CN118692749A - Concentric cable stranding machine - Google Patents

Abstract

The application discloses a concentric cable stranding machine, which comprises at least one stranding module; the stranding module comprises a frame, a main shaft, at least one pair of storage reels and at least one flying wing tension control mechanism; the flying wing tension control mechanism is fixedly arranged on the main shaft and is positioned between a pair of corresponding wire storage reels; the storage reels are arranged on the main shaft through corresponding clutch mechanisms, and the two storage reels of each pair are suitable for alternately paying off to the flying wing tension control mechanism; when one of the wire storage reels pays out, the other wire storage reel is driven by the clutch mechanism to be separated from the main shaft and synchronously rotate, so that the wire storage reels reversely rotate and are wound again. The application has the beneficial effects that: setting two wire storage reels to alternate directions, and when one wire storage reel pays out, separating the other wire storage reel and driving the other wire storage reel to reversely rotate through a corresponding mechanism to rewind wires; therefore, the downtime of the stranding machine can be effectively reduced, and the production efficiency of the stranding machine is improved.

Description

Concentric cable stranding machine

Technical Field

The application relates to the technical field of stranded wire equipment, in particular to a concentric type cable stranding machine.

Background

The concentric strander is a non-withdrawal twisting machine, a plurality of pairs of wire storage reels are arranged on a main shaft at intervals, and an all-wing tension controller is arranged between two wire storage reels of each pair to control the tension of a cable. A plurality of wires are rewound into the storage wire coil simultaneously, and the wires are discharged through the flying wing simultaneously after rewinding is completed.

However, when the existing concentric strander performs compound wire after completing stranded wire, the existing concentric strander always needs to stop and then can continue to operate by re-winding the wire storage disc, and the existing concentric strander still needs to stop although the existing concentric strander does not need to be used for winding and unwinding. The time required for re-winding of the strander is generally relatively long, which will affect the production efficiency of the strander.

Disclosure of Invention

It is an object of the present application to provide a concentric cable strander that overcomes at least one of the above-mentioned drawbacks of the prior art.

In order to achieve at least one of the above objects, the present application adopts the following technical scheme: a concentric cable stranding machine comprising at least one stranding module; the stranding module comprises a frame, a main shaft, at least one pair of storage reels and at least one flying wing tension control mechanism; the main shaft is rotatably arranged on the frame and rotates; the flying wing tension control mechanism is fixedly arranged on the main shaft and is positioned between a pair of corresponding wire storage reels; the storage reels are arranged on the main shafts through corresponding clutch mechanisms, the storage reels are suitable for synchronously rotating along with the main shafts and paying off to the flying wing tension control mechanisms, and two storage reels of each pair are suitable for alternately paying off; when one of the wire storage reels is paid out, the other wire storage reel is driven by the clutch mechanism to be separated from the main shaft and synchronously rotate, so that the wire storage reels reversely rotate and are wound again.

Preferably, the clutch mechanism comprises a clutch sleeve, a traction assembly and a brake assembly; the clutch sleeve is slidably arranged on the main shaft and is in spline connection, and the storage wire disc is rotatably arranged on the main shaft and is in spline connection with the clutch sleeve, so that the storage wire disc is in synchronous rotation connection with the main shaft through the clutch sleeve; the traction assembly is arranged on the frame and matched with the clutch sleeve, so that the clutch sleeve is driven by the traction assembly to axially move along the main shaft, and the storage wire disc is separated from or kept connected with the main shaft; the braking component is installed in the frame and is suitable for being in braking fit with the wire storage disc separated from the main shaft.

Preferably, the traction assembly comprises a connecting sleeve, a traction frame and a first telescopic device; the clutch sleeve is elastically and slidably arranged on the main shaft, and the connecting sleeve is rotatably arranged on the clutch sleeve; the traction frame is rotatably arranged on the frame through a rotary groove with a strip-shaped middle part; one end of the traction frame is hinged with the connecting sleeve, and the other end of the traction frame is provided with a strip-shaped traction groove; the first telescopic device is arranged on the frame, the output end of the first telescopic device is hinged with the traction groove through a traction plate, so that the traction frame is driven by the first telescopic device to rotate around the rotation groove, and the connecting sleeve is pulled to drive the clutch sleeve to axially reciprocate along the main shaft.

Preferably, the wire storage reel is directly used for winding wires; the brake assembly comprises a second telescopic device and a rotating device; the second telescopic device is fixedly arranged on the frame, the rotating device is arranged at the output end of the second telescopic device, so that the rotating device is driven by the second telescopic device to approach and be attached to the side part of the storage wire coil, and the storage wire coil which is separated from the main shaft for transmission is reversely rotated under the friction transmission of the rotating device.

Preferably, the wire storage disc is rotatably provided with a plurality of wire storage boxes along the circumferential direction, and the wire storage boxes are suitable for paying off the flying wing tension control mechanism; the braking component is suitable for braking the wire storage disc separated from the main shaft; the stranding module further comprises a reversing mechanism arranged on the wire storage disc; the reversing mechanism is suitable for connecting the main shaft with the wire storage box in a transmission way after the wire storage disc is separated from the main shaft, so that the wire storage box can reversely rotate.

Preferably, at least one side of the wire storage box is provided with a coaxial first friction wheel; the reversing mechanism comprises a rotating device, a rotating sleeve, a plurality of transmission gear trains and a plurality of second friction wheels; the rotating device is fixedly arranged on the storage wire disc, and the rotating sleeve is concentrically arranged on one side of the storage wire disc in a rotating way and meshed with the output end of the rotating device; the transmission gear trains are arranged on one side of the wire storage disc and correspond to the wire storage boxes along the circumferential direction, the input ends of the transmission gear trains are meshed with the clutch sleeve or the main shaft, and the output ends of the transmission gear trains are spaced from the first friction wheels corresponding to the wire storage boxes; the second friction wheel is rotatably arranged on a sliding block, the sliding block is slidably arranged on one side of the storage wire disc along the direction of the output end of the transmission gear train and the perpendicular bisector of the first friction wheel, and the sliding block is hinged with the rotating sleeve through a hinge plate; when the storage wire disc and the main shaft synchronously rotate, the second friction wheel is far away from the first friction wheel; when the wire storage disc is separated from the main shaft and the wire storage box is reversely wound, the rotating sleeve is driven by the rotating device to rotate, and then the hinged plate drives the second friction wheel to slide until the second friction wheel is in friction fit with the output end of the transmission gear train and the first friction wheel respectively.

Preferably, at least one side of the storage reel is provided with an extension part; the transmission gear train is suitable for being meshed with the clutch sleeve or the main shaft through the extension part in a radial direction; the brake assembly comprises a second telescopic device and a brake block, the second telescopic device is installed on the frame, the brake block is installed at the output end of the second telescopic device, so that the brake block is driven by the second telescopic device to be close to and attached to the extension portion, and further the storage wire disc separated from the main shaft is braked.

