EP0403730B1 - Sabot - Google Patents

Description

The invention relates to a segmented dropable sabot for a sub-caliber balancing projectile according to the features in the preamble of claim 1.

Such a conventional two-flange drive cage (push-pull drive cage) with a caliber-sized guide flange on the front and a caliber-sized pressure flange at the rear and over its entire length with a rotationally symmetrical cross section is shown in FIG. Two-flange sabot cages with at least one longitudinal rib on the back of a sabot segment between the front guide flange and the rear pressure flange are, for. B. from US-A-4,326,464 or DE-A-37 04 027 known.
Furthermore, common single-flange sabot (pull sabot) with front pressure and guide flange and rear gas-permeable guide webs z. B. from DE-A-28 36 963 (corresponding to US-A-4,542,696) known. Here, too, the sabot segments have a longitudinal rib in the central circumferential area to increase the bending stiffness.
The advantage of a longitudinal rib construction is that it is the caliber-reduced intermediate area of the sabot between the front guide flange and the rear are used incompletely for the transmission of axial force (introduction of thrust) and thus longitudinal ribs represent for the most part a "dead mass". In addition, the machining of a sabot with a longitudinal rib is very cost-intensive, especially if the longitudinal ribs also have a diagonal or helical course (e.g. B. DE-A 37 04 027). To produce the longitudinal ribs or to work out the intermediate material, expensive, specially shaped special tools are required.

Characteristic of a conventional two-flange drive cage with a rotationally symmetrical cross section as shown in FIG. 1 is a rotationally symmetrical conical or cylindrical cross-sectional reduction between the front flange and the rear pressure flange, following the front radius of the rear pressure flange. For reasons of firing resistance when passing through the pipe, a significantly greater reduction in cross-section in the area behind the front guide flange would be possible, since here hardly any thrust forces are introduced from the sabot into the penetrator. The relatively large cross-sectional area is required in this area, however, in order to give the sabot segments the necessary bending stiffness during the detachment process after leaving the pipe mouth. Conventional two-flange drive cages therefore disadvantageously have an excessive weight, in particular in the area behind the front guide flange.

It is an object of the invention to provide a generic sabot in which an increase in the bending stiffness with a simultaneous reduction in mass and an inexpensive series production of the sabot is made possible.

This object is achieved in that the overall cross section of the sabot at least in a portion of its length, ie a polygon according to claim 1 has an almost triangular or according to claim 17 an almost square cross-sectional shape in which a tangent that can be applied at any point on the periphery of the sabot does not pass through the sabot cross-sectional area. In particular, this enables cost-effective series production with simple processing steps. In conventional sabots with a longitudinal rib, a correspondingly created tangent always runs through the cross-sectional area, so that machining is only possible with appropriately shaped special tools and requires a large number of machining steps. In the triangular sabot according to the invention, the radial distance Ri in the sabot cross-sectional area from the central longitudinal axis A to the outer circumference of the sabot at the outer segment separating surfaces is smallest and in the middle circumferential area of a sabot segment between the two outer segment separating surfaces, so that by mass distribution or Redistribution of area from the peripheral areas on the outer segment separating surfaces of a sabot segment in the direction of the central peripheral area (Tk-segment back) gives an increase in the bending stiffness and the bending resistance moment to a value which is at least as great as the bending stiffness of a comparison driving cage with a approx. 25% larger circular cross-sectional area.
It is thereby advantageously achieved that the bending stiffness of the sabot with a polygonal or almost triangular cross-sectional shape is greater by a factor of at least 1.3 than the bending stiffness of a theoretical sabot with an equally large circular cross-sectional area. With the invention, a reduction in mass of the sabot and a reduction of the sabot cross-sectional area to that necessary when firing in the tube Made possible with a larger bending moment. Such a drive cage is very inexpensive to manufacture, especially in series production.

The invention is explained and described in more detail below with reference to exemplary embodiments shown in the drawings.

