipl.-Phys. Dr. K. Fincke Dipl.-Ing. F. A-Weickmann

8 MUNICH 27, DEN ^ g 2 5467

MÖHLSTRASSE 22, CALL NUMBER 483921/22

SABM.

! BEXiDROl "Industries, Inc., 600 Eighteenth Avenue, Illinois, Y.St.v, A.

Industrial articles, in particular screws, nuts and the like, as well as tools for driving the same - and tools to manufacture these items

The invention relates to slewing rings and tools for making - such connections.

A hexagonal configuration, as it is commonly used for transferring The torque used by a driving element on a driven element consists of six flat surfaces, which are arranged symmetrically about a central axis are. Because of the wide drive angle and the point contact between the adjacent, im Engaging surfaces, the torque with poor efficiency from the driving element to the

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transferred element driven. The opposite, ■ surfaces of the driving'Elementes incline depending on the usually provided in between tolerance to spread apart in a wedge shape, while at the same time the Zones of highest stress, such as sharp corners of the driven one Element, to be overstrained »To the danger a break or other cancellation of the driving or of the driven element, these parts become common widened to bring the wing-loading to a value within the strength limits of the metal from which the connecting parts exist to reduce. Through this however, the connecting parts are heavy and this is a hindrance especially in those cases where the lowest possible Weight is sought; it also makes the ropes expensive, especially when expensive alloys are used.

It has already been suggested on the scope of the powered Seiles distributes several right-angled keyways to be provided and on the driving part complementary clariu trained wedges or vice versa. However, such are Surfaces are expensive to produce and often require post-processing; in addition, many zones are formed on them, extreme stress, so that such splined connections can only be used in very limited cases are. ■

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ORIGINAL INSPECTED

It has also been suggested the driven part a surface configuration pit 12 smaller attack surfaces, either flat or curved and either inside or outside, to give * which are evenly distributed over 560 ° and one Form a series of alternating, practically equally wide ridges and grooves, such rotary connections are sufficient but for the transmission of torque a, as it is today Requirements correspond to, not from. Trying to Applying larger torques either breaks the driving force ieil or the relatively narrow ribs of the driven rope are sheared off. With the latter Failure usually involves slipping of the driving element accompanied by the driven element.

Cruciform depressions and complementary driving parts have also already been proposed * the several, proportionately have narrow wings extending radially from the central axis stand outwards. Such slewing rings have numerous parts. One of them is that most of them gin have a very strong tendency to slide, and therefore one require strong pressure on the front side, something for the Can be very tiring for the user. But it is more important than that the manufacturing problem, / because a sufficient accuracy for the countersink irr the driven element and for the engaging part of the driving element required borrowed. is. The lifespan of the stamp for impact

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sinking into the driven element with the necessary Accuracy is relatively short, so the total cost for the stamp are high. As for the engaging part of the driving As far as the element is concerned, this requires Gewönnlcjfi. several pre-work processes, to which sometimes there are also embossing and sharpening work processes come, which all together cause relatively high costs for the driving element.

The present invention overcomes these and other disadvantages in that they have a new and advanced hexagonal surface configuration between complementary, intermeshed.driving and provides driven parts, which is large from the driving part to the driven part Torques can be transmitted. Indeed, with a substantial reduction in size and material requirements transmit large torsional forces for the coupling parts. These high torsional forces can also be transferred from one to the other other element m ± t transferred to such a force distribution that there is hardly any risk of damage to the coupling parts consists. Also not to be fished that the connection loosens,., the driving or the driven element grinds itself off or fails in some other way.

In accordance with the invention there is provided a new and improved six-acre Surface configuration created that

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The fact is that it takes the place of numerous - previously used- • Licher forms of surface configurations can occur and universal, usable. The configuration according to the invention 'isn't just for the exposed heads of powered Elements but also for the driving depressions des lyps with a connecting surface inside. The invention is for diverse products applicable, for example for fasteners and the Corresponding driving elements, further for fittings, for torsional forces transmitting couplings and connections in general and for the tools required for this, such as keys, upper punches, lower punches and the like.

