Device for twisting wires

 

(57) Abstract:

The invention relates to a device for the manufacture of twisted wires of two or more nutrient wires. Twisted wire is wound on the receiving reel, which is axially reciprocating move along its longitudinal axis. Power supply wire is fed through the device by means of a tension drum, the axis of the latter is coaxially arranged relative to the axis of the twisting means. The invention allows to simplify the design of the device. 7 C. and 11 C.p. f-crystals, 12 ill.

The invention relates to industrial equipment, in particular to Assembly machines for the manufacture of twisted wires of two or more nutritious wires, wound on the receiving reel.

Known Assembly machine for making twisted wire. For a number of years have spread these alternative machines, as mebelestroeniya machine, twisting machine, twisting machine is heavy type, bunching machine, and so on. These machines are used for combining multiple individual wires (or cables, filaments, fibers and so on) and twisting them together by message them one, two, or more skroce is, cause, reel up, move and so on to the receiving drum is driven in rotation.

These known mebelestroeniya machines usually have a receiving drum on which is wound a final product or twisted wire, driven in rotation around its axis to perform a full or partial twisting of the twisted wire. As soon as the wires are twisted, usually starts winding (or moving, winding, packaging or collapse in the Bay), in accordance with which the leading end of the twisted wire advancing to the receiving drum, which is then put into rotation by the application thereto of torque.

Known machines for making curled wire can operate at relatively high performance, thanks to which the wires are pushed through the machine with relatively high speeds and wrap the twisted wire on the rotary receiving drum is also carried out with relatively high speeds. Such constructions are described in several patents, in particular in U.S. patent 4397141, 09.08.1983 issued Garecki, in U.S. patent 4599853 issued Varga-Poppa, in U.S. patent 3791131 issued to Scott, and in U.S. patent 4182104, 08.01.1980 issued to Sacla. H the K

In accordance with known devices, the diameter and mass of the Bay of twisted wires that are downloaded to the receiving drum is constantly changing as the continuation of the load operation. This calls for a permanent change of energy required for rotation of the receiving drum. At the beginning of the loading operation of the receiving drum is empty and the wire is first wound on the receiving reel under the low rotational energy required for rotation of the receiving drum. As to the receiving drum wrap more wire, he gradually filled, and for this reason it becomes harder. For this reason, by the end of the loading operation for the rotation of the receiving drum may have considerably more torque.

Consequently, the torque required for rotation of the receiving drum, can be significant. This may be particularly evident towards the end of the loading operation, especially for large foster drums, when you have to rotate a lot of twisted wire, wound on the receiving reel. Thus, as should be obvious, the requirement of the energy required for rotation of the receiving drum, may not be constant, since R machines can become unstable, that is, to swing, during a load operation. Changing the mass of the receiving drum in combination with high speeds of rotation of the receiving drum can impede the adequate balancing of the receiving drum. This is particularly evident for large foster drums operating at high speed. In addition to the rotation around its axis, foster drums can vibrate, for example, around an axis which is offset from the center. Thus, it can be developed the design of modern machines, which could be capable of withstanding the swing of the receiving drum, volatile and unstable rotation of the riots. In addition, the design of today's cars can be made to withstand the constantly changing torque of the receiving drum, from a small torque at the beginning of a load operation prior to a potentially large torque at the end of the load operation.

In addition, during the load operation, if there is an emergency braking situation, the receiving drum with its changing weight can be difficult to resist the control, because the braking force that should be applied may vary depending on, near the, capable of withstanding heavy braking effort.

Some of the operational characteristics of known machines for this reason require larger, heavier and more expensive parts and components to counteract a large torque is generated due to a large mass rotating at high speed. For this reason, may increase the cost of manufacture, purchase and installation of such a machine. The size of the motors or actuators needed to bring the receiving drum in rotation, may also be considerably more to bring the rotation of the receiving drum, which will increase the size and weight in the boot process.

In addition, the machine known constructions can be further designed so that the configuration of the location of funds for promotion of wires, that is, for example, a tension drum, was such that the tension drum was located on the cradle or is to he revolved or oscillated (in addition to the rotation around its own axis). As a consequence, modern design can be expensive and difficult to manufacture. In addition, while the level of difficulty of removal and installation nating the e with an effective transfer of power to them, that may lead to loss of performance. In addition, the configuration of known construction the tension of the drum can often require a large number of complex and expensive parts and components.

In addition, the arrangement of funds for promotion of wires, that is, for example, a tension drum known constructions machines, can impede the speed change means for the implementation of the promotion of the wires during the load operation of the receiving drum, so that it may adversely affect operating range and performance of the known machines.

For this reason, it would be desirable to have a device that would prevent the need to align the receiving drum in rotational motion.

Additionally it would be desirable to have a device that would prevent the necessity of a tension drum, which has a suitable configuration and is located on an axis eccentric to the axis of rotation of the device.

For this reason, it would be desirable to have a device that would lower the cost of its production. It is therefore desirable to provide a device which could be characterized by less perfo the th of the invention.

The invention consists in that the device for manufacturing twisted wire from a variety of nutritious wires promoted through him, contains twisting means for at least one twisting specified multiple nutrient wires to get twisted wire, means for twisting the twisted wire to the receiving drum mounted on the longitudinal axis. The device is also equipped with means for reciprocating movement of the receiving drum along the longitudinal axis. The receiving drum is installed with the possibility of reciprocating movement along the specified axis for winding the twisted wire on it.

The device can also be so designed that twisting the product is intended for two twists of many nutrients wires. Moreover, the device can additionally be provided with a means for advancement through him many nutritional wires.

In another embodiment (second) execution of the specified device may be provided with a means for reciprocating movement of the receiving drum along the longitudinal axis. The receiving drum in this set is the County it when you wrap the twisted wire on it.

Moreover, the device can additionally be provided with a means for advancement through him many nutritional wires and twisting component.

Means for twisting the many nutritious of wires is made in the form of a first twisting means and the second twisting means. The first twisting the tool is designed for first curl and contains the specified torque component that is installed with the possibility of rotation around the longitudinal axis in a limited amount of space. Second twisting the tool is intended for the second curl after the first. The receiving drum in a specified volume of space.