Figur 1 und Figur 1a:

einen herkömmlichen Zweiflansch-Treibkäfig mit rotationssymmetrischem Querschnitt,

Figur 2:

den qualitativen Biegemomentenverlauf in einem Treibkäfigsegment während des Ablösevorganges,

Figur 3a, 3b und 3c:

verschiedene Querschnittsflächen von Treibkäfigsegmenten zur Veranschaulichung der Erfindung in Fig. 3c,

Figur 4a und Figur 4b:

weitere Querschnittsformen von erfindungsgemäßen Treibkäfigen,

Figur 5 und Figur 5a:

einen Längsschnitt durch einen erfindungsgemäßen Treibkäfig,

Figur 6 und Figur 7:

Querschnitte durch den erfindungsgemäßen Treibkäfig aus Figur 5 gemäß Schnittlinie VI/VI und VII/VII,

Figur 8:

ein weiteres Ausführungsbeispiel eines erfindungsgemäßen Treibkäfig-Querschnittes,

Figur 9:

eine perspektivische Ansicht eines erfindungsgemäßen Treibkäfigs,

Figur 10 und Figur 11:

Seitenansichten eines erfindungsgemäßen Treibkäfigs in Teildarstellung,

Figur 12:

ein weiteres Ausführungsbeispiel eines erfindungsgemäßen Treibkäfigs in Längsschnittdarstellung,

Figur 13 und Figur 14:

weitere Ausführungsbeispiele von erfindungsgemäßen Querschnittsformen gemäß Schnittlinien XIII/XIII und XIV/XIV in Fig. 12,

Figur 15 und Figur 16:

weitere erfindungsgemäße Ausführungsbeispiele von vierteiligen Treibkäfigen in Querschnittsdarstellung.

Show it:

Figure 1 and Figure 1a:

a conventional two-flange sabot with a rotationally symmetrical cross-section,

Figure 2:

the qualitative bending moment curve in a sabot segment during the detachment process,

Figures 3a, 3b and 3c:

different cross-sectional areas of sabot segments to illustrate the invention in Fig. 3c,

4a and 4b:

further cross-sectional shapes of sabots according to the invention,

Figure 5 and Figure 5a:

2 shows a longitudinal section through a sabot according to the invention,

Figure 6 and Figure 7:

Cross sections through the sabot according to the invention from Figure 5 according to section line VI / VI and VII / VII,

Figure 8:

another embodiment of a sabot cross-section according to the invention,

Figure 9:

2 shows a perspective view of a sabot according to the invention,

Figure 10 and Figure 11:

Partial side views of a sabot according to the invention,

Figure 12:

another embodiment of a sabot according to the invention in longitudinal section,

Figure 13 and Figure 14:

further exemplary embodiments of cross-sectional shapes according to the invention in accordance with section lines XIII / XIII and XIV / XIV in FIG. 12,

Figure 15 and Figure 16:

further exemplary embodiments of four-part driving cages according to the invention in cross-sectional representation.

In Figure 1, the reference numeral 10 is a conventional two-flange sabot with front guide flange 12 and rear pressure flange 14 z. B. in caliber 120 mm for a sub-caliber wing-stabilized balancing projectile 30 made of tungsten heavy metal of high slenderness. Between the sabot 10 and the balancing projectile 30 there is a conventional positive-locking zone (not shown) (with thread or ring grooves). The front guide flange 12 has an air pocket 16 and a circumferential guide band 18 on the front; the rear pressure flange 14 is also provided with a guide band 20 and gas sealing band 22 in the caliber-sized circumferential region. A rear part 24, which tapers conically, adjoins the pressure flange 14.
Usually, the rotationally symmetrical sabot 10 consists of three sabot segments 26, 27, 28 with flat segment separating surfaces 31, 32, 33 in between (FIG. 1a). Between the front guide flange 12 and the rear pressure flange 14, the sabot 10 is designed with a reduced diameter or has a cylindrical / conical cross-section reduction following the rounding radius 34 of the pressure flange 14. In the non-caliber area 36 in the longitudinal extension of the sabot 10, a further or greater reduction in cross-sectional area down to the front guide flange 12 would be possible for reasons of the firing strength of the sabot when passing through the pipe, since for this area 36 only a very low material utilization is given with a conventional design. For reasons of sufficient flexural rigidity in the sabot detachment and thus to avoid uneven and uncontrollable interferences on the penetrator, the sabot 10 in this area 36 must have a still relatively large cross-sectional area. Shelling results have shown that rotationally symmetrical sabot cages, in which the cross-sectional area in area 36 was further reduced, led to an uncontrolled breakage of the sabot cage segments during detachment in area 36 behind the front guide flange 12.