The configuration consists essentially of a first Group of spaced, semi-cylindrical faces that are hexagonal are arranged, the axes of curvature of the surfaces coinciding with the tips of the regular 'hexagon. In addition, there is a second group of semi-cylindrical surfaces, which are opposite to the first-mentioned surfaces are curved and alternate with these, the surfaces of the second Group at their edges tangential to the faces of the first Skip group. The axes of curvature of the first group lie between the associated surface and the central axis of the body, whereas the axes of curvature of the second group the side opposite to the central axis of the / associated Area. '■

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An essential aspect of the invention "consists in that the radius of curvature of the second group of surfaces is "significant is greater than that of the first surface group, so that the arc length of the first surface is significantly smaller than the arc length of the second surface. The strongly curved surfaces of the first group can be seen as the corners of the six-humped structure are viewed, with the slightly curved surfaces of the second group then forming its sides. The difference-between the largest radial, dimension - from the central axis - the first surfaces and the smallest radial dimension of the second surfaces considerably larger than the radius of curvature of the first group of surfaces, so that in each case between two adjacent Areas relatively large attack surfaces come about.

This way, there is quite a small drive angle_between the driving rope and the driven rope. The relatively large attack surfaces on which driving and driven part are in singreef, deliver a low wing loading and due to the Satsaciie, that sharp corners on the circumference are completely eliminated, no peak loads are generated. Due to the arrangement of curved surfaces, the complementary ones can be made Coupling parts conveniently and with high straightness with the help of Manufacture stamps and dies; because there are no sharp corners,

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the tools have a long service life, The figures are listed below *

Figure 1 is a side view of a portion of a fastener having a "-" head shaped in accordance with the invention; "". - " . \ .-; _,". ■

Pig, 2 is a top plan view of the head of FIG. 1;

Fig. 3 is a schematic sketch that is more precise and clearer the scope configuration. that shown in Figs Head illustrated} * "

Fig. ^ 4 seeigt a "workpiece, from which a fastening means can be produced in the manner shown in FIGS. 1 and 2;

! Fig ·. 5 is a side view of a workpiece during a • middle manufacturing phase in the manufacture of the • fastener; ν

Fig. 6 is a side view, partially sectioned "": "the a "rererkatück for the shaping of the head. of the in Fig.l. illustrated fastening means;

Figure 7 is a side view of the finished billet shows after shaping the head;

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8AD ORIGINAL

Fig. 8 is a side view, partly in section, showing the a driven rope with a mon- » shows driving part;

Figure 9 is a side view of a connecting shaft a driving tool;

Pig.10 is a section along line 10-10 of Pig. Β;

Mg. 11 -is one of the pig. 10 comparable cut, however shows an arrangement of a heretofore known type;

Fig.12 is a side view, partly in section, showing a

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Figure 3 illustrates a driven member in the form of a fastener with a countersunk drive head;

Figure 13 is a top plan view of the fastener of Figure 12; : "'■■. ■■

Flg. Figure 14 is a partially sectioned view of a tool that may be used to make the fastener shown in Figure 13; .. -'-

Fig. 15 is a side view of part of another driving tool, that in connection with the invention Fasteners is useful;

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Pig. 16 and 17 is a side view / or. a brewing look a nut with a surface configuration according to the invention;

Pig. 18 is a section through a pitting according to another Field of application of the invention;

Pig. 19 is a cut - after the line 19-19 of Pig. 18;

Pig.20 and 21 is a section or a plan view of a further embodiment of a fitting according to the invention; ".

Pig.22 and 23 are a side view and a plan view, respectively another embodiment of the invention;

Pig.24 is a sectional view showing a hexagon socket wrench shows attached to an exposed! Ereibkopf according to the invention; ■. .

