Stretch texturing machine

Abstract

Stretch texturing machine (1) in which false twist devices (65) designed for false twisting yarns (Y), winding devices (71) designed for winding the false twisted yarns (Y) by the false twist devices (65), and feed rollers (62, 66, 68, 70) designed for feeding the yarns (Y) are provided to correspond to yarn paths which are designed to be set up in a setup direction, wherein the stretch texturing machine (1) comprises: a main frame (10) which supports the false-spin devices (65) positioned in the direction of installation; a winding base (20) on which the winding devices (71) are mounted; one or more support elements (13, 14, 23, 24) provided in the main frame (10) and / or the winding base (20) to extend in the installation direction, each of the support elements (13, 14, 23, 24) supporting the feed rollers (62, 66, 68, 70); and a dynamic vibration damper (80) which is designed to suppress a vibration in a direction orthogonal to an axial direction of the one or more support elements (13, 14, 23, 24), wherein the dynamic vibration damper (80) is provided with respect to at least one of the one or more support elements (13, 14, 23, 24), wherein the dynamic vibration damper (80) comprises: a support device (81) attached to the corresponding support element (13, 14, 23, 24); a weight (82) supported by the support device (81); and an elastic element (83) provided between the support device (81) and the weight (82), and wherein the support device (81) comprises two inclined surfaces (81b) which are inclined to a horizontal plane in a cross-section orthogonal to the axial direction, and the two inclined surfaces (81b) support the weight (82).

Description

BACKGROUND OF THE INVENTION

[0001] The present invention relates to a stretch texturing machine designed for stretch texturing of yarns.

[0002] In a stretch texturing machine described in patent literature 1 (JP 2014-77217 A), for example, a single main frame and a single winding base form a unit called a span, and a plurality of such spans are set up to structure the entire machine. In each span, a plurality of false-twist devices, set up in a single setup direction of the spans (hereinafter simply referred to as a setup direction), are supported by the main frame, and a plurality of winding devices are mounted on the winding base. As a result, a plurality of yarn guides are formed, which are set up in the setup direction in each span of the stretch texturing machine, and this enables the simultaneous production of a plurality of packs of false-twisted yarns.

[0003] DE 10 2010 033 570 A1 relates to a false-twist texturing machine comprising a winding device for yarn, a false-twist device, and a heating device arranged in a main frame. The winding device is arranged on a winding frame in four stages, the winding frame being positioned above a working chamber opposite the main frame. A feed roller is arranged in the winding frame to guide the yarn from a yarn feed section to a further heating device. The latter heating device and a cooling device are arranged in an upper section of the chamber.

[0004] DE 100 60 593 A1 relates to a winding machine. A winding device for synthetic yarns has a rotating head that carries spindles. A pressure roller is supported by a rocker arm equipped with piezoelectric elements, each containing a piezoelectric sensor electrically connected to a piezoelectric actuator. The damping elements can be mounted on other moving parts of the machine.

[0005] DE 42 40 920 A1 relates to a thread winding machine. The winding device for thread onto a spool consists of a machine frame that carries at least one spool holder for holding at least one spool onto which thread spools are wound. The machine frame supports a second frame which has a movable part that carries a roller and to which a dynamic vibration damper is attached. The vibration damper dampens the resonant frequencies of the device.

[0006] DE 37 80 188 T3 refers to a yarn reel, specifically a yarn reel which enables a continuous intake of a synthetic continuous thread spun by a spinning machine at high speed, while avoiding strong spindle vibrations. SUMMARY OF THE INVENTION

[0007] In recent years, there has been a tendency to increase the number of mistwist devices and winding devices provided in a single span to further improve pack production efficiency. This increases the number of mistwist devices positioned in the setup direction, and consequently, the size of each span in that direction also increases. This necessitates extending the lengths of support elements provided in a main frame and winding base to extend in the setup direction. Such an extension adversely increases the likelihood of vibration amplification in a direction orthogonal to the axial direction of the support element. Vibration is particularly likely to occur in the support elements that hold the yarn feed rollers, due to the rotation of these rollers.Because the feed rollers are relatively light, each support element also has a smaller cross-sectional dimension, which makes the vibration amplification resulting from the expansion more noticeable.

[0008] To solve the vibration problem mentioned above, it would be conceivable to increase the cross-sectional dimensions of each support element to enhance its rigidity. However, the mountings for the feed rollers and a braiding unit (braiding device) are located close together in the vicinity of the support element. Therefore, increasing the cross-sectional dimensions of the support element could impair operability during yarn placement and / or maintenance, and could also increase the overall size of the machine. For this reason, increasing the cross-sectional dimensions of the support element has proven difficult.

[0009] In view of the above, it is an object of the present invention to provide a stretch texturing machine which enables a reduction of vibration occurring in a support element for feed rollers without increasing the cross-sectional dimension of the support element.

[0010] The present invention was made to solve the problem described above. According to one embodiment, a stretch texturing machine, comprising false-twist devices designed for false-twisting yarns, winding devices designed for winding the false-twisted yarns by the false-twist devices, and feed rollers designed to feed the yarns to correspond to yarn paths configured to be oriented in an installation direction, comprises: a main frame supporting the false-twist devices oriented in the installation direction; a winding base on which the winding devices are mounted; one or more support elements provided in the main frame and / or the winding base to extend in the installation direction, each of the support elements supporting the feed rollers;and a dynamic vibration damper configured to suppress vibration in a direction orthogonal to an axial direction of one or more support elements, wherein the dynamic vibration damper is provided with respect to at least one of the one or more support elements. The dynamic vibration damper comprises: a support device attached to the corresponding support element; a weight supported by the support device; and an elastic element provided between the support device and the weight. The support device comprises two inclined surfaces inclined to a horizontal plane in a cross-section orthogonal to the axial direction, and the two inclined surfaces support the weight.