The aim of the development of sabots of sub-caliber balancing bullets is to minimize the sabot mass in order to transfer a maximum of kinetic energy to the penetrator during pipe passage. After leaving the pipe, the sabot is released, caused by the air flow forces acting on the air pocket 16 of the front guide flange 12. The lower the sabot mass and, above all, the lower the moment of inertia of the sabot segments around its rear rolling edge, the faster the detachment process and the lower the kinetic energy loss of the penetrator. This is especially true if in the front part of the Sabotage mass can be saved. Because this mass has the longest lever arm and thus has the largest share of the mass moment of inertia in relation to the rear rolling edge (pivot point of the sabot segments).

Figure 2 shows the process of sabot removal in a slim balancing projectile after leaving the gun barrel muzzle. In an applied coordinate system with the application of the bending moment M _b over the length of the sabot, the sabot performs a pure rotary movement around its rear rolling edge 38 up to an opening angle of Phi (φ) = 20 ° to 30 °. This rotary movement is caused by the air flow forces acting on the sabot, in particular in the area of the front air pocket. For small opening angles Phi (φ), only the dynamic pressure in the air pocket 16 acts, symbolically represented here by the resulting air force F _L. This air force in conjunction with the inertial forces of a sabot segment result in the bending moment curve shown qualitatively in FIG. 2. Characteristic of this course is the very steep increase in the bending moment M _b in the area 36 of the sabot directly behind the front guide flange 12. Therefore, the cross sections of the sabot segments are very vulnerable to breakage, as the results of bombardment have confirmed many times. For safe transmission of bending moments during detachment, a sabot segment in this area therefore requires a cross-sectional area that has a sufficiently large surface moment and bending resistance moment.

FIGS. 3a, 3b and 3c exemplarily show different cross-sections of sabot segments 42, 44, 46. For each of these cross sections are below the corresponding area torque I and the bending resistance moment W _b about the dashed center of gravity axis 40 indicated or compared in a table. The focus is labeled S. The area torque I is a measure of the bending stiffness of the respective cross section of a sabot segment. The linear relationship applies: the larger the surface moment I, the less the deflection of the sabot segment when detached. The bending resistance moment W _b is a measure for the maximum material stress of a cross section under bending load. A linear relationship also applies here: the greater the section modulus W _b , the lower the maximum bending stress in cross section for a given bending moment. Caused by the bending load of a sabot segment during detachment, the bending stresses occur in the cross-sectional area above the center of gravity axis 40 in the form of axial compressive stresses, while in the lower cross-sectional area - viewed in the longitudinal direction of the sabot cage - axial tensile stresses occur. The maximum bending stresses occur in the edge fibers of the cross section at a maximum distance from the center of gravity axis 40. The superscript indices "o" and "u" relate the specified bending resistance moments W _b to the upper and lower edge fibers of the respective sabot segment cross-section. Accordingly, the upper section modulus W _b ^{o is} a measure of the maximum axial compressive stress in the shoulder of the sabot segment cross section, while the lower section modulus W _b ^{u represents} a measure of the maximum tensile stress in the form-locking area of the sabot cross section at the two outer segment boundaries occurs. If the lower bending resistance torque is too small, a crack is initiated in the sabot cage detachment due to the bending tensile stress in the notch base of a thread. which leads to the breakage of the sabot segment in the area 36 behind the front guide flange 12. If, on the other hand, the upper bending resistance moment is too small, plasticization merely results in a rearrangement of the compressive stress peaks in the shoulder of the respective sabot segment cross-section; however, it cannot break.