There is one more option (third) of the apparatus for manufacturing twisted wire, from a variety of nutritious wires promoted through him. This device contains a means for at least two twists of many nutrients wires to get twisted wire, and means for twisting the twisted wire to the receiving drum mounted on the longitudinal axis with the exception of rotation relative to it. The device is further provided with means is attached with the possibility of reciprocating movement along the longitudinal axis for winding the twisted wire on it.

In addition, the device may be provided with a means for advancement through him many nutritional wires.

In the fourth embodiment, the above mentioned device comprises means for advancing wires, twisting means for at least one curl of many nutrients wires, and means for winding the twisted wire to the receiving drum. This twisting means includes first twisting component that is installed rotatably around the first axis in a limited amount of space. In addition, the device has a tensioning drum serving to promote the wires, and the second axis is coaxially installed with respect to the first axis. Moreover, the tension pulley is located with the possibility of rotation around the second axis.

With such design, device, twisting the tool may be designed for at least two twists of many nutrients wires. Means for advancing wires can be made in the form of functionally connected to the tensioning drum drive, used for messages tensioning drum rotation and located outside a specified amount of space. Thus n is the double twisting for the manufacture of double-twisted wire from a variety of nutritious wires, containing means for promotion of wires, the first twisting means for the first curl of many nutrients wires, which has a curved arm with opposite ends mounted rotatably on each of the opposite end around a common axis in a limited amount of space, and smachiwausa tool winder twisted wire to the receiving drum, which is mounted to the longitudinal axis, with the exception of rotation relative to it. The device is equipped with a second twisting means, intended for the second curl of many nutrients wires after the first twisting, and means for reciprocating movement of the receiving drum along the longitudinal axis for winding the twisted wire to the receiving drum. In addition, the device has a tensioning handwheel satyayuga means, the first and second axes, a tension drum means for advancing wire and its drive. At the same time the receiving drum is installed with the possibility of axial - reciprocating movement along the longitudinal axis, and a tension flywheel is mounted for rotation around the first axis, the and tension of the wires is mounted for rotation around the second axis, coaxially aligned with a common axis. The stretch drive of the drum is functionally connected with the tensioning drum with message him of rotation.

Propose the construction of a device for coiling wire to the receiving drum mounted on the longitudinal axis, and the method of winding the wire on the receiving drum mounted on the longitudinal axis.

The specified device contains a means for coiling wire on the receiving drum, and means for reciprocating movement of the receiving drum along the longitudinal axis with the winding of the wire on the drum.

The proposed method is characterized by the fact that when the winding wire at the receiving drum last report, the reciprocating movement along the longitudinal axis.

Fig. 1 is a vertical schematic front view of a variant example of implementation of the device corresponding to the present invention, showing the device for manufacturing twisted wire containing twisting means, means for effecting advancement of the wires, the receiving drum (not completely loaded position) and the instrument for reciprocating digieye additional provision of a tension handwheel, as well as the receiving drum is displaced in the axial longitudinal direction in an intermediate position.

Fig. 3 is a vertical schematic front view of a variant example of implementation of the device shown in Fig.1, showing another position of the tension handwheel and the receiving drum, advanced axially displaced in the longitudinal direction at the given position.

Fig. 4 is an enlarged schematic illustration of a modified version of the implementation of the drive.

Fig. 5 is an enlarged schematic illustration of a modified version of the implementation tools for the implementation of the reciprocating motion.

Fig. 6 is an enlarged schematic illustration of a modified version of the implementation tools for the implementation of the reciprocating motion and the receiving drum.

Fig. 7 is a schematic longitudinal section of the receiving drum, showing the mounting of the receiving drum on the shaft of the receiving drum.

Fig. 8 is a detailed schematic illustration of the mounting of the receiving drum, shown in Fig.7.

Fig.9 is an enlarged image of the front end of the shaft of the receiving drum, catalogazione in Fig.8.

Fig. 10 is an enlarged image of the rear end of the shaft of the receiving drum, a more detailed showing of the rear bearing installation connecting the shaft with the shaft of the receiving drum, as shown in Fig.8.

Fig. 10 is an enlarged image of the rear bearing installation connecting the shaft with the shaft of the receiving drum, shown in Fig.8.

Fig. 11 is a vertical front view of the counterweight, not shown mounted on the adjusting shaft received on lines 11-11 shown in Fig. 10.

Fig. 12 is a view of the receiving shaft end received on the line 12-12 shown in Fig.8.

In Fig. 1 shows a schematic illustration of a device 1 corresponding to the present invention containing two twisting means: first twisting means 2 and second twisting means 8, the receiving drum 3, the instrument for the promotion of wires 4, the means for implementing the reciprocating motion 9 rich wires 10 to be twisting device 1. Although it is not shown, but may provide some feed reel for feeding wires. With these drums in a known manner many nutritional wires should the, 1. In addition, the required number of the respective guide pulleys and other guiding mechanisms (not shown) should be located, mainly, to the left of the device 11 (as shown in Fig.1) for the effective direction in a known manner many wires 10 to the device 1. Also provided (but not shown) of the reference frame and the corresponding bearing means, switches, controllers, power supply and connections. Additionally, there are guide pulleys designed for the effective direction of many nutrients wires 10, and the intermediate wires 11 (i.e. wires, which were subjected to the same twisting and twisted wires 12 (i.e. wires, which were subjected to two twists) through the device 1. The guide pulleys are also provided to assist in the implementation of the desired curl. For example, the pulley 13 forms a part of the first twisting means 2 and helps in the message of the first twisting nutrient wire 10, in combination with the rotation of the first twisting means 2.

