JP2016098444A - False twisting machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a false twisting machine which is capable of reducing vibration of a beam member without enlarging the cross-sectional size of the beam member supporting a feed roller.SOLUTION: On a false twisting machine equipped with a false twisting device 65 which false twists yarns by a multiple of yarn guides formed in an arrangement direction, a take-up device taking up yarns false twisted by the false twisting device 65 and a feed roller 66 and 68 which feed yarns, a main machine frame 10 which supports a plurality of the false twisting device 65 disposed in the arrangement direction, a winding stand where a plurality of take-up devices are mounted, beam members 13 and 14 which extend in the arrangement direction at least either on the main machine frame 10 or the winding stand and support the feed rollers 66 and 68, and a dynamic vibration absorber 80 is mounted on the beam members 13 and 14 which controls vibration in a direction perpendicular to an axial direction of the beam members 13 and 14.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a false twisting machine that performs false twisting on a yarn.

  For example, in the false twisting machine described in Patent Document 1, a unit called a span is formed by one main machine base and one winding base, and the whole is configured by arranging a plurality of spans. Yes. In one span, a plurality of false twisting devices are supported by the main machine stand in a state in which they are arranged in the span arrangement direction (hereinafter simply referred to as “arrangement direction”), and a plurality of winding devices are attached to the winding stand. It is installed. As a result, a plurality of yarn paths are formed in the arrangement direction in one span of the false twisting machine, and a plurality of yarn packages subjected to false twisting can be simultaneously produced.

JP 2014-77217 A

  In recent years, in order to further improve the production efficiency of packages, the number of false twisting devices and winding devices provided in one span tends to increase. As a result, the number of false twisting devices arranged in the arrangement direction increases, and the span dimension in the arrangement direction increases. At this time, with respect to the beam members extending in the arrangement direction on the main machine base and the take-up base, there is a problem that vibration in a direction orthogonal to the axial direction is easily amplified by extending the length thereof. It was. In particular, in a beam member that supports a feed roller for feeding yarn, vibration is likely to occur due to the rotation of the feed roller. In addition, since the feed roller is relatively light, the cross-sectional dimension of the beam member is originally small, and the amplification of vibration due to extension is remarkable.

  In order to solve such a vibration problem, it is conceivable to increase the rigidity of the beam member by increasing the cross-sectional dimension of the beam member. However, these accessory parts are densely arranged around the beam member to which the feed roller and interlace (entanglement device) are attached. Therefore, if the cross-sectional dimension of the beam member is increased, the workability of threading and maintenance can be improved. It would be difficult to increase the cross-sectional dimension of the beam member due to a decrease in the size and the increase in the overall dimensions of the machine.

  Accordingly, an object of the present invention is to provide a false twisting machine capable of reducing vibrations generated in a beam member without increasing the cross-sectional dimension of the beam member that supports the feed roller.

  In order to achieve the above-mentioned object, the present invention provides a false twisting device that falsely twists a yarn for each yarn path formed in the arrangement direction, a winding device that winds up the yarn falsely twisted by the false twisting device, And a false twisting machine provided with a feed roller for feeding the yarn, a main machine base that supports the plurality of false twisting devices arranged in the arrangement direction, and a winding stand on which the multiple winding devices are mounted And a beam member extending in the arrangement direction in at least one of the main machine base and the winding base and supporting the feed roller, and the beam member in the axial direction of the beam member A dynamic vibration absorber that suppresses vibrations in the orthogonal direction is provided.

  According to the present invention, the dynamic vibration absorber that suppresses the vibration in the direction orthogonal to the axial direction is provided on the beam member that supports the feed roller. For this reason, it is possible to reduce the vibration of the beam member with a simple configuration in which a dynamic vibration absorber is provided without increasing the cross-sectional dimension of the beam member.

  Further, the main machine base is provided with an entanglement device for entanglement of the yarn, and the feed rollers are provided on both upstream and downstream sides in the running direction of the yarn with respect to the entanglement device. It is preferable that the beam members are supported by different beam members.

  According to such a configuration, the feed rollers are provided on both the upstream and downstream sides in the yarn traveling direction with respect to the entanglement device, so that the yarn tension in the entanglement device can be appropriately adjusted by adjusting the speed of these feed rollers. it can. Further, in this configuration, since the entanglement device, the feed roller, and the beam member are arranged at high density on the main machine base, it is particularly difficult to change the beam member to one having a large cross-sectional dimension. For this reason, the solution means of providing a dynamic vibration absorber is particularly effective.

  The dynamic vibration absorber includes a support provided on the beam member, a weight supported by the support, and an elastic body provided between the support and the weight. It is preferable that

  According to this configuration, when the vibration of the beam member is transmitted to the weight via the support and the elastic body, the elastic body is compressed and deformed, so that the vibration energy of the beam member is absorbed. For this reason, the vibration of the beam member can be effectively reduced.