[0011] According to the embodiment of the present invention, the dynamic vibration damper, which is designed to suppress vibration in a direction orthogonal to the axial direction of one or more support elements, is provided with respect to at least one of the one or more support elements. Thus, vibration of the at least one support element is reduced by means of a simple arrangement of providing the dynamic vibration damper, without increasing the cross-sectional dimension of the support element.

[0012] Furthermore, the dynamic vibration damper comprises: a support device attached to the corresponding support element; a weight supported by the support device; and an elastic element provided between the support device and the weight.

[0013] With this structure, when a vibration of the support element is transmitted to the weight via the support structure and the elastic element, the elastic element is deformed by compression to absorb the vibration energy of the support element. Thus, vibration of the support element is effectively reduced.

[0014] Furthermore, the support device comprises two inclined surfaces which are inclined to a horizontal plane in a cross-section orthogonal to the axial direction, and the two inclined surfaces support the weight.

[0015] In a structure where the weight is supported by two inclined surfaces, the weight itself is applied to the inclined surfaces in both vertical and horizontal directions. Thus, the elastic element, at its points of contact with the two inclined surfaces, is compressed in both the vertical and horizontal directions. This reduces both the vertical and horizontal components of a vibration in any direction perpendicular to the axial direction of the support element. In other words, vibration is reduced in all directions within a plane perpendicular to the axial direction of the support element.

[0016] The stretch texturing machine is preferably arranged such that: a braiding device, designed to impart entanglement to the yarns, is provided in the main frame; the feed rollers comprise upstream feed rollers and downstream feed rollers, arranged upstream and downstream of the braiding device in a direction of travel of the yarns; and the upstream feed rollers and the downstream feed rollers are each supported by different support elements, which are contained in one or more support elements.

[0017] In this structure, the feed rollers are arranged upstream and downstream of the braiding device in the direction of yarn travel. This allows for suitable adjustment of the yarn tension in the braiding device by modifying the speeds of the feed rollers. Furthermore, in the above structure, the braiding device, the feed rollers, and the support elements are arranged close together within the main frame. This makes it particularly difficult to use a support element with a larger cross-sectional dimension. Therefore, the countermeasure of incorporating a dynamic vibration damper is especially effective.

[0018] According to a further embodiment, a stretch texturing machine comprising false-twist devices designed for false-twisting yarns, winding devices designed for winding the false-twisted yarns by the false-twist devices, and feed rollers designed to feed the yarns to correspond to yarn paths configured to be positioned in an installation direction, comprises: a main frame supporting the false-twist devices positioned in the installation direction; a winding base on which the winding devices are mounted; a support holder extending in the installation direction in the main frame and supporting the false-twist devices; and a support element provided in the winding base to extend in the installation direction, the support element supporting the winding devices.A dynamic vibration damper is provided for at least one of the support brackets and the support element, wherein the dynamic vibration damper is designed to suppress vibration in a direction orthogonal to an axial direction of the at least one of the support brackets and the support element. The dynamic vibration damper comprises: a support device attached to the at least one of the support brackets and the support element; a weight supported by the support device; and an elastic element provided between the support device and the weight. The support device comprises two inclined surfaces inclined to a horizontal plane in a cross-section orthogonal to the axial direction, and the two inclined surfaces support the weight.

[0019] According to yet another embodiment, a stretch texturing machine, comprising false-twist devices designed for false-twisting yarns, winding devices designed for winding the false-twisted yarns by the false-twist devices, and feed rollers designed to feed the yarns to conform to yarn paths configured to be oriented in a setup direction, comprises: a main frame supporting the false-twist devices and the winding devices oriented in the setup direction; and a support element provided in the main frame to extend in the setup direction, the support element supporting the feed rollers. A dynamic vibration damper is provided for at least the support element, the dynamic vibration damper being configured to suppress vibration in a direction orthogonal to an axial direction of the support element.The dynamic vibration damper comprises: a support device attached to the support element; a weight supported by the support device; and an elastic element located between the support device and the weight. The support device includes two inclined surfaces inclined to a horizontal plane in a cross-section orthogonal to the axial direction, and the two inclined surfaces support the weight.

[0020] It is preferred that the angle formed by the two inclined surfaces be not less than 70 degrees and not more than 110 degrees.

[0021] If the angle formed by the two inclined surfaces is larger in this arrangement, where the vibrational energy is absorbed by means of the compressive deformation of the elastic element contacting the inclined surfaces, the weight is more likely to rise along the inclined surfaces, thus limiting the directions in which vibration is reduced. Conversely, if the angle formed by the two inclined surfaces is smaller, the weight is restrained between the two inclined surfaces to limit its movement, which impairs its ability to absorb vibrational energy.By setting the angle formed by the two inclined surfaces to no less than 70 degrees and no more than 110 degrees, the vibration energy is thus efficiently absorbed without any loss, by utilizing the compression deformation of the elastic element touching each of the inclined surfaces.

[0022] It is preferred that the two inclined surfaces are inclined to the horizontal plane in opposite directions, each at an angle of not less than 35 degrees and not more than 55 degrees. Furthermore, it is more preferred that the two inclined surfaces are inclined to the horizontal plane in opposite directions, each at an angle of 45 degrees.

[0023] As described above, to reduce vibration by utilizing the compressive deformation of the elastic element, it is preferred to implement an arrangement designed to prevent, as far as possible, the weight from being separated from the inclined surfaces at high vibration acceleration. Setting the angle of inclination of the inclined surfaces to substantially no less than 35 degrees prevents the weight from being separated from the inclined surfaces at high vibration acceleration. Furthermore, setting the angle of inclination of the inclined surfaces to substantially no more than 55 degrees prevents the restriction of movement of the weight held between the two inclined surfaces and shear deformation of the elastic element. Thus, the absorption of vibration energy is not impeded.In particular, setting the inclination angle of the inclined surfaces at approximately 45 degrees allows the inclined surfaces to efficiently share and absorb the vibration energy without any loss, thus maximizing the reduction of the vibration acceleration. This effectively reduces vibration in a direction orthogonal to the axial direction of the support element, regardless of the direction of the vibration.