Pig. 25 is a sectional view showing a hexagonal key in a recess constructed in accordance with the invention shows inserted; . ·

Pig.26 is a side view showing an open-end wrench attached shows on a powered head configured on the outer surface according to the invention;

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FIG. 27 is a sectional view taken along line 27-27 of FIG Mg. 26;

28 is a schematic section along the line 28-28 of FIG. 2. "■ ₌

The invention is initially for a torque transferring Describe connection, such as between a driving part and a complementary driven part can be provided, for example between a fastening means provided with a head and a matching one Rubbing tool or socket wrench. In the Pig. ' I, 2nd and 3rd the upper end of a finished fastener 10 is shown, which has a body with a head 12 and a. Gevandeschaft 14 on the "other end. The head 12 is on one Wfang with the surface configuration used for the attack Mistake. -E has a "widened foot 15 that acts as a washer serves.-The head 12 is bounded in part by a first group of six spaced-apart semicylindrical surfaces 1b. As can be seen even more clearly from the schematic view of FIG. 3, the axes 20 of the surfaces 18 are intrinsically spaced these surfaces and the central axis 19. The axes 20 of the surfaces 18 fall at the tips of a regular hexagon together, which is shown with dashed lines 21. Six semicylindrical ones belonging to a second group Surfaces 22 alternate with surfaces 18 and come on

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the Stoßstfelle smoothly tangentially into the latter about the Srümmüngsachsen the second surfaces 22 which lie at 24, are '■ on the opposite side of the central axis of these surfaces, - arranged. The radius of curvature of the second flat is considerably larger than the radius of curvature; of the first! faces ISj by which the arc length of the faces 22 is much greater than that of the faces 18. Me faces 18 can be referred to as the corners of a hexagonal shape, while the space between these "corners ^{11 represents} the sides of the hexagonal structure.

It should be noted that the largest diameter 25 across the vertices of the first surfaces is very much larger than the smallest diameter 26 across the vertices of the second surfaces. In other words, the distance 28 represents the depth of the grooves between the cusps formed by the surfaces 18. This distance is also the difference between the greatest radial extension of the surfaces 18 and the smallest radial extension of the surfaces 22. This difference is preferably between 20 fo and 30 $ of the greatest radial extent.

For the production of fasteners, as shown in Fig. 2 »is first of a rod or a strand, like he was in Tig when he was 40. 4-illustrates cut off a workpiece. The first time it hits the workpiece in the cold forming machine, the top of the

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Workpiece z \ x ~ eleventh widened block 42 compressed; like him Pig. 5 shows. The upper edge of the block 42 is preferably beveled see 43; at the same time, the lower end of the shaft 44 can be shaped like a cone, as indicated at 45. The block 42 is with the aid of a ram with an insert 48, see Pig. 6, formed into a finished head. The insert 48 is provided with a cylindrical part 49, the diameter of which is only slightly larger than the diameter of the block 42. The latter is in turn only slightly larger than the largest diameter of the finished head measured over the stool. Of course, the workpiece is received in a die while the ram 48 is advanced onto the workpiece * The upper end of the block 42 enters the cylindrical one first. Part 49 and is supported by this against deformation to the side while the ram is advancing. The inwardly rising 'shoulders 50, which form the grooves on the head, direct the. Flow of the metal coming from the ingot, inward, so that the metal in Pig. 5 and 6 is driven upwards until it comes into contact with the bottom of the pushing die 52. As the ram 48 advances further, the lower rope of the block 42 is driven outward and fills the widening 53 of the ram. In the process, the widened foot 15 is shaped, as it is on the semi-finished blank of the Pig. 7 is visible. The finished head 12 of the pig's blank. 7 is thus partly formed in a reverse extrusion process. ¥ he explained in more detail later,

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a head is produced with the described / process, ' which has a higher strength than an exclusively through Compression of the resulting head. The beveled edge 43 am The upper end of the block 42 causes the ram 48 to move without difficulty with the aid of the ejector 52 of the workpiece can be separated without a burr on the top The end of the grooves on the head remains, as it would probably be without the beveling of the pail. The beveled Edge 43 also provides a slight: bevel at the upper ends of the cusps of the finished head, like them at 57 is indicated. In addition, the sloping shoulders carry 58 the one at the bottom of the grooves next to the foot 15 of the finished Head are formed, to help the humps of the head to reinforce.