The first twisting means 2 includes an arcuate arm 5 and the pulley 13. Arcuate arm 5 is protivopolojna the opposite ends 6 and 7 rotatably will be described with reference to Fig.4 (for the end 7) and with reference to Fig.6 (for the end of the 6). Arcuate arm 5, when the device 1 is in working condition, should be driven to rotate around the axis 15 so that the arcuate arm 5 limited amount of space. The specified amount of space covers the receiving drum 3, and covers the tension handwheel 16. Second twisting means 8 also includes a tension handwheel 16. The tension handwheel 16 is so designed and located so as to have an L shape, and is mounted for rotation around a common axis 15. However, it is obvious that the tension flywheel 16 may be of other construction and arrangement and as a result has a different shape, for example, the shape of the letter U. the Mounting tension handwheel 16 rotatably will be described below with reference to Fig.4. Second twisting means 8, when it is in working condition, rotates around the axis 15 and causes the rotation of the tension handwheel 16, which also rotates around the axis 15 and covers the receiving drum 3. According Fig.1, the arcuate arm 5 can rotate around the axis 15 and covers the idler drum 19.

The receiving drum 3 is fixed with the possibility of removal on the shaft 18. Eat the receiving drum 3 from the shaft 18 possible after completion op oraway ledge 90 is provided at the far end of the shaft 75 so that to ensure the actual limit for receiving drum 3. Obviously, whenever the receiving drum 3 is removed from the shaft 18, the other receiving drum 3 of the same or of a different size and configuration can be installed in its place. The longitudinal axis of the shaft 18 shows the coaxial axis of the receiving drum 3, although it is obvious that the axis of the receiving drum 3 does not necessarily have to be coaxially aligned with the axis of the shaft 18. In the embodiment shown in Fig.1, the axis of the receiving drum 3 coaxial common axis 15. Although it is preferred implementation, it is obvious that the axis of the receiving drum 3 can be combined differently than common coaxial axis 15.

The instrument for the promotion of wires 4 includes an idler drum 19, the shaft 32 of the tension of the drum and the motor 31, which is functionally connected with the shaft 32 of the tension of the drum by a drive belt 30. Idler drum 19 is so designed and located so as to be driven in rotation by the shaft 32 of the tension of the drum around the longitudinal axis of the shaft 32 of the tension drum, which in the embodiment shown in Fig. 1, must be essentially coaxial common axis 15. The means 4 for PD is TBA nutrient wires 10 and the intermediate wires 11 through the twisting means.

Means for implementation of the reciprocating motion 9 contains a reversible electric motor 40 and a ball lead screw 57, which contains the carriage 58. It is suitable to induce axial reciprocating movement of the receiving drum 3 along its longitudinal axis. Thus, the means 9 for the implementation of the reciprocating motion can axially move the receiving drum 3 in the direction of the arrows 50 and 51, on the desired or required distance, for example, from the first position to the second position. As soon as the receiving drum 3 is moved to the required or desired distance, the means 9 for the implementation of the reciprocating motion induces the receiving drum 3 to move in the opposite direction, i.e. in the direction opposite to the movement of the arrow 50, for example, in the direction of the arrow 51. For any particular cycle of the reciprocating motion, providing for the movement in the first direction, for example, movement in the direction of arrow 50, and the movement in the opposite direction, for example in the direction of arrow 51, the distance in each direction may not be the same.

Mn is t feed reel (not shown), located in the left part of the view shown in Fig.1. Many intermediate wire 11 is shown partially advanced through the device 1 and through the first twisting means 2. Lots of twisted wires 12 shows additional advanced through the device 1, namely for the second twisting means 8. Twisted wire, indicated by the number 12', shown advanced further through the device 1. However, he is shown ready to move to the receiving drum 3. As may be obvious, the tension handwheel 16 directs the twisted wire 12' and causes the winding of the twisted wires 12' around the output drum 3. Rotational movement of the tension handwheel 16 around the output drum 3 is for this reason that motivates the movement of the twisted wire 12' for receiving the drum 3.

Arcuate arm 5 is driven into rotation around a common axis 15 by means of belts 20 and 21, each of the drive belts acting on the opposite ends 6 and 7, respectively, the arcuate arm 5 through the tubular shafts 17A and 17b. The motor 24 drives the drive belt 23, which is connected with a drive belt 20 and sets it in motion, and is also connected with a drive belt 2A 19, is rotated by an electric motor 31, which drives the drive belt 30, which in turn causes the rotation of the shaft 32 of the tension drum. Provided support bearings and other appropriate mechanical elements (not shown).

Second twisting means 8 includes a second torsion shaft 35, the third torsion shaft 37 and a means 36 for transmission, namely the brake system such as "hysteresis". The second torsion shaft 35 and the third torsion shaft 37 are so designed and located so as to be essentially coaxially aligned and everyone was able to rotate around a common axis 15. Brake system type "hysteresis" functionally connects the second torsion shaft 35 with the third torsion shaft 37 and is so designed and located so that he could make change the rotation speed of the third twisting of the shaft 37 so that the speed of the third twisting of the shaft 37 can be less than or equal to the speed of rotation of the second torsion shaft 35. Intermediate wire 11 is pushed so that he could pass through the center of the brake system "hysteresis", as will be further described with reference to Fig.4. The tension handwheel 16 is fixed on the third crucificado shaft 37 and the axis of rotation of the second torsion shaft 35), which is coaxially aligned with a common axis 15. The tension handwheel 16 is fixed on the third twisting the shaft 37 so that the torque of the third twisting of the shaft 37 induced rotation of the tension handwheel 16.

It is obvious that the drive belts 20, 21, 23 and 30 may be, if desired or necessary, replaced by mechanical or other equivalent alternatives, for example, sprockets, direct transfer or other means.

The drive mechanisms for the above-mentioned first twisting means 2 and the means 4 for the implementation of the promotion of wires, namely, the motor 24 and the motor 31 and their respective shafts, bearings, bearings and so on are designed so that the arcuate arm 5, the pulley 13, the idler drum 19, the second twisting means 8 and the tension handwheel 16 could each be rotated around a common axis 15. However, the speed of rotation of the various components may be different, for example, the speed of rotation of the arcuate arm 5 may be less than the speed of rotation of the idler drum 19. Stretch the flywheel 16 can rotate with the same speed as the third torsion shaft 37, but this speed may be less than the rotation speed of the second crucifixes is to be motor direct transmission, motors with adjustable speed, or alternatively, the electric motor AC or DC.