In the calculation examples attached, the cross section 1 represents the rotationally symmetrical sabot segment 42 according to FIG. 3a, the cross section 2 the reduced rotationally symmetrical sabot segment 44 according to FIG. 3b, the cross section 3 the first inventive sabot segment 46 according to FIG. 3c, the cross section 4 shows a further sabot segment 47 according to the invention in a total area representation according to FIG. 4a and the cross section 5 a modified sabot cage segment 48 according to the invention in a total area representation according to FIG. 4b. The cross section 1 in FIG. 3a shows the cross-sectional area of a sabot segment in the area 36 of the in FIG 1 shown known sabot 10 of the latest design. This cross section 1 has sufficiently large section modulus to reliably absorb the bending moment in the sabot detachment. In order to transmit the axial forces occurring during the passage of the pipe to accelerate the penetrator, only the circular cross-section 2 according to FIG. 3b with an approximately 25% smaller area would be required. Such a large reduction in area would result in an enormous weight saving on the sabot, but the bending resistance moments of the rotationally symmetrical cross section 2 (FIG. 3b) are much too small and lead to the uncontrolled rupture of the sabot segments 44 during the detachment process, as bombardment results have clearly confirmed.

The principle of the solution according to the invention is now based on the use, preferably in the area 36 of a sabot segment 46 that is prone to bending or breaking, of novel cross-sections of a comparatively smaller area with a sufficiently large area torque and bending moment.

Cross sections 3, 4 and 5 in Figures 3c, 4a and 4b show sabot segments according to the present invention. They are no longer rotationally symmetrical and, in comparison to the conventional circular cross sections 1 and 2 in FIGS. 3a and 3b, are distinguished by a compact larger profile height and in each case two flat peripheral surfaces 64, 66. In this case, a tangent 54 that can be applied to any point of the sabot circumference 56 does not pass through the sabot cross-sectional area 50 (see FIG. 6). All of the sabot segments according to the invention listed here have a cross-sectional area that is approximately 25% smaller than the comparison cross-section 1 in FIG. 3a.

Driving cages according to the invention according to FIG. 5, FIG. 6, FIG. 7, FIG. 9, FIGS. 10 and 11 have already been manufactured in the 120 mm caliber and have been successfully fired. Due to the triangular or polygonal cross-sectional design of the sabot segments according to the invention, such a sabot is about 100 g or about 6% lighter than a comparable modern sabot of conventional design with a rotationally symmetrical cross section.
The driving cage segment according to FIG. 3c with cross section 3 is, for example, 7.4% more rigid than the comparative cross section 1 (FIG. 3a) and even has a 5.2% greater bending resistance moment in the tensile stress range of the thread, which is at risk of cracking.
The situation is even more favorable with the sabot segment cross section shown in cross section 4 (FIG. 4a). This profile is clear by 65.2% more rigid than the comparison cross-section 1 (Figure 3a). The thread area, which was originally prone to cracking, has become completely uncritical in this profile because of the 37.7% lower bending moment.

From a manufacturing point of view, the sabot segments according to cross-section 4 (FIG. 4a) and cross-section 5 (FIG. 4b) are distinguished by the fact that the outer profile edges are inclined by 30 ° to the center line of the cross-section or, in other words, in cross-sectional view the flat peripheral surfaces of each sabot cage close -Segment 47 in the back area between the segment separating surfaces 61, 62 an angle of exactly 60 ° and are thus at right angles to the respectively adjacent segment separating surface 61, 62. For production, this means that the entire sabot in the area of the cross-sectional shape according to the invention cuts in only three milling planes If two adjacent flat circumferential surfaces 56 of two adjacent sabot segments 47 along the intervening segment dividing line 62 in the circumferential direction must merge straight or evenly into one another (FIG. 4a). In cross section 3 (FIG. 3 c) there would be six milling planes in the event that two adjacent flat peripheral surfaces of two adjacent sabot segments along the intervening segment dividing line 32 merge or adjoin one another in the circumferential direction at an angle of less than 30 ° (FIG. 6) . Simple cheap cylindrical cylindrical milling cutters can be used for these milling operations on the flat peripheral surfaces.

