EP2405045A1 - Circular sled guide for a braiding machine - Google Patents

Abstract

The guide has outer rollers (6) attached to a support plate (4) such that an outer surface of carriages (20) rolls on a surface (38) of the outer rollers, which are rotated by roller bearings. A set of inner rollers (8) inner radially guides the carriages. The inner rollers are attached to the support plate such that an inner surface of the carriages rolls on the surface of the inner rollers, which are rotated by the roller bearings. Weight of the carriages and a spool support (16) is guided by one of the roller bearings. A wear ring (36) is made from ceramic material.

Description

The invention relates to an intended for a braiding circular slide track guide according to the preamble of claim 1. It is therefore in the braiding machine to a so-called Rotationsflechtmaschine.

Braiding machines are used in particular for braiding wire or textile fabrics and have at least two sets of delivery bobbins. The supply spools serve to receive the so-called warp and weft threads. In order for the weft thread to pass through a compartment formed by the warp threads, associated sets of supports to which the supply spools are attached must move relative to each other about an axis of rotation of the machine. As a rule, both the coil carriers for the weft thread and the coil carriers for the warp thread each execute a rotational movement about the machine rotation axis, the rotational movements being opposite to one another. The weft spools can be arranged both in a smaller radius and in a larger radius than the warp thread bobbins to the rotation axis, which additionally perform a substantially vertical movement for shedding during braiding. The so-called braiding point at which the tissue arises is normally located on the machine axis of rotation.

From the DE 10 2005 058 223 A1 is a generic circular carriage track guide known. In this case, rotary bearings are arranged for the outer radial guidance of the coil carrier along the guide track, whose pivot bearing axes extend at least approximately parallel to the axis of rotation of the machine. For internal radial guidance of the carriage, however, a sliding guide is provided. That is, the carriages slide with an inner surface at an upper and at a lower end along a heel or collar of an upper and a lower guide plate, between which the outer roller bearings are arranged for external radial guidance. Furthermore, sliding surfaces are also provided for axially guiding the coil carrier. Thus, the weight of the carriage and attached to this bobbin, including wound yarn material is added via these sliding surfaces or sliding guide.

A disadvantage of this known Schlittenbahnführung that the said weight can not be absorbed uniformly over the slide. The reason for this is that the bobbins are laterally offset to the carriage attached to this, so that with the weight of a lever action is connected. The resulting torque, which is also unavoidable due to this conventional arrangement of the bobbin, ensures that the sliding of the slide takes place reinforced edges of the carriage. A given pressing of edges of the carriage against the corresponding sliding surfaces of the two guide plates causes a particularly strong friction and makes it necessary to use a high amount of lubricant, which is also difficult to control. A major problem of the lubricant used in this way is that it can be distributed within the braiding machine and in particular can soil the threads and thus the tissue to be produced.

Furthermore, with the described edge pressing the problem of high wear on the sliding surfaces is connected, as far as this can not be compensated by a sufficient lubrication of the surfaces. The adequate lubrication and bending caused by the edge pressure are a cause of the machine and product contamination.

The entire system consisting of reel, spool carrier, outer and inner support of the guide bearing must be able to pass through the warp shed, in particular the diameter of the reel flanges and the extension of the guide bearing are decisive sizes. There is, in fact, the essential requirement with regard to minimized radial expansion of a guide bearing for a carriage, that the angle of the compartment opening needs only to be so large that the bobbin together with its Fadenleitblechs passes through the subject. In contrast, the components of the guide bearing, moreover, should not require a larger opening angle, but rather remain in the shadow of the thread guide, so to speak. The compartment width should thus be determined only by the coil carrier, but not by the guide means of the bobbin. A standard opening width of approx. 170 to 185 mm is usual for a coil flange with a diameter of 80 mm.

The greater the extent of the system of the bobbin carrier guide in the direction of the machine center, the further must be the shed opening angle. Although this could be counteracted by an increase in the machine diameter, which would also cause a larger range. However, an increase in diameter should be avoided because it would lead to an increase in the sliding and rolling speed with the corresponding disadvantages of higher centrifugal load of the complete system and thus in particular again to a higher lubricant consumption at the same speed.