  The support body has two inclined surfaces inclined with respect to a horizontal plane in a cross section orthogonal to the axial direction, and is configured to support the weight by the two inclined surfaces. It is preferable.

  When the weight is supported by two inclined surfaces as in this configuration, the weight of the weight acts in both the vertical direction and the horizontal direction with respect to the inclined surface. It occurs in both the vertical direction and the horizontal direction at the portions that touch each other. For this reason, out of vibrations in the direction orthogonal to the axial direction of the beam member, both vertical and horizontal components, that is, vibrations in all directions in a plane orthogonal to the axial direction of the beam member can be reduced.

  Here, it is preferable that an angle formed by the two inclined surfaces is not less than 70 degrees and not more than 110 degrees.

  When absorbing vibration energy using the compression deformation of an elastic body in contact with the inclined surface, if the angle formed by the two inclined surfaces is large, the weight is likely to rise along the inclined surface, so that vibration can be reduced. Is limited. On the other hand, if the angle formed by the two inclined surfaces is small, the weight is sandwiched between the two inclined surfaces and the movement is restricted, so that the ability to absorb vibration energy decreases. Therefore, by setting the angle formed by the two inclined surfaces to 70 degrees or more and 110 degrees or less, the vibration energy can be efficiently and efficiently absorbed using the compressive deformation of the elastic body in contact with each inclined surface.

  The two inclined surfaces are preferably inclined at an angle of not less than 35 degrees and not more than 55 degrees in the opposite direction with respect to the horizontal plane. Furthermore, the two inclined surfaces are respectively inclined at 45 degrees in the opposite direction with respect to the horizontal plane. More preferably, it is inclined.

  As described above, when the vibration is reduced by using the compression deformation of the elastic body, it is preferable that the weight is not lifted from the inclined surface as much as possible even if the vibration acceleration is increased. Therefore, by setting the inclination angle of the inclined surface to about 35 degrees or more, it is possible to prevent the weight from floating from the inclined surface even when the vibration acceleration is increased. In addition, by setting the inclination angle of the inclined surface to about 55 degrees or less, it is possible to prevent the weight from being sandwiched between the two inclined surfaces to restrict movement and shear deformation of the elastic body, thereby absorbing vibration energy. Is not inhibited. In particular, by setting the inclination angle of the inclined surface to about 45 degrees, vibration energy can be efficiently shared and absorbed by each inclined surface without waste, and the vibration acceleration that can be reduced can be maximized. . For this reason, the vibration in the direction orthogonal to the axial direction of the beam member can be effectively reduced regardless of the vibration direction.

  Further, it is preferable that the weight has a cylindrical shape extending in the axial direction.

  If the weight is a cylindrical shape extending in the axial direction, the dimension of the weight in the direction orthogonal to the axial direction of the beam member can be suppressed. For this reason, even if it is a narrow space, arrangement | positioning of a dynamic vibration absorber becomes easy.

  Further, it is preferable that the elastic body is an O-ring attached to a peripheral surface of the columnar weight.

  By making the elastic body an O-ring, the contact area between the elastic body and the inclined surface is reduced, the elastic body is easily compressed and deformed, and the vibration reduction effect can be improved. Further, since the O-ring is a general-purpose product and there are a wide variety of types, the elastic modulus and dimensions of the O-ring can be easily changed, and the natural frequency of the dynamic vibration absorber can be easily adjusted. For this reason, it becomes easy to effectively reduce the vibration of the beam member.

  A plurality of the O-rings can be attached to the weight, and each of the plurality of O-rings is detachable from the weight.

  At this time, since the number of O-rings attached to the weight can be adjusted, the degree of freedom in adjusting the natural frequency of the dynamic vibration absorber is improved. For this reason, it becomes easier to reduce the vibration of the beam member more effectively.

  According to the present invention, by providing the dynamic vibration absorber in the beam member that supports the feed roller, it is possible to reduce the vibration generated in the beam member without increasing the cross-sectional dimension of the beam member.

It is a front view which shows the false twist processing machine concerning one Embodiment of this invention. It is the schematic diagram which looked at the main machine stand for 1 span from the winding stand side. It is the schematic diagram which looked at the winding stand for 1 span from the main machine stand side. It is a disassembled perspective view of a dynamic vibration absorber. It is sectional drawing orthogonal to the longitudinal direction of a dynamic vibration absorber It is sectional drawing in VI-VI of FIG. It is a graph which shows the vibration measured value of a beam member. It is sectional drawing orthogonal to the longitudinal direction of the dynamic vibration damper in other embodiment.