The geometric peculiarity of the sabot segment profile shown in FIG. 4b according to cross section 5 is that the profile flanks or flat peripheral surfaces do not differ in comparison to cross section 3 and 4 (FIG. 3c, FIG. 4a) cut more in one point. The shoulder of this cross-sectional profile therefore no longer consists of just one point, but of an arc 58. The advantage of this sabot segment construction compared to cross-section 4 (FIG. 4a) is above all the significantly improved upper bending moment. It is only 0.8% smaller than that of the comparison cross section 1 in FIG. 3a.

Another triangular or polygonal sabot cross section that is favorable in terms of production technology is shown in FIG. Here, instead of the flat circumferential surfaces, slightly outwardly curved or curved circumferential surfaces 68, 70 are provided, while a strongly curved or rounded circumferential region 58 is arranged in the back area between these circumferential surfaces. The advantage of this rounded design lies in the possibility of manufacturing technology to be able to manufacture this sabot as an inexpensive "turned part" on an eccentric lathe.

As already described, the principle of the solution according to the invention is based on using non-rotationally symmetrical cross sections with a smaller area but a larger area torque and bending resistance moment in comparison to conventional rotationally symmetrical cross sections, in particular in the bendable sabot segment area behind the front guide flange of the sabot.

In principle, the triangular cross-sectional surface design of the sabot according to the invention can be used in all non-caliber areas, in particular for sabots with a large length, such as. B. sabot cages for two tandem projectiles arranged one behind the other, the non-rotationally symmetrical cross section can also be provided in the elongated tapered rear part behind the pressure flange in order to increase the bending stiffness there as well.

In the sabot according to the invention shown in FIG. 5, however, for reasons of firing resistance when passing through the pipe, it does not make sense to arrange the web profiles according to the invention in the entire length range of the sabot between the front guide flange 12 and the rear pressure flange 14. The rotational symmetry in the region of the fillet radius 34 in front of the pressure flange 14 should be preserved in any case. For the length L defined in FIG. 5 as the distance between the pressure flange 14 and the beginning of the non-rotationally symmetrical cross-sectional profile in the sense of this invention, the following applies: L greater than D / 5 (with D equal to caliber diameter) L ≧ D / 5. The arrow 52 indicates the firing direction of the sabot arrangement.

The sabot configurations according to the invention shown in the drawings FIG. 5, 9, 10 and 11 have a constant cross-sectional area in the entire non-rotationally symmetrical sabot area. Since, during firing during the passage of the pipe, the axial forces to be transmitted from the sabot segment for increasing acceleration and support of the penetrator increase with increasing distance from the front guide flange 12 to the rear, it makes sense to design the area of the sabot at risk of bending with a profile according to the invention as in FIG. 5a is shown, the cross-sectional area of which increases continuously starting from the front guide flange 12 in the direction of the rear pressure flange 14. The flat circumferential surfaces 64, 66 of the sabot segments can run slightly obliquely to the longitudinal axis A and the rounded intermediate region 58 between two flat circumferential surfaces - if it is provided - would accordingly widen from front to back.
FIGS. 9, 10 and 11 show in perspective or side view in partial section the sabot 60 according to the invention with the sabot segment cross-sectional area shown in FIG. 3c (cross section 3).

With the invention, a significant reduction in mass (dead load component) of a sabot can be achieved with a substantial increase in its bending stiffness, as described. A simple and inexpensive series production is made possible. The application of the invention is conceivable for all possible weapons with small or large calibers as well as with drawn or smooth tubes from which sabot projectiles can be fired. The profiles according to the invention can be used not only with two-flange drive cages, but also with single-flange drive cages.