In the known Schlittenbahnführung the required space has been shortened by the use of a sliding bearing, but the disadvantages described above must be taken into account.

Beyond the inner radial sliding guide, it is also very disadvantageous in the known carriage track guide that the weight of the carriage and the coil carrier is absorbed by the sliding guide, which is associated with the problem of friction. This circumstance contributes significantly to the lubricant problem.

The invention is therefore based on the object to provide a generic carriage track guide available, occurs in the sliding friction only to a relatively small extent.

The object is solved by the features of claim 1. The circular carriage track guide is provided for a braiding machine having at least two sets of supply bobbins. The supply spools serve to deliver the filament material used for braiding by a corresponding unwinding during the braiding process for the latter, whereby the spools become lighter over the duration of the braiding process. For example, the weight of a single spool carrier with fully wound thread material may be about 5 kg. The bobbins are each attached to a carriage of the circular carriage track guide. The carriages must be guided radially both externally to receive the centrifugal force and inside. Furthermore, the carriages must of course be axially guided due to their own weight and the weight of the coil carrier.

For outer radial guidance, the carriage track guide has a set of outer rollers. These are mounted on a substantially circular support plate of the carriage track guide, that the respective carriage, which is curved with a corresponding radius over its circumference, with an outer surface on a rotatably mounted surface of the respective outer roller is unrolled. The rotation of the roller surface is achieved by the use of rolling bearings.

Also for the inner radial guiding of the carriage a set of inner rollers is attached to the support plate accordingly. With an inner surface, the carriages therefore also roll on the rotatably mounted surface or rolling surface of the inner rollers during braiding. Rolling bearings are also used in these rollers. Hereinafter, the rolling bearings of the inner rollers will be referred to as "inner" and the roller bearings of the outer rollers as "outer" roller bearings and the surfaces of the inner and outer rollers serving to roll the carriage surfaces as "rolling surfaces".

Furthermore, the invention is characterized in that the weight of the coil carrier and the carriage is received via at least one of the inner and outer bearings.

Due to the slide guide realized radially both externally and internally by means of rollers, essentially only one rolling friction occurs here. There is only a small amount of sliding friction. This results essentially from the fact that the rotational speed of the rollers slows down after passing a slide, for example by 10%, and the rollers are accelerated again in their rotational speed when they reach a slide again. During the acceleration, which can take place, for example, eight times per machine revolution, gliding of the inner or outer surface of the respective carriage and the rolling surfaces and thus sliding friction occurs to a certain extent. However, their share is very low compared to the rolling friction. A very small proportion of sliding friction can still occur due to a basically caused by pressure deformation in the form of small differences in speed caused by the deformation and thus no pure unrolling can take place.

By at least one roller bearing of the respective role is such that it can be exposed to an axial load and thus can absorb part of the weight of the bobbin and associated carriage, it is achieved that this weight is essentially only in the form of rolling friction and only to a relatively small extent in the form of sliding friction. The advantages of the lowest possible sliding friction force are described above and are briefly summarized in the fact that only a small amount of lubricant must be used and that, moreover, its quantity is easily controllable.

According to a preferred embodiment of the carriage track guide according to the invention, the rolling surfaces are cylindrical in at least one set of rollers, said rollers having a wear ring at an upper end. This wear ring is arranged so that a collar portion of the respective carriage with the own and the weight of the bobbin this is when the carriage rolls with its inner or outer surface on the rolling surface. The collar portion of the carriage is formed so that a shoulder extends substantially radially inwardly and outwardly from the inner and outer surfaces, respectively. Preferably, such a collar portion is provided in both radial directions and provided accordingly that both the inner rollers and the outer rollers have a cylindrical rolling surface and a wear ring.