Fachdem the head is completely formed in the Anköpfmaechine 12, the shank 44 i "may be ⁿ known manner be provided with a thread. The securing means may now so.entstandene as desired still warm treated or plated or both.

The fastening device described so far is of the type who has an exposed operating head .. The associated one Driving tool is therefore provided with an internal, recessed surface configuration that is practical corresponds to the one described; however, the areas are so di-

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dimensioned so that there is a little leeway to allow yourself to be the driving tool conveniently on the * head of the fastener - can be attached. In Pig. 8, a driving tool 62 is shown over the head 12 of the fastener 10. The tool has a connecting! part 64 with a Inner surface 65 which is complementary to the configuration of the head 12 is shaped .. The tool also includes an upper coupling part 67, which has a recess 66 for receiving of the end 69 of a shaft 70 is provided. The shaft 70 is part of a machine driving device 71, which is shown in Fig. 9 is indicated. The depression 66 and the included therein. embedded end 69 of shaft 70 preferably have the same Cross-sectional configuration such as head 12 and part 64, see Fig. 8. A locking ring 68 lies in an ifut- in the Seitenwändeii of the recess 66 and holds the reaming tool 62 on the shaft 70.

Fig. 10 illustrates on an enlarged scale the mutual position of the mutually engaging surfaces of the driving part 64 and the head 12 of the driven part, on the latter of the part 64 a rotational force in the direction of arrow 73 is exercised. As already mentioned, the driving part 64 is with inwardly protruding, convex fla- ' surfaces 72 which are complementary to the concave surfaces 22 of the head 12 and with concaves therebetween Surfaces 74 that are complementary to the convex surfaces 18

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of the head 12 are formed;., - Because of the proportionately great depth of the grooves formed by the concave surfaces 22 »see 28 in Mg. 5, one comes relatively large contact surface for the transmission of the rotary movement conditions. This driving surface, as it is referred to in the following is to be, extends from the deepest point of the groove to the point where the groove tangentially enters the convex surface before the cusp 18 goes over. The so limited Expansion of the driving surface in the circumferential direction is shown in Fig. IO marked with 76. The driving surface 76 is clearly below of the vertex of the neighboring cusp 18> The distance is indicated by the zone ^ 78. This is said to be a ridge zone are designated. The ridge zone 78 extends from the intersection with the end of the adjacent concave Surface 22 to the apex of the cusp 18.

In FIG. 11, a hexagonal wrench 82 is fitted onto a hexagonal driven part 83. When applying torque on the key S2 in the direction of arrow 84 comes There is only contact between adjacent surfaces of the driving and the driven part at points 85 distributed around the circumference To be able to postpone, a certain tolerance must be provided between the complementary surfaces * Below this The condition becomes the whole exercised by the part 82 Torque forces are transmitted through the contact points 85,

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The propulsion angle indicated at 86 is obviously greater than 60 ?. Because of this large propulsion angle is a large component of the. force exerted by the part 82 tends to drive the side walls of this part outward. Often this leads to the side wall bursting if it is not made strong enough to withstand such forces. In addition, the corners of the driven part 83 are deformed and rounded until a sufficient contact area is formed between the adjacent surfaces of the driven part 83 and the driving part 82 for the transmission of the applied rotational force. Often the corners 85 are rounded to such an extent that the driving part 82 can rotate freely on the driven part 83.

In contrast, be on Pig. Referenced 3, at. 87 shows a relatively small propulsion angle, which is preferably about 20 ° or less. As in the empty spaces 80 in Pig. 10, in the example of the invention shown, there is a noticeable margin between the complementary places of the driving tool and the driven part, so that the two parts can be conveniently joined together. Nevertheless, the attack of the driver for transmitting the rotational force from the driving tool to the fastening means takes place over the greater part of the driving surface 76 and consequently with a minimal surface load. As a result, with the rotary joint constructed in accordance with the invention, much larger twisting

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Transferring forces. Than this with previously known rotary joints -fertilize without damaging the surfaces of the driven or driving part was possible.