Preferably, a wire guide disc is mounted at the end part of the main shaft, and a plurality of through grooves are formed in the main shaft at the mounting position of the flying wing tension control mechanism along the circumferential direction; the flying wing tension control mechanism comprises a wheel body and a plurality of tension control components; the wheel body is fixedly provided with the main shaft and penetrates through the penetrating groove through a guide part which is arranged in an inward extending mode so as to extend into the main shaft, and therefore wires which are paid out by the wire storage disc extend into the wire storage disc through the guide part in the main shaft; the tension control assembly is arranged on the side part of the wheel body at equal intervals along the circumferential direction, and is suitable for tensioning the wires which are paid out by the wire storage disc.

Preferably, the tension control assembly comprises a support frame, a third guide wheel, a tension wheel and an elastic assembly; the support frame is fixedly arranged on the wheel body, and the third guide wheel is rotatably arranged on the top of the support frame; the tension wheel is rotatably arranged on the sliding seat, and the sliding seat and the supporting frame are slidably arranged; the wire sequentially passes through the third guide wheel and the tension wheel and extends to the guide part; the elastic component is matched with the sliding seat, and the elastic component is suitable for driving the tension wheel to move when the tension of the wire changes so as to keep the tension of the wire.

Preferably, the elastic component comprises a pull rope, a slide bar, a first elastic piece and a second elastic piece; the sliding rod is arranged on the supporting frame in a flush sliding mode along the moving direction of the tension wheel, and the first elastic piece is arranged on the sliding rod so that the sliding rod is elastically connected with the supporting frame in a sliding mode; one end of the second elastic piece is hinged with the supporting frame, the other end of the second elastic piece is connected with the sliding rod through the pull rope, and an included angle between the extending direction of the second elastic piece and the axial direction of the sliding rod is 90-150 degrees; the pull rope passes through the sliding seat so that the tension wheel slides under the traction of the pull rope.

Preferably, the supporting frame is fixedly provided with clamping blocks at the equal-height positions of the tension wheels; and when the tension pulley moves to the limit position, the tension pulley is suitable for being abutted against the clamping block, so that a loose wire is clamped between the tension pulley and the clamping block.

Compared with the prior art, the application has the beneficial effects that:

A pair of wire storage reels are symmetrically arranged at the front position of each flying wing tension control mechanism, so that when one of the wire storage reels is paid out, the other wire storage reel can be separated and is driven to reversely rotate by the corresponding mechanism to perform re-winding; therefore, the downtime of the stranding machine can be effectively reduced, and the production efficiency of the stranding machine is improved.

Drawings

Fig. 1 is a schematic diagram of the overall structure of the present application.

Fig. 2 is a schematic axial side structure of one of the stranding modules of the present application.

Fig. 3 is a schematic side view of the stranding module of fig. 2 according to the present application.

Fig. 4 is a schematic view showing a partial structure of the twisting module shown in fig. 2 in which a wire is changed according to the present application.

Fig. 5 is a schematic structural view of a spindle according to the present application.

Fig. 6 is a schematic structural diagram of a wire storage reel according to the present application.

Fig. 7 is a schematic view showing an exploded state of the clutch mechanism in the present application.

Fig. 8 is a schematic view showing a partial state when the wire storage reel is connected with the spindle in the present application.

Fig. 9 is a schematic diagram showing a partial state when the wire storage reel is disconnected from the spindle in the present application.

Fig. 10 is a schematic view showing a partial state of the wire storage reel and the spindle in preparation for connection according to the present application.

Fig. 11 is a schematic view of a partial sectional structure of a wire storage reel connected to and disconnected from a spindle under the driving of a clutch mechanism in the present application.

Fig. 12 is a schematic structural view of the reversing mechanism in the present application.

Fig. 13 is a schematic view showing a partial state of the wire storage box of the present application when the wire storage box is driven by the reversing mechanism.

FIG. 14 is a schematic view of the configuration of the wing tension control mechanism of the present application.

Fig. 15 is a schematic view of a partially cut-away configuration of a fly wheel according to the present application.

Fig. 16 is a schematic view of a tension control assembly according to the present application.

Fig. 17 is a schematic view showing a state in which tension control is performed by the tension control assembly according to the present application.

Fig. 18 is a schematic diagram showing a state that the tension control assembly clamps a wire according to the present application.

In the figure: twisting module 1, frame 100, mounting frame 110, support pin 1101, guide slot 1102, transmission 11, first rotating means 111, main shaft 112, first bore 1120, outer gear ring 1121, through slot 1122, baffle 1123, wire reel 113, wire hole 1130, wire reel 12, disc 121, second bore 1210, inner gear ring 1211, extension 1212, clearance slot 1213, positioning wheel 1214, first slide slot 1215, wire storage box 122, first friction wheel 1221, first guide wheel 123, clutch mechanism 13, clutch sleeve 131, connecting slot 1310, outer gear 1311, inner gear 1312, guide rod 1313, first spring 132, pulling assembly 133, connecting sleeve 1331, pulling frame 1332, rotary slot 1333, pulling slot 1334, pulling plate 1335, first telescoping device 1336 brake assembly 134, second telescoping device 1341, connection 1342, brake block 1343, flying wing tension control mechanism 14, wheel body 141, guide 1410, second guide pulley 1411, tension control assembly 142, second runner 1420, support frame 1421, third guide pulley 1422, tension pulley 1423, traction pulley 1424, clamp block 1425, elastic assembly 143, pull cord 1431, slide bar 1432, second spring 1433, third spring 1434, connection block 1435, hinge base 1436, reversing mechanism 15, second rotating device 151, first gear 1511, swivel 152, rack segment 1521, hinge plate 1522, drive train 153, second gear 1531, third gear 1532, fourth gear 1533, second friction pulley 154, cable 200, center line 210, wire 220, and winding device 300.

Detailed Description

The present application will be further described with reference to the following specific embodiments, and it should be noted that, on the premise of no conflict, new embodiments may be formed by any combination of the embodiments or technical features described below.

In the description of the present application, it should be noted that, for the azimuth words such as terms "center", "lateral", "longitudinal", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", etc., the azimuth and positional relationships are based on the azimuth or positional relationships shown in the drawings, it is merely for convenience of describing the present application and simplifying the description, and it is not to be construed as limiting the specific scope of protection of the present application that the device or element referred to must have a specific azimuth configuration and operation.

It should be noted that the terms "first," "second," and the like in the description and in the claims are used for distinguishing between similar objects and not necessarily for describing a particular sequential or chronological order.

The terms "comprises" and "comprising," along with any variations thereof, in the description and claims of the present application are intended to cover a non-exclusive inclusion, such that a process, method, system, article, or apparatus that comprises a list of steps or elements is not necessarily limited to those steps or elements that are expressly listed or inherent to such process, method, article, or apparatus.

One preferred embodiment of the present application, as shown in fig. 1 to 3, is a concentric type cable twisting machine comprising at least one twisting module 1 and a winding device 300; the stranding module 1 may twist the conductors 220 and about the centerline 210 to form a desired cable 200. The winding device 300 is used for winding the twisted cable 200 and improving the tension required for twisting the wires 220. The specific structure of the centerline 210, the wire 220, and the winding device 300 are well known to those skilled in the art, and will not be described in detail herein. The particular number of stranding modules 1 is related to the number of layers of stranding required for cable 200; in one specific example, as shown in fig. 1, the cable 200 needs to be stranded with three layers, and the number of stranded modules 1 is three and sequentially arranged from front to back, and the winding device 300 is spaced from the last stranded module 1. The center line 210 may pass through all of the twisting modules 1, and the twisting modules 1 twist the wires 220 of the first to third layers onto the center line 210 in order from front to back, thereby obtaining the desired cable 200. For ease of understanding, a specific structural description will be made below by way of one of the stranding modules 1.