Between the surfaces of the wear ring and the collar section which come into contact with each other, there is a proportion of rolling friction and sliding friction. However, due to the rotational movement of the wear ring about its own axis, the rolling friction rate is considerable, so that the remaining sliding friction ratio is small as compared with the above-described known carriage track guide.

The cylindrical rolling surfaces ensure that due to the existing torque described above hardly edge pressure occurs, but rather the torque is absorbed as evenly as possible over the cylindrical rolling surfaces away.

Preferably, the wear ring is fastened by means of a clamping screw. The clamping screw is screwed from above into a body portion of the roller and presses the wear ring with a screw head at an inner edge of the upper free wear ring surface. By means of such a clamping screw, the wear ring can be replaced easily and quickly, when it has reached a predetermined degree of wear.

The wear ring may be made of various materials, especially ceramic. The advantages of ceramics are high wear resistance, dimensional stability and thermal shock resistance.

Preferably, the material of the wear ring and that of the respective collar portion are matched to one another.

According to a further embodiment of the carriage track guide according to the invention can also be provided that the weight of the carriage and the bobbin is transferred by positive engagement between the inner and / or outer surface of the carriage and the rolling surface on the inner and / or outer rollers. In particular, when this weight force transmission takes place completely by a positive connection, the sliding friction component can be reduced to a very low level. This is essentially only caused by the above-described acceleration of the rollers when passing a carriage.

In particular, the rolling surface may be convexly curved in at least one of the roller sets, but preferably both in the inner and the outer rollers, and the associated inner or outer surface of the carriages rolling thereon may be concavely curved. In the case of such a form fit, in practice it will be the case that two circular contact lines are formed on which unwinding takes place. This means that in practice no uniform contact of the rolling surfaces is given. However, the two contact lines do not mean a particularly high material wear. A significant advantage of this embodiment is that it can be assumed that the contact lines can change slightly in their axial position in the course of the development of the thread material from the spool and the associated reduction of the bobbin weight. It is thus avoided in comparison to the prior art that the changing weight force has a noticeable effect on the running behavior of the carriage or the rollers.

Of course, it is also possible that the rolling surface is concave and the inner or outer surface of the carriage is convex.

Both in the cylindrical rolling surface embodiment and the curved rolling surface embodiment, the inner and outer rolling bearings may include one or more radial deep groove ball bearings. Take this essentially the weight of the carriage and the bobbin including thread material. The advantage of such a ball bearing is that it can accommodate a relatively large axial load in addition to the radial load. In the carriage track guide according to the invention, the entire weight of the respective carriage and the associated bobbin can be absorbed. For example, it can be provided that in the embodiment with curved rolling surfaces these rolling surfaces represent the surface of a turntable which is rotatably supported by means of a respective radial and deep groove ball bearing arranged above and below. In this case, the roller can be fixed in a bore of the support plate by means of a shaft arranged below the rolling surface.

The radial deep groove ball bearing is preferably a double sealed ball bearing. This has the advantage that a lifetime lubrication is possible and thus can be avoided in particular that lubricant reaches the material to be braided.

It is also possible that the inner and outer bearings have a radial needle roller bearing in addition to a radial deep groove ball bearing. A significant advantage of such a needle bearing over a ball bearing is that it allows a higher maximum speed due to more favorable mass ratios. This in turn allows a higher engine speed. The weight is absorbed by the radial deep groove ball bearing. The needle bearing may in particular be a double-row radial needle bearing. In this case, two needle-shaped rolling elements are arranged axially one above the other. It is preferably provided that the needle bearing can be relubricated via a grease nipple. Another advantage of a needle bearing is that it tends to take up less space than a ball bearing. The weight-collecting radial deep groove ball bearings can be arranged below the needle bearing. Since the needle bearing fully absorbs the radial load, the radial deep groove ball bearing mainly serves to catch the weight. It is preferably provided that the deep groove ball bearings in its angular relationship to adjust the needle bearing something to avoid overdetermination in the attachment of the role in the support plate.