A further sabot 60 according to the invention is shown in FIG. Here, the triangular cross-sectional area is formed not only in the front length region 36 between the front guide flange 12 and the rear pressure flange 14, but also in the rear rear part 24 behind the pressure flange 14. The arrangement of a polygonal cross-sectional shape 72 on the rear part 24 of the sabot 60 also results in an increase in bending stiffness in this area without an additional increase in mass.

In the cross-sectional shape of the sabot 60 shown in FIG. 13, the curvature of the outer surface 70 of the polygonal cross-sectional shape 72 is curved slightly convexly outwards.

The reference number 80 denotes the original circumferential surface, 82 indicating the maximum distance a between the curved outer surface 70 of the cross-sectional shape 72, and 74 the maximum distance b of the curved outer surface 70 from a straight line 76 connecting the corner points 78. The principle of the smallest possible curvature of the outer surface 70 is expressed geometrically in that b ≦ a.

FIG. 14 shows the cross section of the sabot 60 shown in FIG. 12. While the cross-sectional shape according to the invention shown in FIG. 13 characterizes the area in the rear part 24 behind the pressure flange 14, FIG. 14 shows the cross section in the middle back area 36 between the front guide flange 12 and the rear one Pressure flange 14.

These two exemplary embodiments are also interchangeable. The cross section, as shown in FIG. 13, can thus also be applied to the central back region 36 of the sabot 60, and the cross section shown in FIG. 14 can accordingly also be arranged on the rear part 24 behind the pressure flange 14. Furthermore, there is the possibility that the two cross-sectional shapes 72, 72 'shown in FIGS. 13 and 14 merge into one another.

The reference numeral 72 'denotes the polygonal cross-sectional shape, which is modified here in such a way that the adjacent slightly curved outer surfaces 70 do not directly adjoin one another, but are each separated from one another by a narrow piece of the arcuate outer surface 58. The center of this circular arc-shaped outer surface 58 with the radius R _pol lies in the center A of the total cross-sectional surface 72 'of the sabot 60 corresponds to the intersection of the three segment separating surfaces 31, 32, 33. The reference character c in FIG. 14 denotes the length 86 of the segment separating surfaces 31, 32, 33. The circumferential length 84 of the arc-shaped outer surface 58 is smaller than the length c, 86 of the segment separating surfaces 31, 32, 33. The curvature of one As already shown in FIG. 13, the outer surface 70 is as small as possible. In this case, a, 82 'again represent the maximum distance between the curved outer surface 70 of the cross-sectional shape 72' and the circumference 80. The straight line 76 in this illustration connects the corner points 78 '. Compared to FIG. 13, in which there are three corner points 78, six corner points 78 'are obtained with this cross section in that the curved outer surfaces 70 do not directly adjoin one another, but are separated from one another by circular arc segments 58. Each curved peripheral surface 70 has two corner points 78 'with the adjacent circular arc segments 58. These are connected to each other by straight line 76. The maximum distance from this straight line 76 to the curved outer surface 70 is identified by b, 74 '. The smallest possible curvature is determined geometrically, as in FIG. 13, by the fact that b ≦ a.

FIG. 15 shows the cross section of a sabot 88, which is divided into four sabot segments 90. The essentially square cross-sectional shape can also be applied to a partial area of the length extension of a four-part sabot 88 using simple turning techniques.
The four outer surfaces 70 'of this square cross-sectional shape are slightly convexly curved outwards. As described with reference to FIGS. 13 and 14, the curvature of the curved outer surfaces 70 'is also as small as possible here and in turn is determined geometrically by the fact that the maximum distance b between the straight line 76 connecting the corner points 78 ″ to the curved outer surface 70 is less than or equal to the maximum distance a between the curved outer surface 70 ′ and the original circular circumferential surface 80. The four segment separating surfaces of the sabot segments 90 are arranged such that the radial distance from the central longitudinal axis A to the curved outer surface 70 ′ is the smallest at the segment separating surfaces.