In this embodiment, as shown in fig. 2-4, the stranding module 1 includes a frame 100, a transmission mechanism 11, at least one pair of storage reels 12, and at least one flying wing tension control mechanism 14. The transmission mechanism 11 includes a main shaft 112 and a first rotation device 111; the main shaft 112 may be rotatably mounted on the frame 100, and the first rotating device 111 is fixedly mounted on the frame 100 and is in transmission connection with the main shaft 112 through an output end, so that the main shaft 112 is driven to rotate by the first rotating device 111. The first rotating device 111 and the main shaft 112 have various transmission structures, such as gear transmission, belt transmission, chain transmission and the like; since the overall weight of the twisting module 1 is relatively large, it is not suitable to perform rigid actuation of the main shaft 112, and therefore, it is preferable to use a belt drive for the drive structure of the main shaft 112. The specific structure and working principle of the first rotating device 111 are known to those skilled in the art, and a motor is common, and specific power can be selected according to actual needs. The flying wing tension control mechanism 14 and the storage reel 12 are both mounted on the main shaft 112; wherein the flying wing tension control mechanism 14 is fixedly mounted on the main shaft 112 and is positioned between a corresponding pair of storage reels 12; the storage reel 12 may be mounted to the main shaft 112 by a corresponding clutch mechanism 13. In the continuous twisting operation of the twisting module 1, the wire reels 12 may be rotated synchronously with the main shaft 112 and paid out to the flying wing tension control mechanism 14, and the two wire reels 12 of each pair may be alternately paid out. When one of the reels 12 pays out, it is indicated that the other of the reels 12 has completed the entire payoff, and at this time, the other of the reels 12 may be rotated out of synchronization with the main shaft 112 by the driving of the clutch mechanism 13, so that the reels 12 may be rewound by rotating in the opposite direction. Thus, when the working storage reel 12 also completes all paying-off, the wires 220 in the storage reel 12 which has completed winding again can be directly connected with the flying wing tension control mechanism 14 after the strander stops, and then the strander can be restarted for continuous working. Compared with the traditional shutdown winding mode, the application can greatly shorten the shutdown time of the stranding machine, thereby effectively improving the working efficiency of the stranding machine.

It will be appreciated that the conventional strander works in the following manner: twisting, stopping, winding, wiring and twisting; after the technical scheme of the application is adopted, the working mode of the stranding machine is as follows: twisting (synchronous winding) -stopping-wiring-twisting (synchronous winding). Compared with the traditional mode, the application can reduce the time of one winding process, thereby effectively shortening the downtime of the stranding machine and improving the production efficiency of the stranding machine.

It should be noted that the specific number of reels 12 is related to the number of wires 220 required for twisting the cable 200, and if the number of wires 220 required for twisting the cable 200 in a single layer is large, the number of wires 220 paid out on one reel 12 cannot satisfy the number of wires 220 required for twisting the cable in a single layer, and thus a plurality of reels 12 are required to maintain the number of wires 220. Correspondingly, a plurality of flying wing tension control mechanisms 14 are required to be arranged; while the wire reels 12 of the present embodiment are used in pairs, the number of pairs required for the wire reels 12 may be determined by the number of wires 220 required for single layer twisting of the cable 200.

In this embodiment, the clutch mechanism 13 capable of achieving the above-mentioned functions has various specific structures, one of which is shown in fig. 5 to 11, and the main shaft 112 is provided with the outer gear ring 1121 at the corresponding mounting position of the wire storage reel 12. Clutch mechanism 13 includes clutch sleeve 131, traction assembly 133, and brake assembly 134. The clutch sleeve 131 is slidably mounted on the main shaft 112 and is engaged with the outer gear ring 1121 on the main shaft 112 through inner gear teeth 1312 disposed on the inner side to form an axial spline connection, so that the clutch sleeve 131 can synchronously rotate with the main shaft 112 and simultaneously can also reciprocate along the axial direction of the main shaft 112. The storage reel 12 is rotatably mounted to the main shaft 112 through a central second bore 1210; meanwhile, the second inner hole 1210 can also be meshed with the outer gear 1311 arranged on the outer side of the clutch sleeve 131 through the inner gear 1211 arranged on the side wall so as to form axial spline connection. A traction assembly 133 is mounted to the frame 100 and cooperates with the clutch collar 131, and a brake assembly 134 is mounted to the frame 100 for cooperation with the storage reel 12.

When the wire storage disc 12 performs a paying-off operation, the clutch sleeve 131 is kept engaged with the inner gear ring 1211 of the inner hole of the wire storage disc 12, so that the wire storage disc 12 can rotate synchronously with the main shaft 112 through the clutch sleeve 131, and accordingly relative rest with the flying wing tension control mechanism 14 along the circumferential direction is realized for paying-off. When the wire storage reel 12 finishes all paying-off and needs to be wound again, the traction assembly 133 can drive the clutch sleeve 131 to slide axially along the main shaft 112 in a direction away from the wire storage reel 12 until the outer gear teeth 1311 of the clutch sleeve 131 are disengaged from the inner gear ring 1211 on the inner hole side wall of the wire storage reel 12, and at this time, the wire storage reel 12 is in a state of being disengaged from the main shaft 112, but the corresponding other wire storage reel 12 is in a paying-off state. The take-up reel 12 off of the spindle 112 may then be braked by the brake assembly 134 so that the take-up reel 12 in the off state may be rotated in the reverse direction to effect re-winding.

It should be noted that, assuming that the wire storage reel 12 is in a forward rotation state during the wire releasing, the wire storage reel 12 needs to be driven to rotate in a reverse direction during the wire rewinding so that the rewound wire 220 can be smoothly released during the forward rotation of the subsequent wire storage reel 12.

In particular, there are various specific structures of the traction assembly 133 capable of achieving the above functions, and a detailed description will be made below with one of the structures for convenience of understanding. As shown in fig. 7to 11, the clutch sleeve 131 is elastically slidably mounted to the main shaft 112, and a connection groove 1310 is provided at one side of the clutch sleeve 131 in a circumferential direction. The traction assembly 133 is mounted to the mounting bracket 110 on the frame 100 such that the traction assembly 133 is at the same height as the clutch pack 131. The pulling assembly 133 comprises a connecting sleeve 1331, a pulling frame 1332 and a first telescopic device 1336. The connecting sleeve 1331 may be rotatably coupled to the connecting groove 1310 of the clutch sleeve 131 by means of bearing engagement. The traction frame 1332 is in rotary fit with the supporting pin 1101 on the mounting frame 110 through a rotary groove 1333 with a strip-shaped middle part; one end of the traction frame 1332 is hinged with the connecting sleeve 1331, and a strip-shaped traction groove 1334 is formed in the other end of the traction frame 1332. The first telescoping device 1336 is installed on the frame 100, and the output end of the first telescoping device 1336 is hinged to the traction groove 1334 through a traction plate 1335, so that the traction frame 1332 rotates around the groove 1333 under the driving of the first telescoping device 1336, and the traction connecting sleeve 1331 drives the clutch sleeve 131 to axially reciprocate along the main shaft 112.