Both in the embodiment of the carriage track guide with the curved rolling surface and the embodiment with the cylindrical rolling surface can be provided that the rolling surface having component of the respective roller is rotatably mounted relative to the support plate in this. In this case, in particular the beschriebende combination of a radial needle roller bearing and a radial deep groove ball bearings can be provided. However, it is also possible two superimposed within the support plate radial deep groove ball bearings. The inner race of the needle bearing can be given by a shaft of the respective role. The arranged above the support plate body portion of the roller has the rolling surface. Preferably, the body portion has a cavity to reduce the rotating mass inside. In particular, the clamping screw described above can be screwed into this cavity.

The rollers may be arranged so that a carriage is at the same time predominantly in contact with three outer rollers, but for a short time only with two outer rollers. The group of inner and outer rollers, which are arranged between two required for shedding by the warp thread, gap-like recesses of the support plate is here together with a located between the recesses support plate portion referred to as a guide unit. For example, a guide unit may have three inner and four outer rollers.

According to claim 11, a braiding machine according to the invention is provided in particular, which has a slide track guide according to the invention.

According to the invention, in particular, a braiding machine with 6 to 48 supply spools can be provided.

• Fig. 1 eine perspektivische Teilansicht eines Schussfadenträgers, der innere und äußere Rollen mit einer zylinderförmigen Rollfläche aufweist,
• Fig. 2 eine Teildraufsicht auf den Schussfadenträger gemäß Fig. 1,
• Fig. 3 die Schnittansicht gemäß Linie III-III in Fig. 2,
• Fig. 4 eine Seitenansicht einer inneren bzw. äußeren Rolle der Fig. 1,
• Fig. 5 die Schnittansicht gemäß Linie V-V in Fig. 4,
• Fig. 6 eine Draufsicht auf die Rolle gemäß Fig. 4,
• Fig. 7 eine perspektivische Ansicht eines Schlittens der Schlittenbahnführung gemäß Fig. 1,
• Fig. 8 eine perspektivische Teilansicht eines Schussfadenträgers, der innere und äußere Rollen mit einer gewölbten Rollfläche aufweist,
• Fig. 9 eine Schnittansicht des Schussfadenträgers gemäß Fig. 8 entsprechend Linie III-III in Fig. 2,
• Fig. 10 eine Draufsicht auf eine innere bzw. äußere Rolle der Fig. 8,
• Fig. 11 die Schnittansicht gemäß Linie XI-XI in Fig. 10,
• Fig. 12 eine perspektivische Ansicht eines Schlittens der Schlittenbahnführung gemäß Fig. 8.

In the following the invention will be explained in more detail with reference to two embodiments, reference being made to the figures. Show it:

• Fig. 1 a partial perspective view of a weft carrier having inner and outer rollers with a cylindrical rolling surface,
• Fig. 2 a partial plan view of the weft carrier according to Fig. 1 .
• Fig. 3 the sectional view taken along line III-III in Fig. 2 .
• Fig. 4 a side view of an inner or outer roller of Fig. 1 .
• Fig. 5 the sectional view along line VV in Fig. 4 .
• Fig. 6 a plan view of the role according to Fig. 4 .
• Fig. 7 a perspective view of a carriage of the carriage track guide according to Fig. 1 .
• Fig. 8 a partial perspective view of a weft carrier having inner and outer rollers with a curved rolling surface,
• Fig. 9 a sectional view of the weft thread carrier according to Fig. 8 according to line III-III in Fig. 2 .
• Fig. 10 a plan view of an inner or outer roller of Fig. 8 .
• Fig. 11 the sectional view according to line XI-XI in Fig. 10 .
• Fig. 12 a perspective view of a carriage of the carriage track guide according to Fig. 8 ,

Fig. 1 shows a weft yarn carrier 2, which is part of a central unit, not shown, also referred to as braiding a braiding machine. The weft carrier 2 has a support plate 4 on which a set of outer rollers 6 and a set of inner rollers 8 are mounted. The two sets of rollers extend substantially over the entire circumference of the support plate 4 and are secured by a clamping plate 10 of the support plate 4 thereto. The support plate 4 has eight gap-like recesses 12, which serve to guide the warp threads for shedding above and below the support plate 4. The warp threads are supplied by reel carriers which are fastened substantially vertically movable on a warp thread carrier (not shown) belonging to the central unit and located below the weft thread carrier. A support plate portion between two recesses 12, on which a total of four outer rollers 6 and three inner rollers 8 are arranged, is referred to as a guide unit 14. The weft carrier 2 has a total of eight such guide units 14.