FIG. 16 modifies FIG. 15 in such a way that each sabot segment 90 has, in cross-sectional view, a narrow piece of circular-arc-shaped outer surface 58 'between the two adjacent slightly curved outer surfaces 70'. The center of this circular arc-shaped outer surface 58 'with the radius R _qua lies in the center A of the total cross-sectional area of the sabot 88. This center again corresponds to the intersection of the segment separating surfaces. This embodiment in particular has a very slight curvature of the outer surface 70 '.

The cross sections shown in FIGS. 15 and 16 can be converted into one another. The distance b in Figure 15 is specified by the lathe used. The curvature of the outer surfaces 70 'can be varied by the eccentricity of the lathe.

Definitions:

$${\text{f}}_{\text{i}}\text{: =}\frac{{\text{A}}_{\text{i}}\text{-A₁}}{\text{A₁}}{\text{; t}}_{\text{i}}\text{: =}\frac{{\text{I.}}_{\text{i}}\text{-I₁}}{\text{I₁}}{\text{; q}}_{\text{i}}\text{: =}\frac{{\text{W}}_{\text{bi}}{\text{- W}}_{\text{b, 1}}}{{\text{W}}_{\text{b, 1}}}\text{; i = 2,3,4,5}$$

Claims (19)

1. Segmented discardable sabot (60), particularly one of considerable length, for a sub-calibre penetrator projectile (30) with a high degree of slenderness, with at least two sabot segments (26, 28) with at least two plane-parallel separating surfaces (32,33) and with at least one large-calibre gas-sealing pressure flange part (14), measures being taken in those zones (36) of the sabot which are not of large calibre to increase the flexural strength, characterised by the fact that the overall cross section (50) of the sabot (60), at least over part of its length, has a substantially triangular cross-sectional shape in which a tangent (54) which can be placed against every point on the sabot periphery (56) does not pass the cross sectional surface (50) of the sabot (Fig. 3c, 4a, 4b, 6, 7, 8).
2. Sabot in accordance with Claim 1, characterised by the fact that in the triangular cross-sectional shape the radial distance (R_i) from the central longitudinal axis (A) to the outer periphery (56) of the sabot (60) is at a minimum on the outer segment separating surfaces (61,62,63) and the radial distance (R_a) in the median peripheral zone of a sabot segment (46,47,48) is at a maximum between the two outer segment separating surfaces (61,62,63), while by mass distribution or cross-sectional surface redistribution, from the peripheral zones of the outer segment separating surfaces (61,62,63) of a sabot segment (46), with a circular cross-sectional surface of the same size, in the direction of the median peripheral range, an increase of the flexural strength as well as of the flexural resistance moment is provided to a value which is at least as great as the flexural strength of a comparable sabot with a circular cross-sectional surface about 25% greater (Fig. 3a, 3b, 3c, 4a, 4b).
3. Sabot in accordance with Claim 1 or 2, characterised by the fact that the flexural strength of the sabot with a polygonal or approximately triangular cross-sectional form is greater by a factor of at least 1.3 than the flexural strength of the theoretical sabot with a circular cross-sectional surface of the same size (Fig. 3b and 3c).
4. Sabot in accordance with Claim 1, 2 or 3, characterised by the fact that each sabot segment (46) has at least two plane peripheral surfaces (64,66) (Figure 3c, 4b).
5. Sabot in accordance with Claim 1, 2 or 4, characterised by the fact that two adjacent plane peripheral surfaces of two adjacent sabot segments continue in or are contiguous with each other along the segment separating line (32) in the peripheral direction at an angle of less than 30° (Fig. 6).
6. Sabot in accordance with Claim 1, 2, 3 or 4, characterised by the fact that two adjacent plane peripheral surfaces (56) of two adjacent sabot segments (47) continue over a straight or plane course in each other along the segment separating line (62) in the peripheral direction.
7. Sabot in accordance with one of the foregoing Claims 1 to 6, characterised by the fact that, as viewed in cross section, the plane peripheral surfaces (56) of each sabot segment (47), in the rear zone between the segment separating surfaces (61,62), enclose an angle of 60° and are at right angles to the adjacent segment separating surface (61,62) (Fig. 4a).