It should be appreciated that there are a variety of specific resilient sliding mounting means for clutch sleeve 131; for ease of understanding, as shown in fig. 5, 7 and 11, a radially extending baffle 1123 is provided on the main shaft 112, and a plurality of guide rods 1313, such as four guide rods 1313, are provided on the end surface of the clutch sleeve 131 remote from the storage reel 12 at equal intervals in the circumferential direction. The guide rod 1313 can slide through the baffle 1123 on the main shaft 112, and the guide rods 1313 are sleeved with the first springs 132, and two ends of the first springs 132 respectively abut against the baffle 1123 and the end face of the clutch sleeve 131, so that the clutch sleeve 131 and the main shaft 112 are elastically and slidably mounted.

In order to ensure traction stability of the clutch cover 131, at least two hinge points of the traction frame 1332 and the connecting sleeve 1331, a plurality of hinge points may be connected to intersect at a center point of the connecting sleeve 1331. For example, as shown in fig. 7, the connecting end of the traction frame 1332 has a U shape, so that the traction frame 1332 can be hinged with a hinge rod arranged at the upper and lower limit height positions of the connecting sleeve 1331, thereby ensuring that the traction frame 1332 drives the upper and lower ends of the connecting sleeve 1331 simultaneously when rotating so as to improve traction stability. Meanwhile, since the connecting sleeve 1331 is always kept stationary in the circumferential direction, and the clutch sleeve 131 is always rotated together with the main shaft 112, in order to reduce friction between the connecting sleeve 1331 and the clutch sleeve 131, the connecting sleeve 1331 and the connecting groove 1310 may be engaged by a bearing or a ball so that sliding friction is changed into rolling friction to reduce wear.

It should also be appreciated that, since the movement of the clutch sleeve 131 is along the axial direction of the main shaft 112, i.e., the movement path of the clutch sleeve 131 is a straight line; while the traction frame 1332 rotates around the supporting pin 1101, namely, the moving path is arc-shaped; in order to ensure that the operation between the traction frame 1332 and the clutch cover 131 is not interfered, it is necessary to arrange the rotating groove 1333 in a bar shape so that the track difference between the traction frame 1332 and the clutch cover 131 can be compensated by the sliding of the rotating groove 1333 with respect to the support pin 1101 while the traction frame 1332 rotates around the support pin 1101.

It can be appreciated that, as clutch sleeve 131 engages with inner gear ring 1211 of the inner bore of wire storage reel 12 via outer gear teeth 1311; when the clutch sleeve 131 needs to be in transmission connection with the wire storage reel 12 again, the gear teeth and the gaps of the outer gear teeth 1311 and the inner gear ring 1211 may not correspond, and therefore reset of the clutch sleeve 131 may be interfered. In this embodiment, the clutch sleeve 131 is elastically slidably connected to the main shaft 112, and the traction frame 1332 and the traction plate 1335 are hinged through a bar-shaped traction groove 1334. When the outer gear 1311 does not correspond to the gear teeth and the gap of the inner gear 1211, the first telescoping device 1336 may be reset to a state close to the initial position by sliding the traction plate 1335 relative to the traction groove 1334, and then the clutch sleeve 131 may be reset under the elastic force of the first spring 132 to realize the reconnection of the clutch sleeve 131 and the storage wire disc 12 as the main shaft 112 rotates relative to the storage wire disc 12 so that the gear teeth and the gap of the outer gear 1311 and the inner gear 1211 correspond to each other, at this time, the traction frame 1332 rotates around the supporting pin 1101, and the traction plate 1335 may slide along the traction groove 1334 again to avoid interference. To ensure that the elastic force of the first spring 132 is sufficient, the first spring 132 may employ rectangular elasticity. The specific structure and operation of the first telescoping device 1336 are well known to those skilled in the art, and therefore, not described in detail herein, a cylinder or a hydraulic cylinder may be used for the common first telescoping device 1336.

For ease of understanding, the detailed operation of the pulling assembly 133 will be described in conjunction with the drawings.

Initially, as shown in fig. 8 and 11 (1), clutch sleeve 131 is engaged with inner ring gear 1211 of wire storage reel 12 by outer gear teeth 1311. Meanwhile, the traction frame 1332 can be in a state of being vertical to the axial direction of the main shaft 112 and is kept connected with the connecting sleeve 1331; the rotary slot 1333 may correspond to the support pin 1101 through a middle portion or an end remote from the clutch sleeve 131; the traction plate 1335 corresponds to one end of the traction groove 1334 close to the clutch sleeve 131, and the first telescopic device 1336 is close to the clutch sleeve 131, so that the traction plate 1335 inclines towards the direction away from the clutch sleeve 131 to avoid dead points. Meanwhile, the first spring 132 may be in a natural state or an elastically deformed state.

When the storage reel 12 needs to be separated from the main shaft 112, as shown in fig. 9 and fig. 11 (2), the first telescoping device 1336 may drive the traction plate 1335 to extend, so that the traction plate 1335 may slide along the traction groove 1334 to the end of the corresponding traction groove 1334 far away from the clutch sleeve 131, and then the traction plate 1335 abuts against the traction groove 1334 to drive the traction frame 1332 to rotate around the supporting pin 1101 and correspondingly slide relatively, so that the clutch sleeve 131 slides axially in a direction far away from the storage reel 12 under the driving of the connecting sleeve 1331 until the outer gear teeth 1311 are disengaged from the inner gear ring 1211; at this point, the spool 12 is disengaged from the spindle 112 and the first spring 132 is in a resiliently compressed state.

When the spool 12 is finished with re-winding and ready to be connected to the main shaft 112 again, as shown in fig. 10, the first telescopic device 1336 can drive the drawing plate 1335 to retract, so that the drawing plate 1335 can slide along the drawing groove 1334 to a position close to one end of the clutch sleeve 131. In this process, if the outer gear 1311 exactly corresponds to the inner gear 1211, the clutch sleeve 131 may return to the engaged state of the outer gear 1311 and the inner gear 1211 under the elastic force of the first spring 132. In this process, if the outer gear 1311 does not correspond to the inner gear 1211, the first telescoping device 1336 may remain stationary when the traction plate 1335 corresponds to the end of the traction groove 1334 near the clutch sleeve 131, until the wire storage reel 12 rotates relative to the main shaft 112 until the outer gear 1311 corresponds to the inner gear 1211, the clutch sleeve 131 may be restored to the engaged state of the outer gear 1311 and the inner gear 1211 under the elastic force of the first spring 132, and meanwhile, the first telescoping device 1336 may also be restored to the initial position. In general, in the process that the first telescoping device 1336 drives the traction plate 1335 to move along the end, away from the clutch sleeve 131, of the traction groove 1334 to the end, close to the clutch sleeve 131, of the storage reel 12 and the main shaft 112 to perform a certain angle of relative movement, in this process, the outer gear teeth 1311 and the inner gear ring 1211 can be basically exactly corresponding to each other, so that the clutch sleeve 131 can be meshed with the inner gear ring 1211 again under the elastic force of the first spring 132, and the reset driving of the first telescoping device 1336 can ensure that the clutch sleeve 131 can be reset to the initial position.