Furthermore, the weft thread carrier 2 has eight bobbin carriers 16 with delivery bobbins 18, of which only one copy is shown for the sake of clarity. The bobbin 16 are each on a carriage 20 (see Fig. 7 ) attached. The respective carriage 20 (only one is shown) is guided by the outer and inner rollers 6, 8 both radially outwardly and radially inwardly and further perpendicular to the support plate 4, as will be described in more detail below. The bobbin 16 has a number of known means for guiding the weft thread, which will not be discussed in detail here and to which, for example, a roller 22 and two further rollers 24 and 26 belong. A thread guide, which is arranged between the rollers 22 and 24 is not shown.

The support plate 4 is rotated by means of a gear shaft, not shown, and five gears 28. Further, the carriages 20 are driven via an inverting gear including a gear 30 fixed to the shaft, a series of gears 32 driven therefrom (of which in FIG Fig. 1 only two are shown) and a respective with the gears 32 cooperating Tooth portion 34 of the bobbin 16 has. In the plan view of the weft carrier 2 in Fig. 2 the gear 30 is not shown for clarity, however, in the sectional view of Fig. 3 ,

In Fig. 4 For example, one of the outer rollers 6 is shown. These are identical to the inner rollers 8. The roller 6 has a cylindrical rolling surface 38 and is therefore referred to below for the sake of simplicity as a "cylindrical roller". The rolling surface 38 is made of a hardened steel. Above the rolling surface 38 is a wear ring 36 made of ceramic, for example. How out Fig. 5 is visible, a roller component 40, which has the rolling surface 38, a shaft 42. The shaft 42, and thus the entire roller component 40 is rotatably supported by a double-row radial needle bearing 44. The needle bearing 44 has needle-shaped rolling elements 46. The needle bearing 44 is sealed and has a lubricant channel 50 and a grease nipple 52 for relubrication.

Below the needle bearing 44, a radial deep groove ball bearing 54 is arranged with a collar 56. The ball bearing 54 is double-sealed by means of seals 58, and its balls 60 are arranged in a cage 62.

The cylindrical roller 6 is mounted with the needle bearing 44 and the ball bearing 54 in the support plate 4, wherein the ball bearing 54 is fixed in the clamping plate 10. The ball bearing 54 serves to absorb the axial load given by the total weight. The weight is composed of the weight of the cylindrical roller 6 and the weight forces of the carriage 20 and the bobbin 16 together with the wound thread material (not shown). In order to avoid overdetermination in the attachment of the cylindrical roller 6 in the support plate 4, the ball bearing 54 can be slightly adjusted in its angle relative to the needle bearing 44.

The roller component 40 has, in an upper, the rolling surface 38 having body portion 63 a cavity 64 around the rotating mass keep as low as possible. In the cavity 64, a clamping screw 66 is arranged, which serves to fasten it by slight overlap with the wear ring 36.

As in particular in Fig. 7 can be seen, the respective carriage 20, which has a curvature of the carriage track guide corresponding curvature in the circumferential direction, an inner surface 68 and an outer surface 70, which are adapted to the rolling surfaces 38, so do not change in the axial direction. Above the surfaces 68, 70, a collar portion 72 is arranged, which projects both radially inwardly and radially outwardly beyond the surfaces 68, 70. Accordingly, below the surfaces 68, 70, a lower collar portion 74 is arranged. The collar portion 74 projects radially inwardly and outwardly beyond the surfaces 68, 70. The carriage 20 has in the collar portion 72 three threaded holes 76 which serve to tighten the coil carrier 16 to the carriage 20. With the upper collar portion 72 of the carriage 20 is located on the wear rings 36 with the total weight described above. The lower collar portion 74 engages below the lower edge of the rolling surface 38 and serves only to secure against axial movement of the carriage 20 upwards in a possible accident.