As you can see, the first twisting means 2 may optionally be provided with rocker protobalanus, partially shown under reference number 5b dashed lines disposed against the arcuate rocker arm 5. Optional arm 5b of protobalanus may not be provided in all variants of implementation of the present invention. The purpose of the optional rocker arm 5b of protobalanus is providing protobalanus the curved arm 5 so that the rotation of the arcuate arm 5, especially at high speed, could not unbalance or destabilize the device 1.

In Fig. 2 shows the device 1 illustrated in Fig.1, where the second twisting means 8, which is fixed to the tension handwheel 16, shown in another rotary position, it is rotated approximately 180orelative to the positions shown in Fig.1. Thus, in Fig.2 compared to Fig.1 you can see how the tension handwheel 16 is rotated around a common axis 15, as well as around the reception bar is irue in accordance with this fact, as the receiving drum 3 can be moved along the axis of the shaft 18. In Fig.2 position of the suction drum 3 is shown midway between the first (Fig.1) and the second (Fig.3) its provisions. The carriage 58 is also shown displaced in the direction of the arrow 50. The receiving drum 3 is shown partially filled with at least one layer of stranded wire 14, the tension handwheel 16 is rotated, at least a few times for application to a receiving drum 3 a certain amount of twisted wire 14.

In Fig.3 shows the device 1 illustrated in Fig.1, in which the second twisting means 8, which is fixed to the tension handwheel 16, shown in another rotary position, that is, approximately 180orelative to the positions shown in Fig.2, and around back to the position shown in Fig.1. In addition, the receiving drum 3 is additionally moved in the direction of the arrow 50. The carriage 58 is also shown additionally displaced in the direction of the arrow 50. It is shown that at the receiving drum 3 further harm twisted wire 14, and the tension handwheel 16 is rotated at least a few times for application to a receiving drum 3 a is placed on the tension handwheel 16, part of the sequence of axial movement of the receiving drum 3 and the portion of the sequence of axial movement of the carriage 58. From the shown variant of implementation of the present invention can be seen that the receiving drum 3 mounted on the shaft 18, is not rotated around its axis in the course of execution of the technological operation of the winding. Means for implementation of the reciprocating motion 9 informs the receiving drum 3 move only along the axis of the shaft 18 (which, as described above, is coaxially aligned with the longitudinal shaft receiving the RAM 3 and the common axis 15). Thus, the receiving drum 3 is provided in the axial reciprocating movement in the direction of the arrows 50 and 51, while he at the same time not directly provided in the rotation device 1.

As apparent from the above, wrap the twisted wire 14 to the receiving drum 3 is carried out in the combined and coordinated movements axially reciprocating roaming the receiving drum 3 and rotatable around him stretch of the flywheel 16.

Winding the twisted wire 14 to the receiving drum 3 may be for this reason lucrarea only part of the sequence (laying one layer of twisted wire 14) technological load operation of the drum 3, namely, the axial movement of the receiving drum 3 in one direction shown by the arrow 50. However, it is obvious that the movement of the receiving drum 3 is also in the reciprocating motion in the direction of arrow 51 for laying the second layer of twisted wire 14. In Fig.1 shows a receiving drum 3, the axially displaced along its longitudinal axis in the direction indicated by the arrow 50, in approximately the most distant position along a specified longitudinal axis. As an example, in Fig.1 the receiving drum 3 shows essentially not containing coiled wire 14 and, thus, are in or almost in the beginning of the process of the load operation. In Fig.1 twisted wire 14 is shown applied to a receiving drum 3 adjacent opposite to the first disk 51 of the receiving drum 3, although it is obvious that the operation load of the receiving drum can begin applying the twisted wire 14 at any location on the receiving drum 3, for example, near a second opposing disk 52. As soon as the twisted wire 12' is advanced through the device 1 to the receiving drum 3, the tension handwheel 16 is induced to rotate around its axis, which is coaxial common axis 15, so the howick 16 around the output drum 3, the receiving drum 3 moves axially along the longitudinal axis of the shaft 18 in the direction indicated by the arrow 50, to a distance which is sufficient to allow the tension to the flywheel 16 (which continues to rotate around the output drum 3) apply a second series of twisted wire 14 to the receiving drum 3. The distance that moves the receiving drum 3 can be adjusted in function of the speed of rotation of the tension of the flywheel 16, the thickness of the twisted wire 14, the desired winding density of the twisted wire 14 to the receiving drum 3 and from any other operational restrictions.

In Fig. 2 shows that it is possible to further subsequent movement in the implementation of the technological operation of the load receiving drum 3, and also shows that the receiving drum 3 is further moved along the longitudinal axis of the shaft 18 in the direction indicated by the arrow 50. Obviously, the tension handwheel 16 will rotate around the output drum 3 a few times in that time, as the receiving drum 3 is gradually moving to the receiving drum 3 was applied, an additional number of rows of twisted wire 14.

In Fig.3 shows the receiving bar is relay 50, so twisted wire 14 is deposited on the receiving drum 3 adjacent the second opposite to the disk 52.

In Fig.4 shows an enlarged schematic illustration of the drive mechanism corresponding to the present invention. Thus, it can be seen that provided by first twisting the tool 2, which contains the arcuate arm 5, and the second twisting means 8. Arcuate arm 5 is made to rotate around a common axis 15, so that it could limit the initial amount of space, as described above. In addition, provides a tool for the implementation of the promotion of wires 4, which contains the idler drum 19. Idler drum 19 is covered by the first volume of space, limited arcuate rocker 5. Idler drum 19 mounted on the shaft 32 of the tension drum, and the shaft 32 of the tension drum has an end part 32b, which stands for the idler drum 19. The shaft 32 of the tension drum is functionally connected to a drive belt 30 through the pulley 39. The drive belt 30 is functionally connected to the motor 31 (this drawing is not shown). Arcuate arm 5 is supported on a tubular shaft 17b arcuate rocker, and kasalka respective bearings 45. Thus, the tubular shaft 17b arcuate rocker arm is mounted for rotation by means of the belt 21, which in turn is driven by an electric motor through a connecting shaft 22 and the belt 23. However, the tubular shaft 17b arcuate rocker arm does not move axially. Thus, the tubular shaft 17b arcuate arm can rotate around the axis 15, and during this rotation rotates the arcuate arm 5, due to the fact that the arcuate arm 5 respectively connected to the tubular shaft 17b arcuate rocker using the appropriate tools.