  Hereinafter, embodiments of the present invention will be described. FIG. 1 is a front view showing a false twisting machine 1 according to an embodiment of the present invention. The false twisting machine 1 is, for example, for applying a twist to thermoplastic synthetic fibers such as polyester and polyamide to impart crimps to produce a processed yarn rich in elasticity.

  As shown in FIG. 1, in the false twisting machine 1, a unit called a span is formed by one main machine base 10 and one take-up base 20 that are arranged to face each other. Two spans are provided symmetrically about the main stand 10. In other words, the left and right spans share the main machine base 10 arranged at the center. The entire false twisting machine 1 is configured by arranging a plurality of two symmetrical left and right spans in the arrangement direction (the depth direction of the paper surface of FIG. 1).

  Within one span, there are provided a main machine base 10, a take-up stand 20 disposed opposite to the main machine stand 10, a support 30 for connecting the main machine stand 10 and the take-up stand 20 at their upper parts, and the like. In addition, each device described later is arranged in these. The main machine base 10 extends in the arrangement direction. The take-up stand 20 is disposed to face the main machine base 10 with a work space 40 therebetween. On the side opposite to the work space 40 with respect to the take-up table 20, a work space in which an operator picks up a fully wound package P wound up by a plurality of take-up devices 71 provided on the take-up table 20. There are 50.

  Further, in one span, a yarn feeding section 61 disposed opposite to the winding table 20 with the work space 50 interposed therebetween, a plurality of false twisting devices 65 provided in the arrangement direction above the main machine base 10, and a winding table 20 includes a plurality of winding devices 71 and the like. The yarn feeding section 61 holds a plurality of yarn feeding packages S and feeds the yarn Y of the yarn feeding package S. The false twisting device 65 false twists the yarn Y supplied from the yarn supplying unit 61. The winding device 71 winds the yarn Y falsely twisted by the false twisting device 65 to form a package P. The same number of yarn supply packages S, false twisting devices 65, winding devices 71, etc. are provided in one span, and the same number of yarn paths are formed in the arrangement direction.

  On the yarn path from the yarn feeding section 61 to the winding device 71, the first feed roller 62, the first heating device 63, the cooling device 64, the false twisting device 65, and the second feed roller are sequentially arranged from the upstream in the traveling direction of the yarn Y. 66, an interlace (entanglement device) 67, a third feed roller 68, a second heating device 69, and a fourth feed roller 70 are arranged. In the false twisting machine 1, devices along the yarn path from the yarn feeding unit 61 to the winding device 71 are arranged symmetrically with the main machine base 10 in between.

  The first feed roller 62 is disposed on the upper part of the winding table 20. The first heating device 63 is disposed above the work space 40. The cooling device 64 is disposed above the work space 40 and closer to the main machine base 10 than the first heating device 63. The false twisting device 65 is disposed on the upper part of the main machine base 10. The second feed roller 66 is disposed below the false twisting device 65 in the main machine base 10. The interlace 67 is disposed below the second feed roller 66 in the main machine base 10. The third feed roller 68 is disposed below the interlace 67 in the main machine base 10. The second heating device 69 is disposed below the third feed roller 68 in the main machine base 10. The fourth feed roller 70 is disposed at the lower part of the winding table 20.

  The first heating device 63 and the cooling device 64 are arranged substantially linearly in the horizontal direction above the work space 40, and the yarn path from the yarn supplying unit 61 to the winding device 71 passes through the work space 40. It is formed to surround. The first heating device 63 and the cooling device 64 are fixed to the support portion 30. In the work space 40, an operator can get on a working carriage for threading (not shown), perform threading at a high position in the vicinity of the first heating device 63 and the cooling device 64, and perform maintenance. Become.

  Each of the feed rollers 62, 66, 68, 70 is a roller for feeding the yarn Y from the upstream side to the downstream side in the yarn traveling direction. The yarn feed speed of the second feed roller 66 is set faster than the yarn feed speed of the first feed roller 62. For this reason, the yarn Y is stretched between the first feed roller 62 and the second feed roller 66. The yarn feed speed of the fourth feed roller 70 is set slower than the yarn feed speed of the third feed roller 68. For this reason, the yarn Y is subjected to a relaxation heat treatment between the third feed roller 68 and the fourth feed roller 70.