In all figures, like features are designated by like reference numerals. In particular, in the weft yarn carrier according to Fig. 8 the features that feature with Fig. 1 are the same, provided with the same reference numerals. Essentially, the weft thread carrier designated by the reference numeral 2 'differs Fig. 8 of the weft carrier 2 by having outer rollers 6 'and inner rollers 8' having a concavely curved rolling surface 38 '. A support plate 4 'has in contrast to the support plate 4 no clamping plate. The bobbins 16 are each on a on the rolling surfaces 38 'tuned carriage 20' (see Fig. 12 ) attached. The respective carriage 20 'is guided by the outer and inner rollers 6', 8 'both radially outwardly and radially inwardly and further perpendicular to the support plate 4'. In contrast to the weft carrier 2, the weft wheels 2 and 28 have only the toothed wheels 28 and the gearwheel 30 in the sectional view according to Fig. 9 shown. On the other hand are in Fig. 1 To see holes 78 for the gears 28 and also a bore 80 for the gear shaft, in Fig. 9 represented and designated by the reference numeral 82. Furthermore, in Fig. 8 a Fadenleitschild 85 shown.

In the 10 and 11 For example, one of the outer rollers 6 'is shown. These are identical to the inner rollers 8 '. The curved rolling surface 38 'is also made of a hardened steel. In the following, the roller 6 'is referred to as a "barrel roller" for the sake of simplicity. It has only for manufacturing reasons in the middle of a narrow annular region 84 (see Fig. 8 and 9 ), which is not arched and in Fig. 11 for the sake of simplicity is not shown. The barrel roller 6 'is fixed to a shaft 86 of a non-rotatable roller component 88 in the support plate 4'. At an upper portion of the roller component 88 by means of two radial deep groove ball bearings 92 and 94 a the rolling surface 38 'exhibiting turntable 96 is mounted. The two ball bearings 92, 94 are identical. Their balls 60 are held in a cage 62. The ball bearings 92, 94 are double-sealed by means of two seals 58 and include a lifetime lubrication. The ball bearings 92,94 are pressed into recesses of the turntable 96 and are each with a collar 56 against this. By means of a retaining ring 98 and a locking screw 100, the ball bearings 92, 94 are secured.

As in Fig. 12 As can be seen, the respective carriage 20 ', which has a curvature of the carriage track guide corresponding curvature in the circumferential direction, an inner surface 68' and an outer surface 70 ', which are concavely curved in the axial direction to adapt to the rolling surfaces 38'. The carriage 20 'has three threaded bores 76 on an upper end face, which serve for screwing the bobbin 16 to the carriage 20'. The total weight of the carriage 20 'and the bobbin 16 with bobbin 18 and yarn material and own roll weight are absorbed by the positive engagement between the outer and inner barrel rollers 6', 8 'and the outer surface 70' and the inner surface 68 ', respectively. It can be assumed that in practice in such a form fit the respective Rolling surface 38 'and the outer or inner surface 70', 68 'touch only in two circular contact lines.

LIST OF REFERENCE NUMBERS

2,2 ' Weft carrier 56 Bunch of ball bearings 4,4 ' support plate 58 Seal the ball bearings 6.6 ' outer rollers 60 Balls of ball bearings 8,8 ' inner rollers 62 Cage of ball bearings 10 clamp 63 Hull section of cylindrical roller 12 recesses 64 cavity 14 Guide unit 66 clamping screw 16 coil carrier 68.68 ' Inner surface of the carriages 18 supply packages 70.70 ' Outside surface of the carriages 20.20 ' carriage 72 upper collar section 22 Role of bobbins 74 lower collar section 24 Role of bobbins 76 threaded holes 26 Role of bobbins 78 Holes for gears 28 gears 80 Bore for gear shaft 30 gear 82 gear shaft 32 gears 83 axis of rotation 34 tooth portion 84 not curved area of 38 ' 36 wear ring 85 Fadenleitschild 38.38 ' rolling surface 86 Shaft of barrel roll 40 rotatable roller component 88 non-rotatable roller component 42 Shaft of cylindrical roller 92 Radial ball bearings 44 double row radial needle bearing 94 Radial ball bearings 46 acicular rolling elements 96 Turntable of barrel roll 50 lubricant channel 98 circlip 52 grease nipple 100 locking screw 54 Radial ball bearings