It should be appreciated by those skilled in the art that the winding manner of the wire storage reel 12 is different for different application scenarios; when the number of wires 220 required for single-layer twisting of the cable 200 is small, the wire storage reel 12 may directly perform wire winding through the reel body 121; when the number of wires 220 required for single-layer twisting of the cable 200 is large, a plurality of wire storage boxes 122 may be provided on the tray body 121 of the wire storage reel 12, and each wire storage box 122 may be wound. The following will describe in detail specific examples for different application scenarios.

Example one: the winding is directly performed on the wire storage reel 12 through the reel body 121.

The specific structure of the disc 121 is well known in the art, and mainly includes a winding post and a wire blocking plate located at two ends of the winding post, where the wire storage disc 12 can be in running fit with the spindle 112 through the winding post, and the diameter of the wire blocking plate is larger than that of the winding post. For the above scenario, the brake assembly 134 includes a second telescoping device 1341 and a rotating device. The second telescopic device 1341 is fixedly installed on the frame 100, and the rotating device is installed at the output end of the second telescopic device 1341, so that the rotating device can be close to and attached to the side edge of the wire blocking plate of the wire storage reel 12 under the driving of the second telescopic device 1341 and performs friction fit. Through the friction fit of rotary device and storage wire drum 12, can brake storage wire drum 12 to static earlier, then accomplish the butt joint of wire winding with storage wire drum 12 through winding displacement device after, can start rotary device in order to order about storage wire drum 12 to carry out reverse rotation, brake to static again after the completion wire winding of storage wire drum 12, with winding displacement device and storage wire drum 12 separation at last can.

It should be noted that, the specific structure of the wire arranging device is known to those skilled in the art, and when the wire arranging device is mainly used for winding the wire storage reel 12, the wire 220 to be wound can be driven to reciprocate along the axial direction of the wire storage reel 12 while the wire is paid out to the wire storage reel 12, so as to ensure that the wire 220 can be uniformly wound on the winding post of the wire storage reel 12. The specific structure and working principle of the second telescopic device 1341 and the rotating device are known to those skilled in the art, the common second telescopic device 1341 is an air cylinder or a hydraulic cylinder, the common rotating device is a motor, and the motor can be in friction fit with the side edge of the wire baffle of the wire storage reel 12 through a friction wheel installed at the output end.

Example two: a plurality of magazine 122 are provided along the circumferential direction of the disk body 121 for the wire storage disk 12.

As shown in fig. 2,3 and 6, a plurality of wire storage boxes 122 can be rotatably mounted on the disc 121 correspondingly, and pay out the wires to the flying wing tension control mechanism 14 at corresponding positions under the guidance of a first guide wheel 123 arranged on the disc 121. When the storage reel 12 is disengaged from the spindle 112, the brake assembly 134 may brake the storage reel 12 disengaged from the spindle 112. The stranding module 1 further includes a reversing mechanism 15 mounted on the wire storage reel 12, wherein the reversing mechanism 15 can drive the spindle 112 to connect with the wire storage box 122 after the wire storage reel 12 is separated from the spindle 112, so that the wire storage box 122 can reversely rotate relative to the stationary wire storage reel 12 to complete re-winding.

It should be appreciated that the particular number of wire storage boxes 122 may be determined based on the number of wires 220 that are actually stranded; for example, as shown in fig. 6, the number of the wire storage boxes 122 is six, and each wire storage box 122 can be used for paying out a single wire 220 or paying out a complex wire formed by a plurality of wires 220.

Specifically, as shown in fig. 6 to 10, at least one side of the disc 121 is provided with an annular extension 1212, and the extension 1212 is concentric with the second inner hole 1210 of the disc 121. The brake assembly 134 may be mounted to the mounting bracket 110 on the housing 100 such that the brake assembly 134 is flush with the extension 1212. The brake assembly 134 includes a second telescopic device 1341 and a brake block 1343, the second telescopic device 1341 is fixedly mounted on the mounting frame 110, the brake block 1343 is fixedly mounted on a connecting frame 1342 at the output end of the second telescopic device 1341, and the connecting frame 1342 can be slidably matched with a guide slot 1102 on the mounting frame 110 to increase stability. When the storage reel 12 needs to be separated from the main shaft 112, the brake block 1343 can be driven by the second telescopic device 1341 to approach and fit the extension 1212, so as to brake the storage reel 12 separated from the main shaft 112.

It should be noted that, after the storage wire reel 12 is separated from the main shaft 112 by the clutch mechanism 13, the storage wire reel 12 and the main shaft 112 are in running fit through bearings, so that the rotating friction force of the storage wire reel 12 is small, and further the storage wire reel 12 continues to rotate continuously under the condition of large moment of inertia of the storage wire reel 12, so that the braking assembly 134 needs to be provided to rapidly brake the storage wire reel 12 separated from the main shaft 112, so as to rapidly rewind the storage wire box 122 on the storage wire reel 12. And in order to ensure that the brake assembly 134 is stable to the braking of the storage reel 12, a plurality of brake blocks 1343 may be provided, for example, as shown in fig. 7, the number of brake blocks 1343 is two, and two brake blocks 1343 may simultaneously make frictional contact with the extension 1212.

In this example, there are various specific structures of the reversing mechanism 15 capable of effecting the reverse rotation of the magazine 122, and a detailed description will be made below with one of the structures for the sake of easy understanding. As shown in fig. 6, 12 and 13, the extension 1212 is provided with a clearance groove 1213 corresponding to each magazine 122 in the circumferential direction, and the clearance groove 1213 is closer to the disc 121 than the contact position of the brake assembly 134 with the extension 1212, so as to avoid interference between the reversing mechanism 15 and the brake assembly 134. At least one side of the magazine 122 is provided with a coaxially mounted first friction wheel 1221. The reversing mechanism 15 is mounted on the same side as the first friction wheel 1221, and the reversing mechanism 15 includes a second rotating device 151, a rotating sleeve 152, and a plurality of transmission gear trains 153 and a plurality of second friction wheels 154 corresponding to the number of the wire storage boxes 122. The second rotating device 151 is fixedly installed on the wire storage disc 12, and the rotating sleeve 152 is concentrically and rotatably installed on the wire storage disc 12 and is meshed with a first gear 1511 installed at the output end of the second rotating device 151 through a rack segment 1521 arranged on the side edge. Each transmission wheel train 153 is mounted on the wire storage disc 12 and corresponds to each wire storage box 122 along the circumferential direction; the input end of the gear train 153 may be engaged with the clutch sleeve 131 or the main shaft 112 through the space slot 1213, and the output end of the gear train 153 may be spaced from the first friction wheel 1221 coaxially installed with the corresponding wire storage box 122. The second friction wheel 154 is rotatably mounted on a sliding block (not shown), the sliding block can be slidably mounted on a first sliding groove 1215 arranged on the side edge of the disc body 121, and the extending direction of the first sliding groove 1215 is coincident with the direction of a perpendicular bisector of a connecting line between the output end of the transmission gear train 153 and the first friction wheel 1221; the slide and the swivel 152 are hinged by corresponding hinge plates 1522.