  The operation of the false twisting machine 1 until the yarn Y fed from the yarn feeding section 61 is wound up by the winding device 71 will be described. The yarn Y stretched between the first feed roller 62 and the second feed roller 66 is twisted by the false twisting device 65. The false twisting device 65 is, for example, a belt-type nip twister, and twists and feeds the yarn Y with the yarn Y traveling between a pair of belts crossing each other. The twist formed by the false twisting device 65 propagates to the first feed roller 62, and the yarn Y twisted while being drawn is heat-fixed by the first heating device 63 and then cooled by the cooling device 64. The The twisted and heat-fixed yarn Y is untwisted after passing through the false twisting device 65 and reaching the second feed roller 66. By performing air injection with the interlace 67 on the yarn Y that has been subjected to the drawing false twisting in this manner, a partially entangled portion is formed in the yarn Y, and converging properties are imparted. The yarn Y to which the converging property is imparted by the interlace 67 is subjected to relaxation heat treatment by the second heating device 69 and wound by the winding device 71 to form the package P.

  Next, the structure of the main machine base 10 and the winding stand 20 is demonstrated. 2 is a schematic view of the main machine base 10 for one span as viewed from the take-up stand 20 side, and FIG. 3 is a schematic view of the take-up stand 20 for one span as seen from the main machine stand 10 side. In FIGS. 2 and 3, the yarn Y is not shown in order to avoid complication of the drawings.

  As shown in FIG. 2, the main machine base 10 is bridged between a pair of support plates 11 that are spaced apart in the arrangement direction so that the support bracket 12 and the beam members 13 and 14 extend in the arrangement direction. It has a basic configuration. The support bracket 12 is disposed above the support plate 11, the beam member 13 is disposed below the support bracket 12, and the beam member 14 is disposed below the beam member 13. Sixteen false twisting devices 65 are arranged in the support bracket 12, sixteen second feed rollers 66 are arranged in the beam member 13, and sixteen third feed rollers 68 are arranged in the beam member 14 in the arrangement direction. It is attached in the state. In the vertical direction, an interlace 67 is disposed between the beam member 13 and the beam member 14, and a second heating device 69 is disposed below the beam member 14.

  As shown in FIG. 3, the take-up table 20 is bridged between a pair of support plates 21 that are spaced apart in the arrangement direction so that the beam members 22, 23, and 24 extend in the arrangement direction, respectively. It has a basic configuration. One beam member 23 is provided at the upper part of the support plate 21 and one beam member 24 is provided at the lower part of the support plate 21, and four beam members 22 are provided between the beam member 23 and the beam member 24 in the vertical direction. Are arranged at equal intervals. Four winding devices 71 are attached to one beam member 22 in a state of being arranged in the arrangement direction, and the winding table 20 as a whole has a total of 16 (4 × 4 stages) windings. A take-out device 71 can be mounted. Further, 16 first feed rollers 62 are attached to the beam member 23, and 16 fourth feed rollers 70 are attached to the beam member 24 in a state of being arranged in the arrangement direction.

  The main machine base 10 and the take-up base 20 have the same dimensions in the arrangement direction, and a span is formed by arranging them opposite to each other. In this embodiment, as described above, 16 false twisting devices 65, winding devices 71, and 16 feed rollers 62, 66, 68, and 70 are provided in one span, so that 16 threads are arranged in the arrangement direction. A road has been formed.

  Here, the false twisting machine 1 of the present embodiment having a four-stage take-up table 20 (the number of yarn paths of one span is 16), and a conventional take-up table having a three-stage structure (one-span yarn) Consider the case of manufacturing based on a false twisting machine with 12 roads. In this case, it is necessary to increase the number of devices such as the false twisting device 65 and the winding device 71 provided in one span from 12 to 16. The increase in the number of winding devices 71 can be dealt with by increasing the number of stages of the winding table 20 from three to four (increasing the number of beam members 22 from three to four). However, since the false twisting devices 65 are arranged in a line in the arrangement direction, the four increments of the false twisting device 65 are the dimensions of the span in the arrangement direction, in other words, the main machine base 10 and the take-up stand in the arrangement direction. It is necessary to stretch 20 dimensions.

  At this time, if the length in the arrangement direction of the members extending in the arrangement direction (for example, the support bracket 12 and the beam members 13, 14, 22, 23, and 24) is extended, it is orthogonal to the axial direction (matches the arrangement direction). There was a problem that the vibration in the direction to be easily amplified. In particular, the beam members 13, 14, 23, and 24 that support the feed rollers 66, 68, 62, and 70 are likely to be vibrated by the rotation of the feed rollers 66, 68, 62, and 70. 62, 70 are relatively light and the cross-sectional dimensions of the beam members 13, 14, 23, 24 are originally small, so that vibration amplification was significant.