[0024] It is preferred that the weight has a substantially cylindrical shape extending in the axial direction.

[0025] The weight, with its essentially cylindrical shape extending in the axial direction, reduces the size of the weight in a direction orthogonal to the axial direction of the support element. This makes it easier to incorporate the dynamic vibration damper even in a small space.

[0026] It is preferred that the elastic element is formed by at least one O-ring attached to a circumferential surface of the weight having a substantially cylindrical shape.

[0027] Using an O-ring as the elastic element reduces the contact area between the elastic element and any inclined surface. This facilitates compression deformation of the elastic element, thereby increasing the vibration reduction effect. Furthermore, O-rings are widely used and available in a large variety. This allows for easy modification of the O-ring's modulus of elasticity and size, simplifying the adjustment of the dynamic vibration damper's natural frequency. This facilitates effective vibration reduction of the supporting element.

[0028] Furthermore, the at least one O-ring comprises a multitude of O-rings that can be attached to and detached from the weight.

[0029] Because the number of O-rings attached to the weight is adjustable, the degree of freedom for adjusting the natural frequency of the dynamic vibration damper is increased. This further enables an effective reduction of the vibration of the support element.

[0030] In the present invention, by providing the dynamic vibration damper in relation to the support element supporting the feed rollers, a vibration occurring in the support element is reduced without increasing the cross-sectional dimension of the support element. BRIEF DESCRIPTION OF THE DRAWINGS Fig. Figure 1 is a front view of a stretch texturing machine of an embodiment of the present invention. Fig. Figure 2 is a schematic representation of a single span of a main frame, viewed from a winding base. Fig. Figure 3 is a schematic representation of a single span of the winding base, as seen from the main frame. Fig. Figure 4 is an exploded view of a dynamic vibration damper. Fig. Figure 5 is a cross-section of the dynamic vibration damper, which is orthogonal to its longitudinal direction. Fig. 6 is a cross-section in section VI-VI in Fig. 2. Fig. 7A and Fig. 7B are diagrams, each showing measured values ​​for a vibration of support elements. Fig. Figure 8 is a cross-section of a dynamic vibration damper in another embodiment, which is orthogonal to its longitudinal direction. DESCRIPTION OF PREFERRED EXECUTION FORMS

[0031] The following will describe an embodiment of the present invention. Fig. Figure 1 is a front view of a stretch texturing machine 1 of an embodiment of the present invention. The stretch texturing machine 1 is designed to produce highly elastic yarns by false twisting thermoplastic synthetic fibers, such as polyester and polyamide, to crimp the fibers.

[0032] As in Fig. As shown in Figure 1, in the stretch texturing machine 1, a single main frame 10 and a single winding base 20, which are opposite each other, form a unit called a span. Two spans are provided symmetrically with respect to the main frame 10. In other words, right and left spans divide the main frame 10 arranged between them. Groups of the two symmetrical spans are arranged in one installation direction (in a direction away from an observer). Fig. 1) set up to train the entire stretch texturing machine 1.

[0033] Within a single span, the following are provided: the main frame 10, the winding base 20 opposite the main frame 10, a support section 30 connecting the main frame 10 to the winding base 20 above the main frame 10 and the winding base 20; and the like. Devices described later are arranged on or around these elements. The main frame 10 is long in the installation direction. The winding base 20 is located opposite the main frame 10 across a working space 40. Opposite the working space 40 with respect to the winding base 20, there is a working space 50 where an operator picks up filled packs P for which winding by the spooling devices 71 provided in the winding base 20 has been completed.

[0034] In a single span, the following are further provided: a yarn feed section 61 opposite the winding base 20 across the working area 50; a plurality of mistwisting devices 65, which are provided in an upper section of the main frame 10 to be arranged in the installation direction; the winding devices 71 provided in the winding base 20; and the like. The yarn feed section 61 is configured to hold a plurality of yarn supply packs S and to feed the yarns Y to the yarn supply packs S. The mistwisting devices 65 are configured to mistwist the yarns Y fed by the yarn feed section 61. The winding devices 71 are configured to wind the yarns Y mistwisted by the mistwisting device 65 onto winders to form packs P. Within a single span, there is the same number of yarn supply packs S, false twist devices 65, spooling devices 71, and the like.Threads of the same number are designed to be aligned in the direction of installation.

[0035] Along the yarn paths from the yarn feed section 61 to the winding devices 71, first feed rollers 62, a first heating device 63, a cooling device 64, the false-twist devices 65, second feed rollers 66, a braiding unit (braiding device) 67, third feed rollers 68, a second heating device 69, and fourth feed rollers 70 are provided in this order from an upstream side in one direction of travel of the yarns Y. In the stretch texturing machine 1, groups of the above devices are arranged symmetrically with respect to the main frame 10 along the yarn paths from the yarn feed section 61 to the winding devices 71.

[0036] The first feed rollers 62 are arranged in an upper section of the winding base 20. The first heating device 63 is arranged above the working area 40. The cooling device 64 is arranged above the working area 40 and closer to the main frame 10 than the first heating device 63. The anti-twist devices 65 are arranged in the upper section of the main frame 10. The second feed rollers 66 are arranged in the main frame 10 and below the anti-twist devices 65. The interlacing unit 67 is arranged in the main frame 10 and below the second feed rollers 66. The third feed rollers 68 are arranged in the main frame 10 and below the interlacing unit 67. The second heating device 69 is arranged in the main frame 10 and below the third feed rollers 68. The fourth feed rollers 70 are arranged in a lower section of the winding base 20.