When the spool 12 rotates in synchronization with the main shaft 112, the second friction wheel 154 is far from the first friction wheel 1221, so that the magazine 122 can rotate and pay out with the pulling of the wire 220. When the wire storage disc 12 is separated from the main shaft 112 and the reverse winding of the wire storage box 122 is required, the rotating sleeve 152 is driven by the second rotating device 151 to rotate, so that the sliding block can drive the second friction wheel 154 to slide along the connecting line perpendicular bisector between the output end of the transmission gear train 153 and the first friction wheel 1221 under the driving of the hinge plate 1522 until the second friction wheel 154 is simultaneously in friction fit with the first friction wheel 1221 and the output end of the transmission gear train 153, thereby realizing the transmission of the transmission gear train 153 to the first friction wheel 1221 through the second friction wheel 154, and further driving the corresponding wire storage box 122 to reversely rotate to finish the winding.

It will be appreciated that the transmission gear train 153 includes at least one transmission wheel, and the number of gears included in the transmission gear train 153 is required to be an odd number according to the requirement of the reverse rotation of the wire storage box 122 relative to the main shaft 112, so that the rotation direction of the output end of the transmission gear train 153 can be kept opposite to the rotation direction of the main shaft 112, and when the transmission gear train is transmitted to the first friction wheel 1221 through the second friction wheel 154, the first friction wheel 1221 can drive the coaxial wire storage box 122 to reversely rotate relative to the main shaft 112. The specific number of the driving wheels included in the driving wheel train 153 can be determined according to actual needs, such as one, three, five, etc.

It should be noted that, in order to ensure that the second friction wheel 154 can be stably engaged with the first friction wheel 1221 and the output end of the transmission gear train 153, the size of the transmission wheel corresponding to the output end of the transmission gear train 153 needs to be equal to the diameter of the first friction wheel 1221. Because the wire storage box 122 is far away from the main shaft 112, if the transmission wheel train 153 adopts one transmission wheel, the second friction wheel 154 needs a larger size, and is inconvenient to install; therefore, a plurality of driving wheels can be adopted for the driving wheel train 153, so that not only the sizes of the friction wheel and the driving wheels can be reduced, but also the speed ratio between the main shaft 112 and the wire storage box 122 can be increased, so as to accelerate the wire winding efficiency of the wire storage box 122.

For ease of understanding, the following will describe in detail the use of three drive wheels for drive train 153. It is assumed that the input end of the gear train 153 is engaged with the outer gear 1311 of the clutch sleeve 131 through the clearance groove 1213. As shown in fig. 12 and 13, the three driving wheels are a second gear 1531, a third gear 1532, and a fourth gear 1533, respectively; the fourth gear 1533 is close to the clutch sleeve 131 and engaged with the clutch sleeve to serve as an input end of the transmission gear train 153, the third gear 1532 is engaged with the fourth gear 1533, the second gear 1531 is engaged with the third gear 1532, a third friction wheel with the same diameter as the first friction wheel 1221 is coaxially mounted on one side of the second gear 1531 to serve as an output end of the transmission gear train 153, and an extending direction of the first chute 1215 is overlapped with a perpendicular bisector of an axis connecting line of the third friction wheel and the first friction wheel 1221. The second friction wheel 154 may be simultaneously friction fit with the first friction wheel 1221 and the third friction wheel under the urging of the rotating sleeve 152.

When the wire storage boxes 122 are wound, two or more wire storage boxes 122 may be wound in the symmetrical direction at the same time according to the installation position of the wire arranging device; taking six wire storage boxes 122 as an example, assuming that each wire arranging device only performs wire winding on one wire storage box 122, in the stranding and paying-off working time of one wire storage box 122, all wire winding can be completed by three wire winding of the six wire storage boxes 122 on the other wire storage disc 12. The step-up ratio between the first friction wheel 1221 and the main shaft 112 is at least equal to 3, and the step-up ratio between the first friction wheel 1221 and the main shaft 112 is at least greater than 3 in order to allow the reproduction wiring time of the wiring device. Through the transmission gear train 153, the speed increasing ratio between the first friction wheel 1221 and the main shaft 112 is far greater than 3; however, the step-up ratio is not too large, and the too large step-up ratio will cause the rotational speed of the wire storage box 122 to be too fast, so that the winding quality is affected. Generally, the step-up ratio may be set to about 5 to 8.

In this example, the swivel 152 is mounted in a plurality of specific rotational ways, and for ease of understanding, a detailed description will be given below with respect to one of the structures. As shown in fig. 6 and 13, one side of the wire storage reel 12 is provided with a plurality of positioning wheels 1214 in the circumferential direction; the positioning wheel 1214 may be rotatably mounted or may be fixedly mounted, preferably rotatably mounted. Positioning areas can be formed between the positioning wheels 1214, and the rotating sleeve 152 can be installed in the positioning areas to realize concentric rotation installation with the wire storage reel 12. The specific number of the positioning wheels 1214 can be selected according to actual needs, but in order to ensure the formation of the positioning areas, the number of the positioning wheels 1214 is at least three, and the central angle corresponding to the connecting arc length of the three positioning wheels 1214 along the circumferential direction is larger than 180 degrees, so that the rotating sleeve 152 can be stably installed; for example, as shown in fig. 6, the number of positioning wheels 1214 is five.

In this embodiment, as shown in fig. 2,3, 5, 14 and 15, a wire guide plate 113 is mounted on an end of the main shaft 112 remote from the first rotating device 111, and a plurality of wire guide holes 1130 are provided on the wire guide plate 113 at intervals in the circumferential direction. Wires 220 extending from the flying wing tension control mechanism 14 can be stranded through corresponding wire guides 1130 with the centerline 210 passing through the first bore 1120 in the center of the main shaft 112. The wire reel 113 is used to raise the wire 220 to a certain height to ensure that the wire 220 can be stranded at a proper angle with the center line 210. The main shaft 112 is provided with a plurality of through grooves 1122 along the circumferential direction at the mounting position of the flying wing tension control mechanism 14, and the through grooves 1122 can communicate the first inner hole 1120 in the center of the main shaft 112 with the outside. The flying wing tension control mechanism 14 includes a wheel body 141 and a plurality of tension control assemblies 142. The main shaft 112 is fixedly mounted on the wheel body 141, a plurality of guiding parts 1410 extending radially inwards are arranged on the wheel body 141 along the circumferential direction, and the guiding parts 1410 can pass through the through grooves 1122 to extend into the first inner hole 1120 of the main shaft 112, so that the wires 220 paid out by the wire storage disc 12 can extend to the wire guide disc 113 through the guiding parts 1410 in the main shaft 112. The tension control members 142 are installed at equal intervals in the circumferential direction at the sides of the wheel body 141, and the tension control members 142 can tension the wires 220 paid out from the wire storage reel 12.