  In order to solve such a problem, it is conceivable to increase the rigidity of the beam members 13, 14, 23 and 24 by increasing the cross-sectional dimensions thereof. However, if the cross-sectional dimensions of the beam members 13, 14, 23, and 24 are increased, the surrounding space is reduced, so that the workability of threading and maintenance is reduced, and the overall size of the machine is increased. . In particular, around the beam members 13 and 14 to which the feed rollers 66 and 68 and the interlace 67 are attached, these accessory parts are densely arranged, so it is difficult to increase the cross-sectional dimensions of the beam members. As for the support bracket 12 and the beam member 22, in order to support the relatively heavy false twisting device 65 and the winding device 71, a high-rigidity member having a large cross-sectional dimension is originally adopted, and vibration amplification is performed. Hard to occur.

  Reduces vibration of beam members 13, 14, 23, and 24 (hereinafter referred to as "beam members 13 etc.") that support feed rollers 66, 68, 62, and 70 (hereinafter referred to as "feed rollers 66 etc."). Therefore, as shown in FIGS. 2 and 3, a dynamic vibration absorber 80 is provided on the beam member 13 or the like. The dynamic vibration absorber 80 is a device that suppresses vibrations in a direction orthogonal to the axial direction of the beam member 13 and the like, and is provided at substantially the center of the beam member 13 and the like. However, the location of the dynamic vibration absorber 80 can be changed as appropriate according to the actual state of vibration.

  FIG. 4 is an exploded perspective view of the dynamic vibration absorber 80, and FIG. 5 is a cross-sectional view orthogonal to the longitudinal direction of the dynamic vibration absorber 80. The dynamic vibration absorber 80 includes a support body 81 extending in the longitudinal direction, a columnar weight 82 supported by the support body 81, and a plurality of O-rings 83 attached to the circumferential surface of the weight 82. The

  The support 81 includes a bottom surface 81a, two inclined surfaces 81b extending from both ends of the bottom surface 81a, and two side surfaces 81c extending from the end of the inclined surface 81b opposite to the connection end with the bottom surface 81a. Consists of. As a result, the support body 81 has a V-shaped cross section orthogonal to the longitudinal direction, and a space for accommodating the weight 82 is formed therein. More specifically, when the bottom surface 81a is horizontally arranged as shown in FIG. 5, the two inclined surfaces 81b are formed so as to spread outward from the both ends of the bottom surface 81a obliquely upward by approximately 45 degrees. The side surface 81c extends along the vertical direction.

  The weight 82 has a cylindrical shape, and is detachably accommodated with respect to the support 81 so that the longitudinal direction thereof coincides with the longitudinal direction of the support 81. A plurality of annular grooves (not shown) are formed in the longitudinal direction on the circumferential surface of the weight 82, and an O-ring 83 is detachable from each annular groove. For this reason, the number of O-rings 83 attached to the weight 82 can be changed. The weight 82 is accommodated in the internal space of the support body 81 in a state of being lifted from the bottom surface 81a and supported by the two inclined surfaces 81b. Note that a slight gap is secured between the O-ring 83 and the side surface 81c, thereby preventing the horizontal displacement of the weight 82 from being constrained.

  Here, the bottom surface 81a of the support member 81 has a role of connecting the two inclined surfaces 81b and functions as an attachment portion when attaching the dynamic vibration absorber 80 to the beam member 13 or the like. However, the bottom surface 81a is not an essential component from the viewpoint of vibration reduction. For example, when the support body 81 is attached to the beam member 13 or the like by the inclined surface 81b or the side surface 81c, the bottom surface 81a can be eliminated. is there. Further, the side surface 81c of the support body 81 prevents the weight 82 from falling when an operator contacts the weight 82 during maintenance or the like or vibrations more than expected are generated. However, similarly to the bottom surface 81a, the side surface 81c is not an essential component from the viewpoint of vibration reduction, and may be omitted.

  When the dynamic vibration absorber 80 is attached to the beam member 13 or the like, the longitudinal direction of the dynamic vibration absorber 80 is disposed so as to coincide with the axial direction of the beam member 13 or the like. Here, the mounting mode of the dynamic vibration absorber 80 provided on the beam members 13 and 14 will be described with reference to FIG. 6, but the mounting mode of the dynamic vibration absorber 80 provided on the beam members 23 and 24 is also fundamental. The same as above.

  6 is a cross-sectional view taken along line VI-VI in FIG. Before describing the mounting mode of the dynamic vibration absorber 80, the specific arrangement and configuration of the feed rollers 66 and 68 will be described. A second feed roller 66 is provided upstream of the interlace 67 in the traveling direction of the yarn Y, and a third feed roller 68 is provided downstream of the traveling direction of the yarn Y. The feed rollers 66 and 68 are respectively disposed below the beam members 13 and 14 which are hollow rectangular tubes.

  The second feed roller 66 includes a driving roller 66A that is rotatably supported by the bracket 91 and a driven roller 66B that is rotatably supported by the bracket 92. The driving roller 66A and the driven roller 66B are in contact with each other, and the yarn Y is nipped at the contact portion. The drive roller 66A is rotated by a motor (not shown), and the drive roller 66A rotates counterclockwise, whereby the driven roller 66B rotates clockwise, and the nipped yarn Y is sent downward.