[0037] The first heating device 63 and the cooling device 64 are arranged above the work area 40 in a substantially linear manner along a horizontal direction, and the yarn guides from the yarn feed section 61 to the winding devices 71 are designed to surround the work area 40. The first heating device 63 and the cooling device 64 are attached to the support section 30. The work area 40 allows an operator to ride on a work trolley (not shown) for yarn placement, to position the yarns Y at a high position near the first heating device 63 and the cooling device 64, and to perform maintenance.

[0038] The feed rollers 62, 66, 68, and 70 are designed to feed the yarns Y from the upstream side to a downstream side in the direction of travel of the yarns Y. The yarn feed speed of the second feed roller 66 is set to be higher than the yarn feed speed of the first feed roller 62. As a result, the yarns Y are drawn between the first feed roller 62 and the second feed roller 66. Furthermore, the yarn feed speed of the fourth feed roller 70 is set to be lower than the yarn feed speed of the third feed roller 68. As a result, the yarns Y are subjected to a stress-relief heat treatment between the third feed roller 68 and the fourth feed roller 70.

[0039] The following describes the operation of the stretch texturing machine 1, from the feeding of yarns Y through the yarn feed section 61 to the winding of the yarns Y by the winding devices 71. The yarns Y drawn between the first feed rollers 62 and the second feed rollers 66 are twisted by the false twist devices 65. Each false twist device 65 is, for example, a belt-type clamp twisting machine designed to twist and feed the corresponding yarn Y between a pair of intersecting belts. Twists formed by the false twist devices 65 reach the first feed rollers 62. The yarns Y, which are twisted as they are drawn, are heat-strengthened by the first heating device 63 and then cooled by the cooling device 64.The yarns Y, twisted to this width and heat-strengthened, are unspun after passing through the false-twist devices 65 and before reaching the second feed rollers 66. Air is expelled from the yarns Y that have been drawn and false-twisted by the braiding unit 67. This causes each yarn Y to have partially braided sections and imparts cohesion to the filaments of the yarn Y. The yarns Y whose filaments have been given cohesion by the braiding unit 67 are subjected to relaxation heat treatment in the second heating device 69 and then wound by the winding devices 71 to form the packs P.

[0040] Now the structures of the main frame 10 and the winding base 20 will be described. Fig. Figure 2 is a schematic representation of a single span of a main frame 10, viewed from the winding base 20. Fig. Figure 3 is a schematic representation of a single span of the winding base 20, as viewed from the main frame 10. It should be noted that the yarns Y in Fig. 2 and Fig. 3 are not shown, for the convenience of viewing the figures.

[0041] As in Fig. As shown in Figure 2, the main frame 10 is basically structured as follows: a pair of support plates 11 are arranged separately in the installation direction; and a support bracket 12 and support elements 13 and 14 each span a space between the support plates 11 to extend in the installation direction. The support bracket 12 is attached to respective upper sections of the support plates 11. The support element 13 is arranged below the support bracket 12, and the support element 14 is arranged below the support element 13. The sixteen false-twist devices 65, arranged in the installation direction, are attached to the support bracket 12. The sixteen second feed rollers 66, arranged in the installation direction, are attached to the support element 13. The sixteen third feed rollers 68, arranged in the installation direction, are attached to the support element 14.Furthermore, the interlacing unit 67 is arranged vertically between the support element 13 and the support element 14. The second heating device 69 is arranged below the support element 14.

[0042] As in Fig. As shown in Figure 3, the winding base 20 is basically structured as follows: a pair of support plates 21 is arranged separately in the installation direction; and each of the support elements 22, 23, and 24 spans a space between the support plates 21 to extend in the installation direction. The support elements 23 and 24, one of each, are attached to the upper and lower sections of the support plates 21, respectively. The four support elements 22 are arranged at equal intervals in the vertical direction between the support element 23 and the support element 24. The four winding devices 71, which are oriented in the installation direction, are attached to each support element 22. Thus, a total of sixteen (4 devices x 4 stages) winding devices 71 can be mounted on the winding base 20. Furthermore, the sixteen first feed rollers 62, which are oriented in the installation direction, are attached to the support element 23.The sixteen fourth feed rollers 70, which are positioned in the installation direction, are attached to the support element 24.

[0043] The main frame 10 and the winding base 20 have the same length in the setup direction, and the main frame 10 and the winding base 20, which are opposite each other, form a span. As described above, in the present embodiment, the sixteen false-twist devices 65, the sixteen winding devices 71, and the sixteen groups of feed rollers 62, 66, 68, 70 are provided in the individual span. Thus, sixteen thread guides are formed to be set up in the setup direction.

[0044] Now, consider the case where the stretch texturing machine 1 of the present embodiment, with winding bases 20 in a four-stage structure (sixteen thread runs per span), is manufactured based on a known stretch texturing machine with winding bases in a three-stage structure (twelve thread runs per span). In this case, the number of different devices per span, such as the false-twist devices 65 and the winding devices 71, must be increased from twelve to sixteen. The increase in the number of winding devices 71 can be achieved by increasing the number of stages in the winding base 20 from three to four (by increasing the number of support elements 22 from three to four).However, because the false twist devices 65 are aligned in a line in the setup direction, it is necessary to extend the length of the span in the setup direction, in other words, it is necessary to extend the lengths of the main frame 10 and the winding base 20 in the setup direction to accommodate the increase in the number of false twist devices 65 by four.

[0045] The extension of the lengths in the installation direction of such elements, which are designed to extend in the installation direction (e.g., the support bracket 12 and the support elements 13, 14, 22, 23, and 24), adversely increases the probability of vibration amplification in a direction orthogonal to its axial direction (corresponding to the installation direction). Vibration is particularly likely to occur in the support elements 13, 14, 23, and 24, which support the feed rollers 66, 68, 62, and 70, due to the rotation of the feed rollers 66, 68, 62, and 70. Because the feed rollers 66, 68, 62, and 70 are relatively light, and therefore each of the support elements 13, 14, 23, and 24 has a small cross-sectional dimension, vibration amplification is also noticeable.