It should be appreciated that the number and location of guides 1410, tension control assemblies 142, and magazine 122 correspond to one another. In order to ensure smooth guiding of the guide portion 1410 to the wire 220, a second guide wheel 1411 may be installed in the guide portion 1410, and the wire 220 passing through the tension control assembly 142 may extend in the guide portion 1410 in a direction of the wire guide pad 113 through the second guide wheel 1411. By advancing the wire 220 from the inside of the main shaft 112, the twisting safety of the wire 220 can be ensured; that is, the wires 220 are broken in the twisting process, and the broken wires 220 only jump inside the main shaft 112, so that potential safety hazards to external staff are avoided.

In this embodiment, the specific structure of the tension control assembly 142 capable of tensioning the wire 220 is varied, and one of the structures will be described in detail below for the sake of easy understanding. As shown in fig. 14, 16-18, the tension control assembly 142 includes a support frame 1421, a third guide pulley 1422, a tension pulley 1423, and an elastic assembly 143. The supporting frame 1421 is fixedly mounted on the wheel body 141, and the third guide wheel 1422 is rotatably mounted on the top of the supporting frame 1421. The tension pulley 1423 is rotatably mounted on a sliding seat (not shown), and the sliding seat is slidably mounted on a second sliding chute 1420 horizontally disposed on the supporting frame 1421. The wire 220 paid out from the wire spool 12 may sequentially pass through a third guide pulley 1422 and a tension pulley 1423 to reach the guide 1410. The elastic component 143 cooperates with the sliding seat, and the elastic component 143 can drive the tension pulley 1423 to move to maintain the tension of the wire 220 when the tension of the wire 220 changes.

It should be appreciated that in order to ensure that the tension pulley 1423 is able to stably tension the wire 220, the third guide pulley 1422 needs to be offset from the tension pulley 1423 in a horizontal direction. The arrangement of the conductors 220 of the flying wing tension control mechanism 14 during alternate use of the two reels 12 will be described with reference to fig. 3,4 and 17. Two storage reels 12 may be disposed on either side of the fly wing tension control mechanism 14 in the direction shown in fig. 3; the third guide pulley 1422 may be deviated toward the left-hand storage reel 12 with respect to the tension pulley 1423, and the elastic member 143 pulls the tension pulley 1423 rightward. When the left side wire reel 12 is performing a paying-out operation, as shown in fig. 3 and 17, the wire 220 paid out from the wire reel 12 may pass over the upper portion of the third guide pulley 1422 and the tension pulley 1423 to be extended toward the guide 1410. When the right-hand wire reel 12 is paid out, as shown in fig. 4, the wire 220 may be extended from the lower portion to the tension pulley 1423 through the third guide pulley 1422 to the guide 1410.

In this embodiment, the specific structure of the elastic member 143 is various, and for convenience of understanding, a detailed description will be given below with one of the structures. As shown in fig. 16 and 17, the elastic assembly 143 includes a pull cord 1431, a slide bar 1432, a first elastic member, and a second elastic member. The sliding rod 1432 is slidably mounted on the supporting frame 1421 along the moving direction of the tension pulley 1423, and the first elastic member is mounted on the sliding rod 1432, so that the sliding rod 1432 is elastically slidably connected with the supporting frame 1421. One end of the second elastic piece is hinged with the support frame 1421, the other end of the second elastic piece is connected with the slide rod 1432 through a pull rope 1431, and an included angle between the extending direction of the second elastic piece and the axial direction of the slide rod 1432 is 90-150 degrees; the pulling rope 1431 can pull the tension pulley 1423 after passing through the traction pulley 1424 arranged on the sliding seat, so that the tension pulley 1423 slides along the second sliding chute 1420 under the traction of the pulling rope 1431 to realize the tensioning of the lead 220, and the traction pulley 1424 can facilitate the sliding traction of the pulling rope 1431.

It should be noted that, the specific structures of the first elastic member and the second elastic member are various, and there are elastic sheets, springs, etc. in this embodiment, the springs will be described in detail, and the first elastic member is the second spring 1433, and the second elastic member is the third spring 1434. The second spring 1433 may be sleeved on the sliding rod 1432, one end of the third spring 1434 is hinged with the support frame 1421 through a hinged seat 1436 connected, and the other end of the third spring 1434 is connected with the pull rope 1431 through a connecting block 1435. The third spring 1434 may be disposed above the tension pulley 1423, or may be disposed below the tension pulley 1423; if the third spring 1434 is disposed above the tension pulley 1423, the slide bar 1432 will be flush with the lower portion of the traction pulley 1424; if the third spring 1434 is disposed below the tension pulley 1423, the slide bar 1432 will be flush with the upper portion of the traction pulley 1424. For ease of understanding, this embodiment will take the example of the third spring 1434 being disposed below the tension pulley 1423.

It will be appreciated that the hinge point of the third spring 1434 to the support bracket 1421 may be designated as a and the point of connection of the second spring 1433 to the rear end of the slide bar 1432 may be designated as B. The entire elastic assembly 143 may be deformed as a function of the change in length of the line between points A, B during movement of the tension pulley 1423. As the tension of the wire 220 changes, a tension decrease is taken as an example; assuming that the traction wheel 1424 is moved to the right by X distance, as shown in fig. 17, the change in the length of the link between A, B points will be less than X, which results in a greater tension accommodating travel of the resilient assembly 143 of the present embodiment as compared to a conventional single spring construction. And in order to ensure the stress stability of the tension pulley 1423, elastic components 143 may be disposed at both ends of the tension pulley 1423 at the rotational mounting positions.

In this embodiment, as shown in fig. 18, a clamping block 1425 is fixedly mounted on a supporting frame 1421 at the same height as a tension pulley 1423. When the tension pulley 1423 moves to the limit position, the tension pulley 1423 can be abutted against the clamping block 1425, so that the loose wire 220 is clamped between the tension pulley 1423 and the clamping block 1425, wiring of the subsequent wire storage reel 12 in an alternating manner can be facilitated, and meanwhile, the wire 220 can be clamped and protected from being broken suddenly, so that damage caused by flying out of the wire 220 is avoided.

It should be appreciated that when the wire reel 12 completes winding, there will be no contact between the wire 220 and the wire reel 12, and the wire 220 will be in a relaxed state, so the tension pulley 1423 may be driven by the elastic component 143 to slide away from the third guide pulley 1422 or towards the clamping block 1425 until the tension pulley 1423 abuts against the clamping block 1425, which is relatively quick, so the end of the wire 220 that keeps the wire-releasing trend can be rapidly clamped, so as to facilitate the subsequent rewiring when the wire reel 12 is replaced. Meanwhile, when the wire 220 is suddenly broken, the pressure of the wire 220 to the tension pulley 1423 is suddenly lost, and at this time, the tension pulley 1423 can also rapidly approach the clamping block 1425 and clamp the broken wire 220 under the elastic force of the elastic component 143.

It should also be appreciated that for the connection of the conductors 220, there may be continued twisting of the extension cable 200; the end of the wire 220 of the previous wire storage disc 12 can be used for pulling the head end of the wire 220 of the new wire storage disc 12, so that the wire 220 of the new wire storage disc 12 can rapidly pass out from the inside of the main shaft 112 to the position of the wire storage disc 113, and the wire can be threaded from the main shaft 112 again without manual work.