  Similarly, the third feed roller 68 includes a drive roller 68A that is rotatably supported by a bracket 94 and a driven roller 68B that is rotatably supported by a bracket 95. The driving roller 68A and the driven roller 68B are in contact with each other, and the yarn Y is nipped at the contact portion. The driving roller 68A is rotationally driven by a motor (not shown), and the driving roller 68A rotates counterclockwise, whereby the driven roller 68B rotates clockwise, and the nipped yarn Y is sent downward.

  Here, the interlace 67 includes a nozzle 67a for injecting air to the yarn Y and an air supply part 67b for supplying air to the nozzle 67a, and occupies a large space. ing. Further, traverse devices 101 and 103 for traversing the yarn Y at regular intervals are provided in the vicinity of the beam members 13 and 14 in order to prevent one-point wear on the feed rollers 66 and 68. Further, a support member 102 that supports the pair of left and right traverse devices 101 and a support member 104 that supports the pair of left and right traverse devices 103 are also disposed near the upper portions of the beam members 13 and 14, respectively. As described above, in the main machine base 10 in which various members are arranged at high density, it is very difficult to increase the cross-sectional dimensions of the beam members 13 and 14 in order to reduce vibration. The method of providing is particularly effective.

  Here, the dynamic vibration absorber 80 is fixed to the beam members 13 and 14 so that the two inclined surfaces 81b of the support 81 are inclined by approximately 45 degrees in the opposite directions with respect to the horizontal plane. Specifically, like the dynamic vibration absorber 80 for the beam member 13, the bottom surface 81 a of the support body 81 can be fixed to the upper surface of the beam member 13 through an appropriate bracket 93. Further, like the dynamic vibration absorber 80 for the beam member 14, the bottom surface 81 a of the support body 81 may be directly fixed to the upper surface of the beam member 14. Furthermore, the mounting mode of the support body 81 shown in FIG. 6 is not limited, and the dynamic vibration absorber 80 may be fixed to a portion other than the upper surfaces of the beam members 13 and 14. Sites other than the bottom surface 81 a may be fixed to the beam members 13 and 14. That is, as long as the inclination angle of the two inclined surfaces 81b is approximately 45 degrees, the support 81 may be attached in any way.

  By providing the dynamic vibration absorber 80, the O-ring 83 is compressed and deformed by vibration in a direction orthogonal to the axial direction of the beam member 13 and the like. Due to the deformation of the O-ring 83 existing between the beam member 13 and the like and the weight 82, a time difference is generated between the displacement of the beam member 13 and the like and the displacement of the weight 82, and the vibration energy of the beam member 13 and the like is reduced. It is converted into heat energy and absorbed. At this time, each parameter such as the weight of the weight 82 and the type and number of the O-rings 83 may be determined so as to reduce the vibration of the beam member 13 and the like most effectively. For example, if the parameters are adjusted so that the natural frequency of the dynamic vibration absorber 80 is substantially the same as the natural frequency of the beam member 13 or the like, the vibration of the beam member 13 or the like can be effectively reduced.

  FIG. 7 is a graph showing measured vibration values of the beam member 13 and the like. FIG. 7A shows the vibration speed before the dynamic vibration absorber 80 is provided, and FIG. 7B shows the vibration speed when the dynamic vibration absorber 80 is provided. Here, as the beam member 13 and the like that support the feed roller 66 and the like, the beams 1 to 3 were measured, and the vertical and horizontal components of vibration were measured. In this test, a 100 mm square hollow square material having a length of about 2 m is used as the beams 1 to 3, and the vibration speed when the feed speed of the yarn Y is changed in the range of 0 to 1441 m / min (0 to 85 Hz). Was measured. As a result, as is clear from FIG. 7, by providing the dynamic vibration absorber 80, both vertical and horizontal components have greatly reduced vibration, and the vibration reduction effect by the dynamic vibration absorber 80 can be confirmed.

  As described above, according to the false twisting machine 1 of the present embodiment, the dynamic vibration absorber 80 that suppresses vibration in the direction orthogonal to the axial direction is provided on the beam member 13 and the like that support the feed roller 66 and the like. Yes. Therefore, it is possible to reduce the vibration of the beam member 13 and the like with a simple configuration in which the dynamic vibration absorber 80 is provided without increasing the cross-sectional dimension of the beam member 13 and the like.