[0046] To solve the problem described above, it is conceivable to increase the cross-sectional dimension of each of the support elements 13, 14, 23, and 24 to enhance its rigidity. However, increasing the cross-sectional dimension of each of the support elements 13, 14, 23, and 24 reduces the space around these elements, which can impair operability during yarn placement and / or maintenance, and can lead to an increase in the overall size of the machine. Particularly in the vicinity of support elements 13 and 14, where the feed rollers 66 and 68 and the braiding unit 67 are located, their mountings are closely spaced. For this reason, increasing the cross-sectional dimension of each support element has proven difficult. It should be noted that the support bracket 12 and the support element 22 support the mistwist devices 65 and winding devices 71, which are relatively heavy.Thus, each of the support bracket 12 and the support element 22 is originally designed to have a larger cross-sectional dimension and high stiffness. Consequently, it is less likely that vibration amplification will occur in these elements.

[0047] To reduce the vibration of the support elements 13, 14, 23 and 24 (hereinafter referred to as "support elements 13 etc.") which support the feed rollers 66, 68, 62 and 70 (hereinafter referred to as "feed rollers 66 etc."), a dynamic vibration damper 80 is provided on each of the support elements 13 etc., as shown in Fig. 2 and Fig. Figure 3 shows that the dynamic vibration damper 80 is designed to suppress vibration in a direction orthogonal to the axial direction of the support elements 13, etc., and is provided at an essentially central section of each of the support elements 13, etc. It should be noted that, depending on the actual vibration situation, the position of each dynamic vibration damper 80 can be changed.

[0048] Fig. Figure 4 is an exploded view of the dynamic vibration damper 80. Fig. Figure 5 is a cross-section of the dynamic vibration damper 80, which is orthogonal to its longitudinal direction. The dynamic vibration damper 80 comprises: a support device 81 extending in the longitudinal direction; a cylindrical weight 82 supported by the support device 81; and a plurality of O-rings 83 attached to a circumferential surface of the weight 82.

[0049] The support device 81 comprises: a base surface 81a; two inclined surfaces 81b, which are provided to extend from both ends of the base surface 81a; and two side surfaces 81c, which are provided to extend from respective ends of the inclined surfaces 81b, the ends being opposite the respective ends of the inclined surfaces 81b that are connected to the base surface 81a. The support device 81 thus has a substantially V-shaped cross-section orthogonal to the longitudinal direction and includes a space for accommodating the weight 82 therein. To be more precise, as in Fig. As shown in Figure 5, assuming that the ground surface 81a is horizontal, the two inclined surfaces 81b extend obliquely upwards and outwards from the two ends of the ground surface 81a in directions of approximately 45 degrees, while the side surfaces 81c extend in the vertical direction.

[0050] The weight 82 has a substantially cylindrical shape and is located inside the support structure 81, allowing it to be attached and detached so that its longitudinal direction coincides with that of the support structure 81. The weight 82 has a plurality of annular grooves (not shown) on its circumferential surface, arranged longitudinally. The O-rings 83 can be attached to and detached from the respective annular grooves. Thus, the number of O-rings 83 attached to the weight 82 is variable. Located inside the support structure 81, the weight 82 is positioned away from the bottom surface 81a and is supported by the two inclined surfaces 81b. Small gaps provided between the O-rings 83 and the side surfaces 81c allow the weight 82 to move horizontally.

[0051] Here, the bottom surface 81a of the support device 81 serves to connect the two inclined surfaces 81b and acts as an attachment point for the dynamic vibration damper 80 when the dynamic vibration damper 80 is attached to each of the support elements 13, etc. However, the bottom surface 81a is not an essential component with regard to vibration reduction. It is possible to omit the bottom surface 81a, for example, if the inclined surface 81b or the side surface 81c acts as the attachment point for attaching the support device 81 to each of the support elements 13, etc. The side surfaces 81c of the support device 81 prevent the weight 82 from falling if an operator touches the weight 82 during maintenance or the like, or if an unexpected vibration occurs.Similar to the bottom surface 81a, the side surfaces 81c are not essential components with regard to reducing vibration, and they can be omitted.

[0052] The dynamic vibration damper 80 is attached to each of the support elements 13, etc., such that the longitudinal direction of the dynamic vibration damper 80 coincides with the axial direction of each of the support elements 13, etc. The following describes the manner of attaching the dynamic vibration damper 80 to each of the support elements 13 and 14 with reference to Fig. 6. It should be noted that the method of attaching the dynamic vibration damper 80 to each of the support elements 23 and 24 is basically identical to this one.

[0053] Fig. 6 is a cross-section in section VI-VI in Fig. 2. Before describing how the dynamic vibration damper 80 is attached, the specific positions and structures of the feed rollers 66 and 68 will be described. The second feed rollers 66 are located upstream of the braiding unit 67 in the direction of travel of the yarns Y, and the third feed rollers 68 are located downstream of the braiding unit 67 in the direction of travel of the yarn Y. The feed rollers 66 and 68 are positioned below the support elements 13 and 14, each of which is a hollow angled tube.

[0054] Every second feed roller 66 comprises: a drive roller 66A, rotatably supported by a holder 91; and a driven roller 66B, rotatably supported by a holder 92. The drive roller 66A and the driven roller 66B are in contact with each other and are designed to clamp the yarn Y between their respective contact sections. The drive roller 66A is driven by a motor (not shown) to rotate the drive roller 66A counterclockwise. This rotates the driven roller 66B clockwise to feed the clamped yarn Y downwards.