As you can see, the shaft 32 of the tension drum is of such construction and is located in the cavity of the tubular shaft 17b arcuate rocker arm as shown. The axis of rotation of the shaft 32 of the tension of the drum and the tubular shaft 17b arcuate rocker essentially coaxial to each other and to the common axis 15. Thus, the shaft 32 of the tension drum rotates around its axis in the cavity of the tubular shaft 17b arcuate rocker. Between the tubular shaft 17b arcuate rocker arm and shaft 32 of the tension drum is provided by a corresponding number of ball bearings 46 of the appropriate type, cat. Thus, the shaft 32 of the tension of the drum and the tubular shaft 17b arcuate rocker are relative to each other so that each can rotate around its axis without touching the other.

Second twisting means 8 includes a second torsion shaft 35, which is coaxially aligned with a common axis 15. The second torsion shaft 35 is functionally connected to a tubular shaft 17b arcuate beam through the coupling plate 38, with the specified connection plate 38 is functionally connected with the tubular shaft 17b arcuate rocker arm via a connecting means, such as bolts 47 and 48, or other suitable means. As can be seen from Fig.4, the second torsion shaft 35 is in contact with the end part 32b through the respective bearings 46 so as not to inform her of the rotational motion, however, the end part 32b partially supports the second torsion shaft 35. As described earlier, is provided by brake system 36 type "hysteresis", and this system contains two components, the first external component and the second internal component mounted on the first outer component so that the second inner component is rotated relative to eplain to the far end of the second torsion shaft 35, so the part of the said far end of the second torsion shaft 35 also connects with the second internal component and is with him in contact. On the opposite side of brake system 36 type "hysteresis", that is, the second inner component may be secured third twisting the shaft 37. Thus, as can be seen, the axis of rotation of the second torsion shaft 35 and the third torsion shaft 37, essentially coaxially aligned with each other and with the common axis 15. The tension handwheel 16 is fixed on the third twisting the shaft 37 and, as you can see, the specified third twisting the shaft 37 is in contact with the second torsion shaft 35 through the bearings 86.

Second twisting means 8 according to the intermediate wire 11 driven through it, the second twisting between the pulleys 85 and 86. Brake system type "hysteresis" encourages third twisting the shaft 37 to rotate at a lower speed than the rotation speed of the second torsion shaft 35. When promoting intermediate wire 11 between the said pulleys 85 and 86, the difference between the rotational speeds of the third twisting of the shaft 37 and the pulley 85 mounted thereon, and the second skru the Fig.5 shows an enlarged illustration of the means 9 for the implementation of the reciprocating motion modified version of the implementation, relevant to the present invention. Shows a reversible electric motor 40, which is depicted in an alternative configuration the position shown in Fig.1-3. The means 9 for the implementation of the reciprocating motion contains a ball lead screw 57. Moreover, the specified ball screw Assembly is functionally connected to the reversible motor 40 through a belt 55 and through the drive pulley 56. Ball lead screw 57 is shown attached to the frame (shown partially reference number 63) through bearings 61 and 62, and these supports contain the appropriate bearings, liners, or other anti-friction means (not shown). Ball screw Assembly 57 also includes a carriage 58, which is functionally connected with the ball screw 57 so that the specified carriage 58 is supported and moved by a ball screw 57. This carriage 58 is functionally connected to the shaft 18 through bearings 59 and 60 so as to allow the shaft 18 to rotate around the axis 15, but does not report any specified rotation to the carriage 58.

In the process of applying the means 9 for the implementation of the reciprocating motion can operate I (in one direction or in the other direction), he makes the drive belt 55 to rotate in this direction, which in turn induces a spinning ball lead screw 57. The rotation of the ball screw 57 causes the movement of the carriage 58 in the direction determined by the direction of rotation of the reversible motor 40. As you can see, the direction of rotation of the reversible motor 40 in one direction will cause movement of the carriage 58 in the direction indicated by the arrow 50. As soon as the carriage 58 is moved to the required or desired distance along the direction indicated by the arrow 50, limit switch, for example of the type Seimens Proximiti Sensor or other control device or sensor (not shown), is a famous way powered, which will cause the signal reversing motor 40, inducing reversible motor 40 to stop the rotation in this direction and to change the direction of its rotation to rotate in the opposite direction. Now bringing the reversible motor 40 to rotate in the opposite direction will urge the carriage 58 to move in the direction indicated by the arrow 51, via the above mechanism. When functionally direction, indicated by arrows 50 and 51. Thus, the axial reciprocating movement of the carriage 58, in the direction indicated by the arrow 50, and the direction of the arrow 51, will cause identical or substantially identical to the axial reciprocating motion of the shaft 18. For this reason, the shaft 18 will be correspondingly axially reciprocating to move in the direction of the arrows 50 and 51.