Claims (11)

Circular slide track guide for a braiding machine having at least two delivery spool carrier sets, wherein the spool carrier sets perform a relative movement to one another about an axis of rotation (83) of the machine and the spool carriers (16) of one of the spool carrier sets are guided by the slide track guide,
wherein the carriage track guide for each bobbin (16) for its attachment has a carriage (20; 20 ') and
the carriage track guide for externally radially guiding the carriages (20; 20 ') comprises a set of external rollers (6; 6') fixed to a support plate (4; 4 ') of the carriage track guide such that the respective carriage (20; 20 ') with an outer surface (70; 70') on a by means of at least one roller bearing (44,54; 92,94) rotatably mounted surface (38; 38 ') of the outer roller (6; 6') is unrolled,
characterized in that the carriage track guide for internally radially guiding the carriages (20, 20 ') comprises a set of inner rollers (8, 8') fixed to the support plate (4, 4 ') such that the respective carriage (20 20 ') with an inner surface (68; 68') on a by means of at least one roller bearing (44,54; 92,94) rotatably mounted surface (38; 38 ') of the inner roller (8; 8') is unrolled,
and that the weight of the carriage (20; 20 ') and of the bobbin (16) fastened by the latter is taken up via at least one of the roller bearings (44,54; 92,94). Carriage track guide according to claim 1,
characterized in that the surface (38) of the rollers of at least one of the roller sets (6,8) is cylindrical and these rollers (6,8) have a wear ring (36) disposed at an upper end such that a collar portion (72) of the respective carriage (20) with its own and the weight of the bobbin (16) is thereon, when the carriage (20) on the roller (6,8) unrolls. Carriage track guide according to claim 2,
characterized in that the wear ring (36) by means of a clamping screw (66) is attached. Carriage track guide according to claim 2 or 3,
characterized in that the wear ring (36) is made of ceramic. Carriage track guide according to claim 1,
characterized in that the weight of the carriage (20 ') and the bobbin (16) by positive engagement between the inner or outer surface (68', 70 ') of the carriage (20') and the roller surface (38 ') on the inner or outer rollers (8 ', 6') is transmitted. Carriage track guide according to claim 5,
characterized in that the surface (38 ') of the rollers of at least one of the roller sets (6', 8 ') is convexly curved and the associated carriage surface (70', 68 ') rolling thereon is concave, or that the roller surface is concave and Carriage surface is convexly curved. Carriage track guide according to one of the preceding claims,
characterized in that one or more of the roller bearings comprises at least one radial deep groove ball bearing (54; 92,94) which substantially receives the weight of the carriage (20; 20 ') and the bobbin (16). Carriage track guide according to claim 7,
characterized in that the radial deep groove ball bearing is a double sealed ball bearing (54; 92,94). Carriage track guide according to claim 7 or 8,
characterized in that one or more of the rolling bearing (54) additionally comprises or have at least one radial needle bearing (44). Carriage track guide according to one of the preceding claims,
characterized in that the roller component (40; 88) which has the surface (38; 38 ') on which the carriage (20; 20') can be unrolled is rotatably supported relative to the support plate (4) and has a cavity inside (64). Braiding machine with at least two delivery spool carrier sets which execute a relative movement relative to one another during braiding about an axis of rotation of the machine, wherein the spool carriers (16) of one of the spool carrier sets are guided by a circular slide track guide according to one of claims 1 to 10.

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