[0055] Similarly, every third feed roller 68 comprises: a drive roller 68A, rotatably supported by a holder 94; and a driven roller 68B, rotatably supported by a holder 95. The drive roller 68A and the driven roller 68B are in contact with each other and are designed to clamp the yarn Y between their respective contact sections. The drive roller 68A is driven by a motor (not shown) to rotate it counterclockwise. This rotates the driven roller 68B clockwise to feed the clamped yarn Y downwards.

[0056] The interlacing unit 67 comprises: nozzles 67a, from which air is discharged onto the yarns Y; and an air supply device 67b, configured to supply air to the nozzles 67a. The interlacing unit 67 occupies a large space. Crossing units 101 and 103 are provided in the vicinity of the support elements 13 and 14, configured to allow the yarns Y to pass through them at predetermined time intervals to prevent concentrated wear on the feed rollers 66 and 68. A support element 102, which supports the crossing unit 101 with its counterpart in a pair, and a support element 104, which supports the crossing unit 103 with its counterpart in a pair, are also provided above and around the support elements 13 and 14, respectively.In the main frame 10, in which different types of elements are closely arranged, it is therefore very difficult to increase the cross-sectional dimension of each of the support elements 13 and 14 in order to reduce vibration, and therefore the countermeasure of providing the dynamic vibration damper 80 is particularly effective.

[0057] The dynamic vibration damper 80 is attached to each of the support elements 13 and 14 such that the two inclined surfaces 81b of the support device 81 are inclined to a horizontal plane in opposite directions, each at an angle of approximately 45 degrees. Specifically, as is the case for the dynamic vibration damper 80 for the support element 13, the bottom surface 81a of the support device 81 can be attached to an upper surface of the support element 13 by means of a suitable holder 93. Alternatively, as is the case for the dynamic vibration damper 80 for the support element 14, the bottom surface 81a of the support device 81 can be attached directly to an upper surface of the support element 14. Furthermore, the manner of attaching the support device 81 is not limited to the one described in the Fig. The 6 types shown are limited. The dynamic vibration damper 80 can be attached to a different part of the support element 13, 14 than the upper surface, or a different part of the support device 81 than the bottom surface 81a can be attached to the support element 13, 14. That is, as long as the angle of inclination of each of the two inclined surfaces 81b is approximately 45 degrees, the manner of attaching the support device 81 is not limited.

[0058] The dynamic vibration damper 80 designed in this way functions as follows. A vibration in a direction orthogonal to the axial direction of the corresponding support element (13, etc.) causes the O-rings 83 to compress and deform. The deformation of the O-rings 83, which are located between the support element (13, etc.) and the weight 82, creates a difference between the timing of the displacement of the support element (13, etc.) and the timing of the displacement of the weight 82. Vibrational energy from the support element (13, etc.) is converted by the O-rings 83 into thermal energy, which is then absorbed. Parameters such as the weight of the weight 82 and the type and number of O-rings 83 can be determined to effectively reduce the vibration of the support element (13, etc.).For example, by adjusting the above parameters so that the natural frequency of the dynamic vibration damper 80 is essentially identical to the natural frequency of the support element (13 etc.), vibration of the support element (13 etc.) is effectively reduced.

[0059] Fig. 7A and Fig. 7B are diagrams, each showing measured values ​​for a vibration of the support elements 13 etc. Fig. Figure 7A shows vibration speeds without the dynamic vibration dampers 80, and Fig. Figure 7B shows vibration velocities with the dynamic vibration dampers 80. In this experiment, supports 1 to 3 are used for measurement as support elements 13, etc., which support the feed rollers 66, etc., and vertical and horizontal components of the vibration were measured for each of the supports 1 to 3. In this experiment, each of the supports 1 to 3 was a 100 mm square hollow angled element with a length of approximately 2 m. The vibration velocities were measured at yarn feed speeds Y in a range of 0 to 1441 m / min (0 to 85 Hz). As can be clearly seen from Fig. 7A and Fig. As can be seen in Figure 7B, vibration in both the vertical and horizontal components is greatly reduced in the situation where the dynamic vibration dampers 80 are provided. In this way, the effect of the vibration reduction caused by the dynamic vibration dampers 80 was confirmed.

[0060] As described above, in the stretch texturing machine 1 of the present embodiment, the dynamic vibration damper 80, which is designed to suppress vibration in a direction orthogonal to the axial direction, is provided with respect to each of the support elements 13 etc. supporting the feed rollers 66 etc. Thus, vibration of the support elements 13 etc. is reduced by means of the simple arrangement of providing the dynamic vibration damper 80, without increasing the cross-sectional dimension of each of the support elements 13 etc.

[0061] In the present embodiment, the interlacing unit (interlacing device) 67, which is designed to entangle the yarns Y, is provided in the main frame 10. The feed rollers 66 and 68 are arranged upstream and downstream of the interlacing unit 67 in the direction of travel of the yarns Y, respectively, and are supported accordingly by the support elements 13 and 14, which differ from each other. Thus, the tension of the yarns Y in the interlacing unit 67 can be suitably adjusted by changing the speeds of the feed rollers 66 and 68. Furthermore, in the above structure, the interlacing unit 67, the feed rollers 66 and 68, and the support elements 13 and 14 are arranged closely together in the main frame 10. This makes it particularly difficult to use the support elements 13 and 14 with a larger cross-sectional dimension.Therefore, the countermeasure of providing the dynamic vibration damper 80 is particularly effective.

[0062] Furthermore, in the present embodiment, the dynamic vibration damper 80 comprises: the support device 81, which is attached to the corresponding support element (13, etc.); the weight 82, which is supported by the support device 81; and the O-rings (elastic element) 83, which are provided between the support device 81 and the weight 82. With this structure, when a vibration of the support element (13, etc.) is transmitted to the weight 82 via the support device 81 and the O-rings 83, the O-rings 83 are compressed and deformed to absorb vibrational energy from the support element (13, etc.). Thus, vibration of the support element (13, etc.) is effectively reduced.