The foregoing has outlined the basic principles, features, and advantages of the present application. It will be understood by those skilled in the art that the present application is not limited to the embodiments described above, and that the above embodiments and descriptions are merely illustrative of the principles of the present application, and various changes and modifications may be made therein without departing from the spirit and scope of the application, which is defined by the appended claims. The scope of the application is defined by the appended claims and equivalents thereof.

Claims (10)

1. A concentric cable stranding machine comprising at least one stranding module, wherein the stranding module comprises:

A frame;

a main shaft; the main shaft is rotatably arranged on the frame and rotates;

At least one flying wing tension control mechanism; the flying wing tension control mechanism is fixedly arranged on the main shaft and is positioned between a pair of corresponding storage reels; and

At least one pair of wire reels; the storage wire disc is arranged on the main shaft through a corresponding clutch mechanism, and is suitable for synchronously rotating along with the main shaft and paying off to the flying wing tension control mechanism;

the two wire storage reels of each pair are suitable for carrying out alternate paying-off; when one of the wire storage reels is paid out, the other wire storage reel is driven by the clutch mechanism to be separated from the main shaft and synchronously rotate, so that the wire storage reels reversely rotate and are wound again.

2. The concentric cable strander of claim 1, wherein the clutch mechanism comprises:

a clutch sleeve; the clutch sleeve is slidably arranged on the main shaft and is in spline connection, and the storage wire disc is rotatably arranged on the main shaft and is in spline connection with the clutch sleeve, so that the storage wire disc is in synchronous rotation connection with the main shaft through the clutch sleeve;

A traction assembly; the traction assembly is arranged on the frame and matched with the clutch sleeve, so that the clutch sleeve is driven by the traction assembly to axially move along the main shaft, and the storage wire disc is separated from or kept connected with the main shaft; and

A brake assembly; the braking component is installed in the frame and is suitable for being in braking fit with the wire storage disc separated from the main shaft.

3. The concentric cable strander of claim 2, wherein the pulling assembly comprises:

Connecting sleeves; the clutch sleeve is elastically and slidably arranged on the main shaft, and the connecting sleeve is rotatably arranged on the clutch sleeve;

A traction frame; the traction frame is rotatably arranged on the frame through a rotary groove with a strip-shaped middle part; one end of the traction frame is hinged with the connecting sleeve, and the other end of the traction frame is provided with a strip-shaped traction groove; and

A first telescopic device; the first telescopic device is arranged on the frame, the output end of the first telescopic device is hinged with the traction groove through a traction plate, so that the traction frame is driven by the first telescopic device to rotate around the rotation groove, and the connecting sleeve is pulled to drive the clutch sleeve to axially reciprocate along the main shaft.

4. A concentric cable twisting machine according to claim 2 or 3, wherein the wire storage reel is directly used for winding of wires; the brake assembly includes:

a second telescopic device; the second telescopic device is fixedly arranged on the frame; and

A rotating device; the rotating device is arranged at the output end of the second telescopic device, so that the rotating device is driven by the second telescopic device to approach and be attached to the side part of the storage wire disc, and the storage wire disc which is separated from the main shaft for transmission is reversely rotated under the friction transmission of the rotating device.

5. A concentric cable strander according to claim 2 or 3, wherein the wire storage reel is rotatably mounted with a plurality of wire storage boxes in a circumferential direction, the wire storage boxes being adapted to pay out wires to the flying wing tension control mechanism;

The braking component is suitable for braking the wire storage disc separated from the main shaft;

The stranding module further comprises a reversing mechanism arranged on the wire storage disc; the reversing mechanism is suitable for connecting the main shaft with the wire storage box in a transmission way after the wire storage disc is separated from the main shaft, so that the wire storage box can reversely rotate.

6. The concentric cable strander of claim 5, wherein at least one side of the cable storage box is provided with a coaxial first friction wheel; the reversing mechanism includes:

a rotating device; the rotating device is fixedly arranged on the wire storage disc;

a rotating sleeve; the rotating sleeve is concentrically arranged on one side of the storage wire disc in a rotating way and meshed with the output end of the rotating device;

A plurality of transmission trains; the transmission gear trains are arranged on one side of the wire storage disc and correspond to the wire storage boxes along the circumferential direction, the input ends of the transmission gear trains are meshed with the clutch sleeve or the main shaft, and the output ends of the transmission gear trains are spaced from the first friction wheels corresponding to the wire storage boxes; and

A plurality of second friction wheels; the second friction wheel is rotatably arranged on a sliding block, the sliding block is slidably arranged on one side of the storage wire disc along the direction of the output end of the transmission gear train and the perpendicular bisector of the first friction wheel, and the sliding block is hinged with the rotating sleeve through a hinge plate;

when the storage wire disc and the main shaft synchronously rotate, the second friction wheel is far away from the first friction wheel;

When the wire storage disc is separated from the main shaft and the wire storage box is reversely wound, the rotating sleeve is driven by the rotating device to rotate, and then the hinged plate drives the second friction wheel to slide until the second friction wheel is in friction fit with the output end of the transmission gear train and the first friction wheel respectively.

7. The concentric cable strander of claim 1, wherein a wire reel is mounted at an end of the main shaft, and a plurality of through slots are provided in a circumferential direction at a mounting position of the main shaft to the flying wing tension control mechanism;

the flying wing tension control mechanism comprises:

A wheel body; the wheel body is provided with the main shaft and penetrates through the penetrating groove through a guide part which is arranged in a radial extending mode to extend into the main shaft, and then a wire which is discharged from the wire storage disc extends into the wire storage disc through the guide part in the main shaft; and

A plurality of tension control assemblies; the tension control assembly is arranged on the side part of the wheel body at equal intervals along the circumferential direction, and is suitable for tensioning the wires which are paid out by the wire storage disc.

8. The concentric cable strander of claim 7, wherein the tension control assembly comprises:

a support frame; the support frame is fixedly arranged on the wheel body;

a third guide wheel; the third guide wheel is rotatably arranged at the top of the support frame;

A tension wheel; the tension wheel is rotatably arranged on the sliding seat, and the sliding seat and the supporting frame are slidably arranged; the wire sequentially passes through the third guide wheel and the tension wheel and extends to the guide part; and

An elastic component; the elastic component is matched with the sliding seat, and the elastic component is suitable for driving the tension wheel to move when the tension of the wire changes so as to keep the tension of the wire.

9. The concentric cable strander of claim 8, wherein the elastic assembly comprises:

A slide bar; the sliding rod is arranged on the supporting frame in a flush sliding manner along the moving direction of the tension pulley;

a first elastic member; the first elastic piece is arranged on the sliding rod so as to enable the sliding rod to be elastically connected with the supporting frame in a sliding manner;

a second elastic member; one end of the second elastic piece is hinged with the supporting frame, the other end of the second elastic piece is connected with the sliding rod through a pull rope, and an included angle between the extending direction of the second elastic piece and the axial direction of the sliding rod is 90-150 degrees; and

A pull rope; the pull rope passes through the sliding seat so that the tension wheel slides under the traction of the pull rope.

10. The concentric cable strander of claim 8, wherein the support bracket is fixedly mounted with clamping blocks at equal height positions of the tension pulley; and when the tension pulley moves to the limit position, the tension pulley is suitable for being abutted against the clamping block, so that a loose wire is clamped between the tension pulley and the clamping block.