  In the present embodiment, the main machine base 10 is provided with an interlace (entanglement device) 67 for entanglement of the yarn Y, and feed rollers 66 and 68 are provided on both sides of the interlace 67 in the traveling direction of the yarn Y. The feed rollers 66 and 68 are supported by different beam members 13 and 14, respectively. Therefore, the tension of the yarn Y in the interlace 67 can be appropriately adjusted by adjusting the speed of the feed rollers 66 and 68. Further, in this configuration, since the interlace 67, the feed rollers 66 and 68, and the beam members 13 and 14 are arranged in the main machine base 10 with high density, the beam members 13 and 14 are changed to those having a large cross-sectional dimension. Is particularly difficult. Therefore, the solution means of providing the dynamic vibration absorber 80 is particularly effective.

  In this embodiment, the dynamic vibration absorber 80 is provided between the support body 81 provided on the beam member 13 and the like, the weight 82 supported by the support body 81, and the support body 81 and the weight 82. And an O-ring (elastic body) 83. According to such a configuration, when the vibration of the beam member 13 and the like is transmitted to the weight 82 via the support body 81 and the O-ring 83, the O-ring 83 is compressed and deformed, so that the vibration energy of the beam member 13 and the like is absorbed. The For this reason, vibrations of the beam member 13 and the like can be effectively reduced.

  In the present embodiment, the support body 81 has two inclined surfaces 81b that are inclined with respect to the horizontal plane in a cross section orthogonal to the axial direction, and the weight 82 is supported by the two inclined surfaces 81b. It is configured. When the weight 82 is supported by the two inclined surfaces 81b as in this configuration, the weight of the weight 82 acts in both the vertical direction and the horizontal direction with respect to the inclined surface 81b. This occurs both in the vertical direction and in the horizontal direction at the portions in contact with the two inclined surfaces 81b. For this reason, among the vibrations in the direction orthogonal to the axial direction of the beam member 13 and the like, both vertical and horizontal components, that is, vibrations in all directions in the plane orthogonal to the axial direction of the beam member 13 and the like are reduced. Can do.

  In the present embodiment, the angle formed by the two inclined surfaces 81b is set to 70 degrees or more and 110 degrees or less. When absorbing vibration energy using the compressive deformation of the O-ring 83 in contact with the inclined surface 81b, if the angle formed by the two inclined surfaces 81b is large, the weight 82 is likely to float along the inclined surface 81b. The direction in which vibration can be reduced is limited. On the other hand, if the angle formed by the two inclined surfaces 81b is small, the weight 82 is sandwiched between the two inclined surfaces 81b and the movement is restricted, so that the ability to absorb vibration energy decreases. Therefore, as in the present embodiment, by setting the angle formed by the two inclined surfaces 81b to 70 degrees or more and 110 degrees or less, the vibration energy is utilized by compressive deformation of the O-ring 83 in contact with each inclined surface 81b. It can be absorbed efficiently without waste.

  In the present embodiment, the two inclined surfaces 81b are inclined by about 35 degrees or more and 55 degrees or less in opposite directions with respect to the horizontal plane. By setting the inclination angle of the inclined surface 81b to about 35 degrees or more, the weight 82 can be prevented from floating from the inclined surface 81b even when the vibration acceleration is increased. Further, by setting the inclination angle of the inclined surface 81b to about 55 degrees or less, it is possible to suppress the movement of the weight 82 between the two inclined surfaces 81b and the movement of the O-ring 83 being sheared and deformed. Absorption of vibration energy is not hindered.

  In particular, in the present embodiment, since the two inclined surfaces 81b are inclined approximately 45 degrees in the opposite directions with respect to the horizontal plane, vibrations can be efficiently shared and absorbed by the inclined surfaces 81b without waste. In addition, the acceleration of vibration that can be reduced can be maximized (approximately 0.7 G). For this reason, the vibration in the direction orthogonal to the axial direction of the beam member 13 or the like can be effectively reduced regardless of the vibration direction.

  Further, in the present embodiment, the weight 82 has a cylindrical shape extending in the axial direction, so that the dimension of the weight 82 in the direction orthogonal to the axial direction of the beam member 13 and the like can be suppressed. For this reason, even if it is a narrow space, arrangement | positioning of the dynamic vibration absorber 80 becomes easy.

  In this embodiment, an O-ring 83 is employed as an elastic body provided in the dynamic vibration absorber 80. By using the O-ring 83 as the elastic body, the contact area between the elastic body 83 and the inclined surface 81b is reduced, the elastic body 83 is easily compressed and deformed, and the vibration reduction effect can be improved. Further, since the O-ring 83 is a general-purpose product and there are a wide variety of types, the elastic modulus and dimensions of the O-ring 83 can be easily changed, and the natural frequency of the dynamic vibration absorber 80 can be easily adjusted. For this reason, it becomes easy to effectively reduce the vibration of the beam member 13 and the like.