[0063] Furthermore, in the present embodiment, the support device 81 comprises two inclined surfaces 81b, which are inclined in cross-section orthogonal to the axial direction with respect to the horizontal plane, and the two inclined surfaces 81b support the weight 82. In the above structure, in which the weight 82 is supported by the two inclined surfaces 81b, the weight of the weight 82 is applied to the inclined surfaces 81b in both the vertical and horizontal directions. Thus, the O-rings 83 are deformed by compression at their respective sections that contact the two inclined surfaces 81b in both the vertical and horizontal directions. This enables a reduction of both the vertical and horizontal components of a vibration in any direction orthogonal to the axial direction of the support element (13, etc.).This means that vibration is reduced in all directions within a plane orthogonal to the axial direction of the support element (13 etc.).

[0064] Furthermore, in the present embodiment, the angle formed by the two inclined surfaces 81b is not less than 70 degrees and not more than 110 degrees. If the angle formed by the two inclined surfaces 81b is larger in this arrangement, where the vibration energy is absorbed by means of the compressive deformation of the O-rings 83 contacting the inclined surfaces 81b, the weight 82 is more likely to rise along the inclined surfaces 81b, thus limiting the directions in which vibration is reduced. Conversely, if the angle formed by the two inclined surfaces 81b is smaller, the weight 82 is restrained between the two inclined surfaces 81b to restrict its movement, which impairs its ability to absorb vibration energy.By setting the angle formed by the two inclined surfaces 81b to not less than 70 degrees and not more than 110 degrees, as is the case in the present embodiment, the vibration energy is thus efficiently absorbed without any loss, by utilizing the compression deformation of the O-rings 83 contacting the inclined surfaces 81b.

[0065] Furthermore, in the present embodiment, the two inclined surfaces 81b are inclined in opposite directions to the horizontal plane, each at an angle of not less than 35 degrees and not more than 55 degrees. Setting the angle of inclination of the inclined surfaces 81b to substantially not less than 35 degrees prevents the weight 82 from being separated from the inclined surfaces 81b under high vibration acceleration. Moreover, setting the angle of inclination of the inclined surface 81b to substantially not more than 55 degrees prevents restriction of the movement of the weight 82 held between the two inclined surfaces 81b and prevents shear deformation of the O-rings 83. Thus, absorption of vibration energy is not impeded.

[0066] In particular, in the present embodiment, the two inclined surfaces 81b are inclined in opposite directions to the horizontal plane, each at an angle of approximately 45 degrees. This allows the inclined surfaces 81b to efficiently share and absorb vibration without any loss, maximizing the reducible acceleration of the vibration (approximately 0.7 G). Thus, vibration in a direction orthogonal to the axial direction of the support element 13, etc., is effectively reduced, regardless of the direction of the vibration.

[0067] Furthermore, in the present embodiment, the weight 82 has a substantially cylindrical shape extending in the axial direction. This reduces the size of the weight in a direction orthogonal to the axial direction of the support element 13, etc. This makes it easier to provide the dynamic vibration damper 80 even in a small space.

[0068] Furthermore, in the present embodiment, the O-rings 83 are used as an elastic element attached to the dynamic vibration damper 80. Using the O-rings 83 as the elastic element reduces the contact area between the elastic element 83 and any inclined surface 81b. This facilitates the compressive deformation of the elastic element 83, thereby increasing the vibration reduction effect. Moreover, O-rings 83 are widely used and available in a variety of types. Therefore, the modulus of elasticity and the size of the O-rings 83 can be easily changed, making it simpler to adjust the natural frequency of the dynamic vibration damper 80. This facilitates an effective reduction of the vibration of the support element 13, etc.

[0069] Furthermore, in the present embodiment, the plurality of O-rings 83 can be attached to and detached from the weight 82. Thus, the number of O-rings 83 attached to the weight 82 is adjustable, which increases the degree of freedom in adjusting the natural frequency of the dynamic vibration damper 80. This further enables an effective reduction of the vibration of the support element 13, etc. [Other embodiments]

[0070] The present invention is not limited to the embodiment described above. Combinations of components of the embodiment described above, as well as various modifications and variations, are possible within the scope of the invention.

[0071] For example, the above embodiment describes the case where the dynamic vibration damper 80 is provided for each of the support elements 13, etc., that support the feed rollers 66, etc. However, if there is a vibration problem with the support holder 12 that supports the false-twist devices 65 and / or the support element 22 that supports the winding devices 71, the dynamic vibration damper 80 can be provided for the support holder 12 and / or the support element 22.

[0072] Furthermore, it is self-evident that the specific structure of the dynamic vibration damper 80 can be modified. For example, an elastic element provided between the support device 81 and the weight 82 is not limited to the O-rings 83. Moreover, such an elastic element need not be attached to the weight 82, but can be attached to the support device 81. Furthermore, instead of the support device 81 of the above embodiment, which is provided separately from the corresponding support element (13, etc.), the support device 81 can be integrated with the corresponding support element (13, etc.).

[0073] In the above embodiment, the dynamic vibration damper 80 is provided outside the corresponding support element (13 etc.); however, the dynamic vibration damper 80 can be provided inside the corresponding support element (13 etc.), as shown in Fig.Figure 8 shows that this arrangement saves space where the dynamic vibration damper 80 is provided. It should be noted that, in the case where the dynamic vibration damper 80 is provided inside the corresponding support element (13, etc.), it is preferred that the support element (13, etc.) has an openable / closable section 13a through which the weight 82 is removed for the purpose of replacing the O-rings 83 or the like.