8. Sabot in accordance with one of the foregoing Claims 1 to 7, characterised by the fact that between the plane peripheral surfaces (64,66) of each sabot segment (48), in the rear zone, a bevelled or rounded peripheral zone (58) is provided (Figure 4b).
9. Sabot in accordance with one of the foregoing Claims 1 to 8, characterised by the fact that in place of the plane peripheral surfaces, peripheral surfaces (68,70) are provided which curve slightly outwards, while in the rear zone between the slightly curved peripheral surfaces (68,70) a distinctly curved or rounded peripheral zone (58) is provided (Figure 8).
10. Sabot in accordance with one of the foregoing Claims 1 to 9, characterised by the fact that the triangular cross-sectional form is only provided in a certain zone (36) of the length of the sabot (60), between the front guide flange (12) and the rear pressure flange (14), this longitudinal zone (36) being directly connected up to the front guide flange (12) while the remaining zone, of smaller calibre diameter, is formed in a rotationally symmetrical manner in front of the pressure flange (14) (Fig. 5).
11. Sabot in accordance with Claim 10, characterised by the fact that the longitudinal zone (36) with the triangular cross-sectional surface amounts to less than 80% and preferably to about 60% of the distance between the front guide flange (12) and the rear pressure flange (14) (Fig. 5).
12. Sabot in accordance with one of the foregoing Claims 1 to 11, characterised by the fact that the plane peripheral surfaces (64) of a sabot segment (46) slant slightly in relation to the longitudinal axis (A) (Fig. 5a).
13. Sabot in accordance with one of the foregoing Claims 1 to 12, characterised by the fact that the three external surfaces (70) of the triangular cross-sectional shape of the sabot are slightly convex towards the outside, resulting in a polygonal overall cross section.
14. Sabot in accordance with Claim 13, characterised by the fact that the convexity of curvature of an external surface (70) of the polygonal cross-sectional shape (72) is made as small as possible and satisfies the geometrical conditions (b ≦ a) wherein B is equal to the maximum distance (74) of the convex external surface (70) from a straight line (76) between the two outer corners (78) of the convex external surface (70) while a is equal to the maximum distance (82) between the convex external surface (70) and the original circular peripheral surface (80).
15. Sabot in accordance with Claim 13 or 14, characterised by the fact that each sabot segment (42,44,46) as viewed in cross section, in the median rear zone (84) between the two adjacent slightly curved external surfaces (70), has a narrow portion or arcuate external surface (58) of which the radius (R_pol has its origin in the centre (A) of the overall cross-sectional surface of the sabot (60,72) (at the same point of intersection of the segment separating surfaces).
16. Sabot in accordance with Claim 15, characterised by the fact that for any sabot cross section the length of the portion of arcuate external surface (58), as viewed in the peripheral direction, is less than or equal to the length C (86) of the segment separating surface (31,32,33).
17. Segmented ejectable sabot (88), particularly of considerable length, for a sub-calibre penetrator projectile with a high degree of slenderness, with at least two sabot segments with adjacent plane-parallel segment separating surfaces and with at least one gas-sealing pressure flange part of large calibre, measures being taken in those zones of the sabot which are of large calibre to increase the flexural strength, characterised by the fact that the overall cross section of the sabot (88), when subdivided into four sabot segments (90), has at least over part of its length a substantially square cross-sectional form, in which a tangent n which can be placed against a point on the periphery of the sabot does not pass through the cross section surface of the sabot.
18. Sabot in accordance with Claim 17, characterised by the fact that the four external surfaces (70) of the square cross-sectional shape are slightly convex towards the outside.
19. Sabot in accordance with Claim 17 or 18, characterised by the fact that each sabot segment (90), as viewed in cross section, in the median rear zone between the two adjacent slightly convex external surfaces (70'), has a small portion of arcuate external surface (58) of which the radius (R_qua) has its origin in the centre (A) of the overall cross-sectional surface of the sabot (88).

Images