  In the present embodiment, a plurality of O-rings 83 can be attached to the weight 82, and each of the plurality of O-rings 83 is configured to be detachable from the weight 82. For this reason, the number of O-rings 83 attached to the weight 82 can be adjusted, and the degree of freedom in adjusting the natural frequency of the dynamic vibration absorber 80 is improved, so that the vibration of the beam member 13 and the like can be more effectively reduced. It becomes easy.

[Other Embodiments]
The present invention is not limited to the above embodiment, and the elements of the above embodiment can be appropriately combined or variously modified without departing from the spirit of the present invention.

  For example, in the above-described embodiment, the case where the dynamic vibration absorber 80 is provided on the beam member 13 that supports the feed roller 66 and the like has been described. However, if vibration may be a problem with the support bracket 12 that supports the false twisting device 65 or the beam member 22 that supports the winding device 71, a dynamic vibration absorber 80 may be provided on the support bracket 12 or the beam member 22. It is.

  It goes without saying that the specific configuration of the dynamic vibration absorber 80 can be changed. For example, a member other than the O-ring 83 may be employed as an elastic body provided between the support body 81 and the weight 82. Further, the elastic body is not limited to the one attached to the weight 82, and may be attached to the support body 81. Further, instead of providing the support 81 separately from the beam member 13 and the like as in the above embodiment, the support 81 may be formed integrally with the beam member 13 and the like.

  In the above embodiment, the dynamic vibration absorber 80 is disposed outside the beam member 13 and the like. However, as shown in FIG. 8, the dynamic vibration absorber 80 is disposed inside the beam member 13 and the like. It may be. If it carries out like this, at the time of arrangement | positioning of the dynamic vibration damper 80, space saving can be achieved. When the dynamic vibration absorber 80 is provided inside the beam member 13 or the like, the beam member 13 is preferably provided with an opening / closing portion 13a so that the weight 82 can be taken out for replacement of the O-ring 83 or the like. .

  Moreover, in the said embodiment, the winding apparatus 71 shall be provided in the winding stand 20 arrange | positioned facing the main machine stand 10. FIG. However, for example, a false twisting machine as described in JP 2012-097369 A, that is, a false twisting machine in which a winding device is provided in a main machine stand and the main machine stand is also used as a take-up stand. The present invention can also be applied to.

1: False twisting machine 10: Main machine stand 20: Winding stand 13, 14, 23, 24: Beam members 62, 66, 68, 70: Feed roller 65: False twisting device 67: Interlace (entanglement device)
71: Winding device 80: Dynamic vibration absorber 81: Support body 81b: Inclined surface 82: Weight 83: O-ring (elastic body)
Y: Yarn

Claims (10)

For each of the plurality of yarn paths formed in the arrangement direction, a false twisting device that falsely twists the yarn, a winding device that winds the yarn falsely twisted by the false twisting device, and a feed roller that feeds the yarn are provided. In false twisting machine,
A main stand that supports the plurality of false twisting devices arranged in the arrangement direction;
A winding stand on which a plurality of the winding devices are mounted;
A beam member extending in the arrangement direction in at least one of the main machine base and the winding base, and supporting the feed roller;
With
A false twisting machine, wherein the beam member is provided with a dynamic vibration absorber that suppresses vibration in a direction orthogonal to the axial direction of the beam member. The main machine base is provided with an entanglement device for entanglement of the yarn, and the feed rollers are provided on both upstream and downstream sides of the running direction of the yarn with respect to the entanglement device,
The false twisting machine according to claim 1, wherein the feed rollers on both sides are supported by the different beam members.   The dynamic vibration absorber includes a support provided on the beam member, a weight supported by the support, and an elastic body provided between the support and the weight. False twisting machine described in 1.   The false twist according to claim 3, wherein the support has two inclined surfaces inclined with respect to a horizontal plane in a cross section perpendicular to the axial direction, and the weight is supported by the two inclined surfaces. Processing machine.   The false twisting machine according to claim 4, wherein an angle formed by the two inclined surfaces is not less than 70 degrees and not more than 110 degrees.   The false twisting machine according to claim 5, wherein each of the two inclined surfaces is inclined in a direction opposite to the horizontal plane by 35 degrees or more and 55 degrees or less.   The false twisting machine according to claim 6, wherein the two inclined surfaces are inclined 45 degrees in opposite directions with respect to a horizontal plane.   The false weight machine according to any one of claims 3 to 7, wherein the weight has a cylindrical shape extending in the axial direction.   The false twisting machine according to claim 8, wherein the elastic body is an O-ring attached to a circumferential surface of the columnar weight.   The false twisting machine according to claim 9, wherein a plurality of the O-rings can be attached to the weight, and each of the plurality of O-rings is detachable from the weight.

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