In the foregoing description, a driven part with a head which has external operating surfaces has been assumed. However, it goes without saying to me as a person skilled in the art that the configuration according to the invention in the same way for driven Parts are applicable that have a head with a recess or receptacle that is shaped complementarily with a th piece of the driving part interacts.

As shown in Figs. 12 and! As can be seen in FIG. 3, FIG. ₉ in this case a fastening means has a threaded shaft 89 with a widened head 88 at one end of the shaft. the

The top of the head 88 is provided with a recess 90 for receiving the driving part. The depression has the same cross section ₉ as schematically shown in FIG. 3 and is provided in the part 64 of the propulsion unit 62. The depression 90 in the head 88 can also be produced in a cold-forming heading machine with the aid of a punch insert 92, as shown in FIG Heading machine pushed forward against a 331ock _? the piece of Ifek at the end of a suitable piece of Ifek cut from a strand or rod

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kes is formed. The protrusion 94 is low 'Conical tip 96 provided, which facilitates the penetration of the punch into the workpiece by directing the flow of metal outwards as the punch advances * The Edge between the conical tip 96 and the side, walls of the actual protrusion is slightly rounded at 95. The inwardly rising shoulders 93 at the foot of the Grooves form a bowl-shaped depression 97 around the depression 90, which allows the end of a driving force to be inserted Partly in the recess 90 facilitated. The cross section con-: figuration of the protrusion 94 is the same as in the Pig. 3 and ^ 10, and therefore need not be explained in more detail will. Due to the fact that the peripheral surfaces of the projection are rounded over the entire circumference and neither have sharp corners on the outside and on the inside, the depression can be shaped without difficulty and with a high degree of accuracy.

he punches have a long life because they are solidly built, di "have a relatively large cross-section compared to its largest diameter, or thin radial \ ribs, as is the Pail with stamps for! forms of conventional Phillips depressions. Furthermore, since there are no relatively narrow approaches to the depression, which run radially outward to the circumference of the head · ^; the risk of the heads of the fasteners breaking at the extreme ends of such lugs is eliminated. Since the cross-section profile is composed of rounded surfaces with a relatively large radius over 360,

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if there are no load peaks in the finished mating strip, see above that high torsional forces can be transmitted via the rotary joint and the stability of the body of the fastener fully can be exploited. This allows a substantial reduction of the entire dimensions of the complementary coupling parts, although from one part to the other turn-r loafte can be transferred that are noticeably above the The limit of the fastening means that the Inside diameter of the attached to the fastener Thread given 1st.

FIG. 15 shows another embodiment of a tool which can be used for engaging a recess, such as that shown as a recess 90 in the head 88 of the fastening means. In this case, the tool is a screwdriver with a shaft 100, at one end of which a coupling part 102 is formed. The coupling part 102 can be formed in a reverse extrusion process using a press die similar to that shown in FIG. 6 or with a different machining process. The corner 101 of the coupling part 102 can be bevelled, as shown in the figure, so that it, in cooperation with the recess 97 on the head 88, makes it easier to insert the four-wheel tool into the counterbore 90. The cross-sectional configuration of the coupling part 102 corresponds to what is described with reference to FIG. 3. The combination of the induction compound shown in FIG. as shown in, Fig. 12, would be the

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same as shown in FIG. 10, but with parts interchanged. In other words: The outer cable 64 in ig * 10 'would, in this Pail the driven member, whereas the inner part 12 of the driving T _e would represent il.

The rotary joint described above is universal in its field of application and in many different cases useful where previously a polygonal surface configuration had been provided to transfer the torque from one part to the other part * For example, in Figures 16 and 17 a nut 106 is shown which has a widened foot 108 serving as a washer. The cross-section of the head part of the nut is clearer shown at 110 in FIG. He has the same configuration, as shown schematically in FIG. The nut 108 is provided with a threaded hole 112.