In Fig.6 shows another schematic illustration of the means 9 for the implementation of the reciprocating motion modified version of the implementation of the present invention, showing the relationship between the shaft 18 and the rest of the means 9 for the implementation of the reciprocating motion. Shown first twisting means 2, containing arcuate arm 5, and the second twisting means 8. In addition, the tension handwheel 16, with a variation of the configuration shown without any twisted wire on it. Tubular shaft 17A arcuate rocker is shown supported on the frame (shown partially under the reference number 64) through a set of corresponding bearings, indicated by reference numbers 71, 72 and 73. Tubular shaft 17A is which in turn is driven by an electric motor 24 (Fig.1 is not shown). Tubular shaft 17A arcuate rocker arm is mounted for rotation around the axis 15, but he resists axial movement either in the direction indicated by the arrow 50, or in the direction indicated by the arrow 51. As can be seen in Fig.6, the tubular shaft 17A arcuate rocker has a cavity. The shaft 18 is shown as a shaft having a configuration and located in the cavity of the tubular shaft 17A arcuate rocker. For this reason, the shaft 18 comes into contact with the slidable with the inner walls of the tubular shaft 17A arcuate rocker. The keyway 70, which is in contact with the slidable with key 80, fixes the shaft 18 and the tubular shaft 17A arcuate rocker together so that rotation of the tubular shaft 17A, arcuate rocker when casting into rotation by a drive belt 21, was also caused by the rotation of the shaft 18. Thus, the tubular shaft 17A arcuate rocker arm and shaft 18 rotate with the same speed. The correspondence between the tubular shaft 17A arcuate rocker arm and shaft 18 such that the shaft 18 is supported at least partially tubular shaft 17A arcuate rocker.

As described, the shaft 18 is subjected to a rotation around the axis 15, however, the receiving drum 3, which, as will be described below, is mounted on the end of it, does not undergo any rotation or any substantial rotational movement of the shaft 18. The receiving drum 3 can be mounted with the possibility of removal on the installation of Wales by means of bearings 76 and 77. The specified shaft 81 of the drum, in turn, fixedly connected to the specified shaft 18 of the drum, so that the shaft 81 of the drum to be turned around the axis 15 due to the rotation of the shaft 18. These bearings 76 and 77 do not convey any rotation of the mounting shaft 75 on the shaft 81 of the drum, from which it follows that the shaft 18 and the shaft 81 of the drum can rotate, but the installation shaft 75 and the receiving drum 3 will not rotate due to the rotation of the shaft 18.

However, the installation shaft 75 must be mounted on the shaft 81 of the drum so that axial reciprocation in the direction of the arrows 50 and 51, reported receiving drum 3. Axial reciprocating movement means to carry out a reciprocating motion 9 described in the application above. It makes axial reciprocating movement of the shaft 18, the shaft 81 of the reel mounting shaft 75 and the receiving drum 4. Obviously, if necessary, the installation shaft 75 can be eliminated, and the receiving drum 3 can be mounted directly on the shaft 18 at a corresponding modification. In addition, the receiving drum 3 can be assembled with the appropriate cargo 78, which can lastwow is intended to regulate the tension of the twisted wire 12'.

The shaft 18 has a groove or groove 200, which has such a size and configuration that it could enter the pulley 13, when the shaft 18 is moved in the axial direction.

In Fig. 7 shows a schematic section of the drum, showing the means of fastening the receiving drum on the shaft 81 of the drum. The receiving drum 3 is mounted for rotation directly on the shaft 81 of the drum. The shaft 81 of the drum is shown as a shaft having edge 90 at the far end of the shaft 81 of the drum. Shows the bearings 76 and 77. The receiving drum 3 is removed from the shaft 81 of the drum by lifting in the direction shown by the arrow 91, and then move in the direction indicated by the arrow 92. The receiving drum 3 must be raised on the distance that must be greater than shown by the reference number 93 to be removed from the edge 90.

In Fig. 8 shows a detailed schematic illustration of the mounting of the receiving drum 3, as illustrated in Fig.7. The receiving drum 3 is shown mounted with the possibility of removal on the installation shaft 75' and held in place partly under the influence of gravity. Mounting shaft 75' and the receiving drum 3 have the same configuration, and the materials from which they are made, are selected so that contato frictional resistance to the relative motion between them. Mounting shaft 75' further comprises at its far end of the ledge 100, which serves as a temporary measure to prevent the decay of the receiving drum 3 with the mounting shaft 75', for example, in the case when the machine is running. As shown in Fig.8, the receiving drum 3 is located on the mounting shaft 75' so that between the lip 100 and the edge 96 there was a gap, and Vice versa, so that the opposite end 96A of the receiving drum 3 rests against the flange 101 of the mounting shaft 75'. However, it is obvious that this configuration may be reversed, or alternatively, the receiving drum may not be in contact either with the tab 100, no flange 101. Although it is not shown, but the receiving drum 3 may be stationary with the possibility of removal is connected with the mounting shaft 75', thanks to the use of any known fastening means, such as pins, screws, brackets and so on.

Mounting shaft 75' mounted on the shaft 81 of the drum due to the application of anti-friction means, namely a front bearing 77' and the rear bearing 76 . As described above, for example, with reference to Fig.1-3, the shaft 81 of the drum can be transmitted rotation via a shaft 18. However, the presence of bearings 77' and 76' AK obviously, when the shaft 81 of the reel mounting shaft 75' will not (or essentially will not be transmitted to the rotation due to the presence of bearings 76' and 77'. Therefore, the receiving drum 3 also will not rotate relative to the (rotating) shaft 81 of the drum.

However, it is obvious that the bearings 76' and 77' may not all not to have friction and for this reason, transfer the torque from the shaft 81 of the reel mounting shaft 75'. In addition, the winding of the twisted wire 14 to the receiving drum 3 (as shown in Fig.1-3) may create some torque, which is transmitted to the receiving drum 3 by a twisted wire (not shown). For this reason, to counter the (unwanted) torques, if they occur, use the counterweight 79, mounted by the mounting means 175, for example, pins, screws, brackets and so on.

The receiving drum 3 can be removed from the mounting shaft 75' by lifting using the tool in the direction indicated by the arrow 110, so that the edge 96 of the receiving drum 3 could overcome the ledge 100 mounting shaft 75'. As soon as the edge 96 of the receiving drum 3 has overcome the protrusion 100, the receiving drum 3 may be provided additionally is and 75'. Obviously, to implement the removal of the receiving drum 3, the diameter of the body 105 of the receiving drum 3 must be greater than the overall diameter 106 of the mounting shaft 75'.

In Fig.9 shows an enlarged view from the front end of the shaft 81 of the drum, which shows in detail the front bearing 77' connecting the mounting shaft 75' with the shaft 81 of the drum, as shown in Fig.8.