[0074] Furthermore, in the above embodiment, the winding devices 71 are provided in the winding base 20 opposite the main frame 10. In this respect, the present invention is also applicable to a stretch texturing machine described, for example, in JP 2012-097369 A, in which: winding devices are provided in a main frame; and the main frame also functions as the winding base.

Claims

[1] Stretch texturing machine (1) in which false twist devices (65) designed for false twisting yarns (Y), winding devices (71) designed for winding the false twisted yarns (Y) by the false twist devices (65), and feed rollers (62, 66, 68, 70) designed for feeding the yarns (Y) are provided to correspond to yarn paths which are designed to be set up in a setup direction, wherein the stretch texturing machine (1) comprises: a main frame (10) which supports the false-spin devices (65) positioned in the direction of installation; a winding base (20) on which the winding devices (71) are mounted; one or more support elements (13, 14, 23, 24) provided in the main frame (10) and / or the winding base (20) to extend in the installation direction, each of the support elements (13, 14, 23, 24) supporting the feed rollers (62, 66, 68, 70); and a dynamic vibration damper (80) which is designed to suppress a vibration in a direction orthogonal to an axial direction of the one or more support elements (13, 14, 23, 24), wherein the dynamic vibration damper (80) is provided with respect to at least one of the one or more support elements (13, 14, 23, 24), wherein the dynamic vibration damper (80) comprises: a support device (81) attached to the corresponding support element (13, 14, 23, 24); a weight (82) supported by the support device (81); and an elastic element (83) provided between the support device (81) and the weight (82), and wherein the support device (81) comprises two inclined surfaces (81b) which are inclined to a horizontal plane in a cross-section orthogonal to the axial direction, and the two inclined surfaces (81b) support the weight (82). [2] Stretch texturing machine (1) according to claim 1, wherein: a braiding device (67) configured to entangle the yarns (Y) in which a main frame (10) is provided; the feed rollers (62, 66, 68, 70) comprising upstream feed rollers (66) and downstream feed rollers (68) arranged upstream and downstream of the braiding device (67) in a running direction of the yarns (Y); and the upstream feed rollers (66) and the downstream feed rollers (68) each being supported by different support elements (13, 14) contained in one or more support elements (13, 14, 23, 24). [3] Stretch texturing machine (1) in which false twist devices (65) designed for false twisting yarns (Y), winding devices (71) designed for winding the false twisted yarns (Y) by the false twist devices (65), and feed rollers (62, 66, 68, 70) designed for feeding the yarns (Y) are provided to correspond to yarn paths which are designed to be set up in a setup direction, wherein the stretch texturing machine (1) comprises: a main frame (10) which supports the false-spin devices (65) positioned in the direction of installation; a winding base (20) on which the winding devices (71) are mounted; a support bracket (12) which extends in the installation direction in the main frame (10) and supports the false-twist devices (65); and a support element (22) provided in the winding base (20) to extend in the installation direction, wherein the support element (22) supports the winding devices (71), wherein a dynamic vibration damper (80) is provided for at least one of the support holder (12) and the carrier element (22), wherein the dynamic vibration damper (80) is designed to suppress a vibration in a direction orthogonal to an axial direction of the at least one of the support holder (12) and the carrier element (22), wherein the dynamic vibration damper (80) comprises: a support device (81) attached to at least one of the support holder (12) and the support element (22); a weight (82) supported by the support device (81); and an elastic element (83) provided between the support device (81) and the weight (82), and the support device (81) comprises two inclined surfaces (81b) which are inclined to a horizontal plane in a cross-section orthogonal to the axial direction, and the two inclined surfaces (81b) support the weight (82). [4] Stretch texturing machine (1) in which false twist devices (65) designed for false twisting yarns (Y), winding devices (71) designed for winding the false twisted yarns (Y) by the false twist devices (65), and feed rollers (66, 68) designed for feeding the yarns (Y) are provided to correspond to yarn paths which are designed to be set up in a setup direction, wherein the stretch texturing machine (1) comprises: a main frame (10) that supports the false-twist devices (65) and the spooling devices (71) which are positioned in the installation direction; and a support element (13, 14) provided in the main frame (10) to extend in the installation direction, wherein the support element (13, 14) supports the feed rollers (66, 68); and wherein a dynamic vibration damper (80) is provided for at least the support element (13, 14), wherein the dynamic vibration damper (80) is designed to suppress a vibration in a direction orthogonal to an axial direction of the support element (13, 14), wherein the dynamic vibration damper (80) comprises: a support device (81) attached to the support element (13, 14); a weight (82) supported by the support device (81); and an elastic element (83) provided between the support device (81) and the weight (82), and the support device (81) comprises two inclined surfaces (81b) which are inclined to a horizontal plane in a cross-section orthogonal to the axial direction, and the two inclined surfaces (81b) support the weight (82). [5] Stretch texturing machine (1) according to any one of claims 1 to 4, wherein an angle formed by the two inclined surfaces (81b) is not less than 70 degrees and not more than 110 degrees. [6] Stretch texturing machine (1) according to claim 5, wherein the two inclined surfaces (81b) are inclined to the horizontal plane in opposite directions, each at an angle of not less than 35 degrees and not more than 55 degrees. [7] Stretch texturing machine (1) according to claim 6, wherein the two inclined surfaces (81b) are inclined to the horizontal plane in opposite directions, each at an angle of 45 degrees. [8] Stretch texturing machine (1) according to any one of claims 1 to 7, wherein the weight (82) has a substantially cylindrical shape extending in the axial direction. [9] Stretch texturing machine (1) according to claim 8, wherein the elastic element is formed by at least one O-ring (83) attached to a circumferential surface of the weight (82) having a substantially cylindrical shape. [10] Stretch texturing machine (1) according to claim 9, wherein the at least one O-ring (83) comprises a plurality of O-rings (83) that can be attached to and detached from the weight (82).

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