Figures 18 and 19 illustrate a typical shape of a Fittings (pipe connector) χ The fitting 114 has a Conventional sleeve cutters to a tube 115 on a to attach threaded pipe socket 116. Instead of The fitting in this is the usual hexagonal outer surface Case, however, with a six-humped cross-sectional profile 118, which is identical to that described above for FIG. 3. ·

In FIGS. 20 and 21 a sealing plug is shown,

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which can be screwed into a threaded hole. The plug has in this pail an externally threaded body 120, which carries a flange 122 at the upper end and is provided with a depression 124 on the upper side; "The cross-sectional shape of the depression 124 is the same as shown in Pig. 3.

The Pig. 22 and 23 show another typical example of a connector that is a plug in this pail with a body 126 which carries an external thread. The upper end of the plug is provided with a drive head 128. the The cross-sectional shape of the drive head corresponds to that in Pig. 3 shown.

An / important advantage of the invention is the fact that many conventional porms of keys for the different both the driven parts described above and the exposed as well as the submerged type can be used. It is preferable on every pail if the attack surfaces of the the driving part are completely complementary to those of the driven part; but it can be, for example, in Hot traps happen that the right tool for those with the maintenance person is not always at hand.

In Pig. 24, a socket wrench 130 is illustrated, the receptacle of which has a conventional hexagonal cross-section 132. As the illustration shows is a hexagon socket wrench ■ be readily in connection with one according to the invention

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constructed part 134 with a six-bumped outline can be used. In Fig. 25, conversely, a hex wrench 136 is in a six-humped .sinking 138 of a driven part 137 inserted according to the invention. *

Open-ended spanners of different shapes can also be used for driven parts of the type described here * the. An open-end wrench is shown in FIGS. 26 and 27 as an example. 140 shown, the two of a surface parallel to each other has parking pin 142, both of which protrude perpendicularly from the handle 'of the wrench. The radius of curvature the peg 142, at least on the side facing the head of the driven part 144 applies is only slightly smaller than that of the concave surfaces of the exposed head of the driven part I.44 »Due to the large contact area between the pin I42 and the adjacent surfaces of the driven Part 244 can transmit a large torque between such an open-ended wrench and part 144 will.

For the person skilled in the art it is obvious that other keys can also be used for driven parts with exposed attack surfaces , for example keys with an open end or keys of the so-called Loc-Iiite type.

To compare the torque transmission characteristics at complementary hexagonal rotary joint of the type described above with those of conventional rotary joints

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Tests were carried out on the hexagonal Iyps. I ^{1 For} these tests, heads of both shapes were used on 5/16 inch screws. The conventional hexagonal heads for this screw size have a dimension of 0.50 max. Measured over the flat sides and a height of 0.50 max. Heads shaped in accordance with the invention for this very dome size have an effective height of 0.166, max., A largest diameter, see 23 in Pig. 3, of 0.367 max, and a smallest diameter, see 26 in Fig. 3, of 0.268 max. All Versachsstükke were made of 1Q22 steel and hardened in the same way. Standard hex wrenches were used for the hex heads, and a socket wrench with a receptacle as in Pig, 10 designated 64? was used for the hexagonal heads according to the invention. For the six hex head attempts, approximately 40 pounds (18 kg) of force was applied to the key end and the key slipped at torques of 360 pounds to 450 pounds <4.1 - 5.2 kg :. m) \ on average at 418 inch-pounds (4j.8 kg.m) "Similar experiments were made with six six-humped heads according to the invention, but in this case no force was exerted on the end of the key and the torque would be increased until the slewing ring failed by "shearing off. In these vexes there was no slipping in a single Jtall; a shearing of the head occurred at torques between 660 nominal pounds and 720 three-inch pounds (T. , 6 to 8.5 kg · m) ia liittel ^at: 10 target pounds (t>, - 2 kg.n) ./ the shear strength of the thread of a

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5/16 inch 18 screw made of the same material and also tempered, is 380Zoil-pounds (4.4 kg.m). Although the six- " bumpy head very. much smaller and one substantial The hexagonal head according to the invention contains less material than the conventional hexagonal head no tendency to let the key slip, as is the case with the hexagon head with matching key Case is not even if the key fails a force exerted on the end is pressed. Even though so the six-humped head is a very 'much smaller dimension in the transverse direction than the conventional hexagonal head, it has more than adequate shear strength compared to the shear strength of the screw thread. ·