The bearing 77' mounted so as to allow to transmit the power of the translational motion between the shaft 81 of the drum and mounting shaft 75', i.e. in the direction indicated by arrows 50 and 51, not transmitting torque between them. The front bearing 77' may be bearing any known type and, as shown, includes an annular support which is arranged to surround the far end of the shaft 81 of the drum. Although the bearing 77' is shown as annular bearing, it can be bearing any other appropriate type.

In particular, it is shown the shaft 81 of the drum, having at its front end a number of narrow concentric steps, which limit between a shoulder 145 and 146, on which rests the front bearing 77'. The bearing 77' held in place between the shaft 81 of the drum and mounting shaft 75' posed 153 are located on opposite sides of the bearing 77', and retaining snap ring 152 is in front of the bearing 77'. The locking device spring rings 151, 152 and 153 such that the bearing 77' held in place against shoulder 145 and 146.

The transfer of forces translational motion between the shaft 81 of the drum and mounting shaft 75 is partially through the combined action of the shoulder 145 and 146 and locking spring rings 151, 152 and 153 acting on the front bearing 77'. Thus, when movement of the shaft 81 of the drum in the direction indicated by the arrow 51, the flange 145 and 146 thrust bearing 77', which causes the bearing 77' to transmit the power of the translational motion stoparea spring ring 151. This force of the translational motion is then transmitted mounting shaft 75', which, consequently, is also moved in the direction indicated by the arrow 51.

When the movement of the shaft 81 of the drum in the opposite direction, i.e. in the direction indicated by the arrow 50, the shaft 81 of the drum pulls the retaining snap ring 152. Retaining snap ring 152 then pushes the bearing 77', causing the bearing 77' to transmit the power of the translational motion stoparea spring ring 153. After this translational force is shown by arrow 50.

As you can see, the locking spring ring 151 and 153 are located in the grooves 155 and 156 located on the surface of the inner diameter 157 mounting shaft 75'. The retaining snap rings 151, 152 and 153 should be made of appropriate elastic material, for example, of steel. The locking spring ring 151 and 152 must be installed so that when compressed they would be deformed, pressed in the groove (for example, in grooves 155 and 156), and when removing the load otpugivali would be back and would strongly retained in place in the specified slot. Conversely, when exposed to a force in the opposite direction of the locking snap ring 152 is deformed to fit to the far end of the shaft 81 of the drum, and removing the load they would otpugivali ago and tightly held in place.

In Fig. 10 shows an enlarged image of the rear end of the shaft 81 of the drum, which shows in detail the rear bearing 76' connecting the mounting shaft 75' with the shaft 81 of the drum, as shown in Fig.8.

As described with reference to the bearing 77, the bearing 76' is set to enable transmission power of the translational motion between the shaft 81 of the drum and mounting shaft 75', i.e. in the direction of the movement is any known type of bearing and as shown, to have the support ring, which is arranged to surround the end a shaft 81 of the drum. Although the bearing 76' is shown as annular bearing, it can also be any other suitable type of bearing.

The shaft 81 of the drum is shown as a shaft having at one end 81a a number of narrow concentric steps, which limit between the flange 160 and 161, on which rests the rear bearing 76'. Mounting shaft 75' also has a shoulder 165 and 166, which also relies bearing 76'. The bearing 76' held in place between the shaft 81 of the drum and mounting shaft 75' by means of the locking spring ring 162 and for this reason rests on the shoulder 160 and 161 and the flange 165 and 166.

The transfer of forces translational motion between the shaft 81 of the drum and mounting shaft 75' is done partly through the combined action of the shoulder 160, 161 and shoulder 165, 166, and impact spring retainer ring 162 on the bearing 76'. Thus, when movement of the shaft 81 of the drum in the direction indicated by the arrow 51, the shoulder 160 and 161 thrust bearing 76', which causes the bearing 76' to transmit the power of the translational motion of the shoulder 165 and 166 of the mounting shaft 75', to encourage and shaft 8 of the drum in the opposite direction, that is, in the direction indicated by the arrow 50, the shaft 81 of the drum is not directly transmits the force of the translational motion of the rear bearing 76'. In this case, they represent the strength of the progressive movement, acting on the retaining snap ring 152, as shown in Fig.9, which encourage the installation shaft 75' to move in the direction indicated by the arrow 50, and make the shoulder 165 and 166 to push the bearing 76'.

As you can see, the retaining snap ring 162 is located in the groove 167. As described above with reference to the retaining snap rings 151, 152 and 153, retaining snap ring 162 must also be made of elastic material, for example, of steel.

In Fig. 10 additionally shows the counterweight, 79, containing the support plate 171, which in turn contains the support ring 170. The support ring 170 is in contact with the mounting shaft 75', tight to him and attached (with pickup) by means of the fastening means, e.g. bolts 173', as further described with reference to Fig.11. The base plate 171 is also firmly attached to the counterweight 78', which are attached to the base plate 171 (removal) posredstwom in Fig.10) counterweight 79, shown not mounted on the mounting shaft 75'. The counterweight 79 includes a support plate 171 having a support ring 170 having the same configuration and located so as to provide the possibility of contact interaction with the possibility of removal and fit the mounting shaft 75' (as shown in Fig.10). The support ring 170 includes a mounting means 173, 173' 173', as shown, for example, as pins or set screws, which can be used for attaching the support ring 170 to the mounting shaft 75' (as shown in Fig.8 and 10). The counterweight 79 further comprises a counterweight 78' shown mounted on the base plate 171 by means of the fastening means 97, 97' and 97", for example, of bolts, the heads of which are shown on the drawing. The base plate 171 is also provided with fastening means 175, for example, a cotter pin, screw, mounting bracket, and so on, which can be fastened to the counterweight 79 for receiving the drum 3, as shown in Fig.8 and 10.

In Fig. 12 illustrates a vertical front view of the receiving drum 3 along lines 12-12 shown in Fig.8. Details front bearing 77', shown in Fig.8 and 9, were excluded. The receiving drum 3 shown mounted (with pickup) on the installation vechnosti 98 of the receiving drum 3. Mounting shaft 75' shown with the protrusion 100 and the protrusion 100 has such a configuration and is ideally located to act as a temporary means to prevent the decay of the receiving drum 3 with the mounting shaft 75'.