The pressing process in which the head of the driven Partly molded, it is ascribed that, a high grade $ of strength between the head and the shaft, for example in the case of a fastener as shown in FIG is generated. As shown in Fig. 5, the end of the metal blank 44 in the first stroke of the topping machine only slightly upset. As a result, the metal of the block 42 so formed remains in a relatively unstressed condition State. On the second hit, the grooves in the side wall of the block 42 by means of the converging shoulders 50 of the press ram, see FIG. As from the 28, the converge Shoulders at an angle 150 to the longitudinal axis 19 of the head

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of about 30 °. The compression of the metal between the shoulders 50 of the ram, which forms the shoulders 58 of the finished head, results in a stress zone in the metal of the head which, however, is dome-shaped, as shown by the dashed line 152 indicated. While the metal is not excessively stressed during the reverse pressing process, the connection point between the head and the shaft is not weakened due to the fact that the tension zone extends into the center of the head. Is in some method for Inköpfen, in which the head upsetting steps by a plurality of arrival formed transversely _s generated between the corners 154 on the shaft at the junction between the shaft and head, a highly stressed zone Bin Such a condition is undesirable and often leads to a Break across the shaft just below the head. "

From the above description it emerges that the invention does not relate to Kpfe of fasteners, such as Screws and associated driving tools, limited, but also advantageous for fittings and slewing rings is applicable in a variety of ways. Whether the slewing ring is now exposed or sunk, the driven part is not functional in its functionality depending on the use of a driving part with an identical complementary surface configuration. The tools according to the invention can jaus drivers, stamps or

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There are coupling links to transmit the torque, as shown in Figures 8 and 9 at 67 and 69, respectively are. In either case, the tools or tool parts are alike with little variation between them different shapes.

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Claims (14)