Obviously, for the removal of the receiving drum 3 with the mounting shaft 75', the receiving drum 3 must be raised in the direction indicated by the arrow 110. Overcoming surface 98 of the upper part of the protrusion 100, the receiving drum 3 can then be moved in the direction indicated by the arrow 111, as shown in Fig.8, i.e. in the direction facing from the page toward the reader. Thus, in order to implement removal of the receiving drum 3, the diameter of the body 105 of the receiving drum 3 must be greater than the overall diameter 106.

1. Device for manufacturing twisted wire from a variety of nutritious wires promoted through him, containing twisting means for at least one twisting specified multiple nutrient wires to get twisted wire, means for twisting the twisted wire to the receiving drum mounted on the longitudinal axis, characterized in that it is provided with means for reciprocating the post is using reciprocating movement along the specified axis for winding the twisted wire to the receiving drum.

2. The device under item 1, characterized in that the twisting tool is designed for two twists of many nutrients wires.

3. The device under item 1, characterized in that it is provided with a means for advancement through him many nutritional wires.

4. The device according to p. 2, characterized in that it is provided with a means for advancement through him many nutritional wires.

5. Device for manufacturing twisted wire from a variety of nutritious wires promoted through him, containing twisting means for at least two twists specified multiple nutrient wires to get twisted wire, means for twisting the twisted wire to the receiving drum mounted on the longitudinal axis, characterized in that it is provided with means for reciprocating movement of the receiving drum along the longitudinal axis, while the latter is installed with the possibility of reciprocating movement along the longitudinal axis and rotatably around it when you wrap the twisted wire to the receiving drum.

6. The device under item 5, characterized in that it is provided with a means for prodsnaba twisting component, and means for twisting the many nutritional wires made in the form of first and second twisting means, with the first twisting the tool is designed for first curl and contains the specified torque component that is installed with the possibility of rotation around the longitudinal axis in a limited amount of space, and the second twisting the tool is intended for the second curl after the first twist, and the receiving drum is located in a specified volume of space.

8. Device for manufacturing twisted wire from a variety of nutritious wires promoted through him, containing means for at least two twists of many nutrients wires to get twisted wire, means for twisting the twisted wire to the receiving drum mounted on the longitudinal axis with the exception of rotation relative to it, characterized in that it is provided with means for reciprocating movement of the receiving drum along the longitudinal axis, while the latter is installed with the possibility of reciprocating movement along the longitudinal axis for winding the twisted wire to the receiving drum.

10. Device for manufacturing twisted wire from a variety of nutritious wires containing means for advancing wires, twisting means for at least one curl of many nutrients wires, means for winding the twisted wire to the receiving drum, while twisting means includes first twisting component that is installed rotatably around the first axis in a limited amount of space, characterized in that it is provided with a tensioning drum serving to promote the wires, and the second axis is coaxially installed with respect to the first axis, and a tension pulley is located with the possibility of rotation around the second axis.

11. The device according to p. 10, characterized in that the twisting tool is designed for at least two twists of many nutrients wires.

12. The device according to p. 10, characterized in that the means for advancing wires made in the form of functionally connected to the tensioning drum drive, used for messages tensioning drum rotation and located outside a specified amount of space.

13. The device according to p. 11, characterized in that the means dlds messages tensioning drum rotation and located outside a specified amount of space.

14. The device according to p. 12, characterized in that the tension drum is located in a specified volume of space.

15. The device according to p. 13, characterized in that the tension drum is located in a specified volume of space.

16. The double twist for the manufacture of double-twisted wire from a variety of nutritious wires containing means for promotion of wires, the first twisting means for the first curl of many nutrients wires having arcuate arm with opposite ends mounted rotatably on each of the opposite end around a common axis in a limited amount of space, smachiwausa tool winder twisted wire to the receiving drum mounted on the longitudinal axis with the exception of rotation relative to it, wherein it is provided with a second twisting means, intended for the second curl of many nutrients wires after the first curl, means for reciprocating movement of the receiving drum along the longitudinal axis for winding the twisted wire to the receiving drum, a tension handwheel satyayuga among the Yemen dryer is installed with the possibility of axial reciprocating movement along the longitudinal axis, stretch the flywheel is mounted for rotation around the first axis, coaxile combined with a common axis, and is located in the specified volume of space, the tension drum means of tension wires is mounted for rotation around the second axis, coaxile combined with a common axis, and the drive of the tensioning drum functionally connected with the tensioning drum with message him of rotation.

17. Device for coiling wire to the receiving drum mounted on the longitudinal axis containing a means for coiling the wire to the receiving drum, characterized in that it is provided with means for reciprocating movement of the receiving drum along the longitudinal axis with the winding wire at the receiving drum.

18. The way the wire winding on the receiving drum mounted on the longitudinal axis, characterized in that when the winding wire at the receiving drum last report, the reciprocating movement along the longitudinal axis.

 

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FIELD: packing equipment, particularly for strapping articles with binding material and for tightening wire binding and tensioning members.

SUBSTANCE: device has body, in which indicator, the first gear wheel, detachable finger and torque sensor are installed. Rod with stop is secured to body. Detachable finger may be installed in axial orifice of the first gear wheel perpendicular to gear wheel axis of rotation. The second gear wheel mounted on shaft and reducer are linked to drive through above orifice. Torque sensor is connected to drive and mounted on shaft. The first gear wheel includes the first removable toothed section. Finger ends may be installed in slots formed in side wall of above axial orifice or may be secured in toothed section and in slot formed in side wall of above axial orifice opposite to toothed section.

EFFECT: simplified device structure, reduced time of binding or tie members installation on item, increased reliability due to provision of optimal wire tensioning force applied to item.

5 cl, 4 dwg

FIELD: technological processes.

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FIELD: mechanical engineering.

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FIELD: process engineering.

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5 cl, 6 dwg

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