4625467 P a, t e η t a η s ρ r Ü c ti e: 1. Industrial items, especially screw, nut, etc., with . a body containing a first group of objectionable, semi-cylindrical Areas and a second group of with the areas of the first group has alternating semi-cylindrical surfaces which merge tangentially into this group, both of which have axes of curvature extend parallel to each other and to the central axis of the body, the towering axes of the first Area group between these areas and the central axis and the summation axes ^ de: r. ". Second area group on the to the central axis opposite side of the associated surface, characterized in that the cross section of the Prefabricated parts through these surfaces create a symmetrical, hexagonal shape Shape has that the axis of curvatureii / the first Flat group with the tips (20) of a regular hexagon coincide that the radius of curvature (240 of the second Area group is more than twice as large as that of first surface group, whereby the arc length of the second surfaces is significantly greater than the arc length of the first FIa. chen ', and that the difference between the largest dimension «(25) in a radial curve over the first group of surfaces and the smallest radial dimension (26) of the second group of surfaces is significantly larger than the radius of the first surface chen group. V 0 0 9 8 3 0/0 7 1 i ": ²⁸ " • BÄÖ ORIGWÄt, 2. Article according to claim 1, characterized in that the Ka? Üm— the radius of the second surface group no more than four times is as large as that of the first surface group. * 3. Article according to claim 1, characterized in that the. The difference between the largest radial dimension (25) and the first group of surfaces and the smallest radial dimension (26) of the second group of surfaces is at least 20 fo the largest radial dimension (25). - 4. Article according to claim 3, characterized in that the difference between the largest radial dimension (25) of the most surface group and the smallest radial dimension (26) the second group of spaces between # 20 and $ 30 the largest radial dimension. 5. Article according to claim 1, characterized in that the first group of surfaces is convex humps (18) and the second group of surfaces concave grooves (22) on the periphery of a driven one Part form (Fig. 1). 6. Article according to claim 1, characterized in that the first surface group concave, fiiefen and the second surface group * pe inwardly projecting convex ribs on the inner circumference of a Form a recess (9CT) in a driven part (Fig. 12). 009830/071 1 ■■ '"" ^ßAD 7. Article after. Claim 1, characterized in that Both groups of surfaces together form the inner side wall surface form a press ram (Pig * 6). 8. Article according to claim 1, characterized in that the surface . Chen of the first and second groups the outer surface of a Sternpelvorspruges Form (94) which has a tapered tip (96) and in a depression at one end a stamp body (92) is arranged (Pig. 14). 9. Article according to claim 1, characterized in that between the surfaces of the first and second group undjdem -. the rest of the body a widened _s as a washer "nender S ¹ UO (15) is provided (3? ig. I) ₀ 10, article according to claim I _9, characterized ^ that die'er Stalladhengruppe convex cusps: and the second - i ■ I. group 'forms concave grooves andl that each one shoulder ^ i ¹ (48) from the inner end of the stool to the central axis of the body and towards the free end that converges towards Höekar and that these shoulders create a dome-shaped stress zone (152) in the metal which: extends from the junction of the humped section with the rest of the body of the article bulges out towards the free end (Pig. 28). 11. Tool with a body that has an EeLl with a first Group of spaced half-Alindrian! Laugh and 009530/0711 BAD ORIGINAL ^ ³⁰ ~ a second group of surfaces alternating with the first! and has surfaces merging tangentially into these, whose in which the axes of curvature run practically parallel to each other and to the central axis of the body, the axes of curvature the first area group between the associated "areas and the central axis and the axes of curvature of the second surface group on the opposite side of the central axis associated surfaces are, characterized in that the cross section of the bounded by the two surface groups Part has a symmetrical, hexagonal configuration that the axes of curvature of the first group of surfaces with the tips of a regular hexagon coincide, the surfaces of the first group being convex surfaces with a relative small radius of curvature and the surfaces of the second group concave grooves with a radius of curvature that is more than twice as large are and being from; the bottom of each groove that is formed by a surface of the second surface group until to the outermost points of the first surfaces, where they meet the rest of the body, a shoulder (58.) extends. ■. 12. Tool according to claim 11, characterized in that the * free end of the part delimited by the first and second group of surfaces> carries a relatively flat conical tip: (96) and that the corner (95) between the conical tip and the semi-cylindrical surfaces is rounded. - 31 009830/071 1 SAD ORiGiNAL 13. Tool according to claim 11, characterized in that each shoulder (58) is at an angle (150) of about 30 ° extends to the central axis (Fig. 28). 14. Tool for grooved hexagonal heads with a body t which has a part with a first group of spaced apart, semi-cylindrical surfaces and a second group of iBLbzylindrisehen, with the surfaces of the first group alternating and tangential into these surfaces, the two axes of curvature of which meet extend parallel to each other and to the central axis of the body, the axes of curvature of the first surface group between the associated Surface and the central axis and the axes of curvature of the second Face group lie on the side of the associated face opposite the central axis, characterized in that that the cross-section of the part bounded by these surfaces has a symmetrical, six-humped configuration that the axes of curvature of the first group of surfaces with the tips of a regular hexagon coincide in that the surfaces of the first group are concave surfaces with a relatively small radius of curvature, while the surfaces of the second Group of convex ribs with a radius of curvature more than twice as large, and that shoulders form in one Angle from the bottom of the ^ faces of the second group to the outermost points of the faces-the first. Group where this merge into the body, extend and the ribs on the ■ free end of the tool are tapered. 009830/0711 ™ BATH _ 32. '. 162S4 & 7 15 ·. Method for producing a production part according to a of the preceding claims, characterized in that 'a elongated piece of a round metal strand is upset first, so that a block is formed at one end that When this block is formed, a bevel is formed around the upper end of the Baroque without doing so to generate a substantial tension in the metal of the block, that then in a single blow to the body Braid is shaped by taking the two groups of semi-cylindrical Surfaces in the lateral outer walls of the block between several spaced apart, converging at an angle Shoulders are shaped by extrusion, with a stress zone in the metal of the head at a suitable distance from the transverse plane at the joint between the head and the rest of the body is caused. 009830/0711 bad original