Guide wire body and wire coiler

Abstract

The present application relates to a guide thread body and a thread winder, capable of suppressing a change in thread quality at low cost. The guide thread body (16) has a fulcrum guide (31) that becomes a fulcrum when a thread is wound on a bobbin while being traversed, wherein the fulcrum guide (31) has a cylindrical shape and is rotatable around a center axis, the guide thread body (16) is provided with a rotation resistance application mechanism (37) that applies a rotation resistance to the fulcrum guide (31) to cause the fulcrum guide (31) to perform driven rotation at a peripheral speed slower than a traveling speed of the thread in a case where the thread that travels while contacting an outer peripheral surface of the fulcrum guide (31) on one side receives a torque of a prescribed value or more.

Description

Technical Field

[0001] The present invention relates to a guide wire body and a wire winding machine having the guide wire body, the guide wire body having a fulcrum guide that serves as a fulcrum when winding the wire into a bobbin while moving it laterally. Background Technology

[0002] It has long been known that a yarn winding machine is used to wind yarn spun from a spinning device onto a bobbin while moving it laterally. Such a yarn winding machine includes a fulcrum guide that serves as the fulcrum for the lateral movement of the yarn. For example, in Patent Documents 1 and 2, a cylindrical fulcrum guide (a guide roller in Patent Document 2) is provided, and the yarn is hooked onto the outer circumferential surface of the fulcrum guide.

[0003] In Patent Document 1, the fulcrum guide is configured not to rotate around a central axis during yarn winding. Therefore, the high-speed traveling yarn continuously contacts the same portion of the outer peripheral surface of the fulcrum guide, making localized wear within the fulcrum guide prone to develop. Consequently, the contact state between the yarn and the fulcrum guide changes, potentially leading to a decrease in yarn quality. Therefore, Patent Document 1 is configured such that the fulcrum guide can be rotated by a motor, allowing for a change in the contact position with the yarn. However, Patent Document 1 requires a drive unit such as a motor to rotate the fulcrum guide, thus increasing costs.

[0004] On the other hand, in Patent Document 2, the fulcrum guide is a roller capable of rotating freely around a central axis. Therefore, during yarn winding, the fulcrum guide rotates continuously through friction with the yarn, suppressing localized wear. Furthermore, by using a freely rotating roller, a drive unit for rotating the fulcrum guide is unnecessary, thus reducing costs.

[0005] Patent Document 1: Japanese Patent Application Publication No. 2013-23787

[0006] Patent Document 2: Japanese Patent Publication No. 2008-531438

[0007] However, in Patent Document 2, the pivot guide requires a precision bearing construction to withstand high-speed rotation. Precision bearing construction is prone to deterioration, resulting in a decrease in the pivot guide's rotational speed during yarn winding, which could potentially lead to unexpected changes in yarn quality. Summary of the Invention

[0008] In view of the above issues, the object of the present invention is to provide a guide body that can suppress changes in yarn quality at a low cost.

[0009] The present invention is a wire guide body having a fulcrum wire guide that serves as a fulcrum when winding a wire onto a bobbin while moving laterally. The wire guide body is characterized in that the fulcrum wire guide has a cylindrical shape and is rotatable about a central axis. The wire guide body is provided with a rotational resistance application mechanism. When the fulcrum wire guide receives a torque of more than a predetermined value from the wire traveling while contacting the outer peripheral surface of the fulcrum wire guide, the rotational resistance application mechanism applies rotational resistance to the fulcrum wire guide so that the fulcrum wire guide rotates passively at a circumferential speed slower than the traveling speed of the wire.

[0010] According to the present invention, the fulcrum guide rotates passively when receiving a torque exceeding a predetermined value from the yarn, thus allowing variation in the portion of the fulcrum guide in contact with the yarn on its outer circumferential surface, thereby suppressing localized wear of the fulcrum guide. Furthermore, since no drive unit such as a motor is required to rotate the fulcrum guide, costs can be reduced. Moreover, by applying a rotational resistance mechanism, the fulcrum guide rotates at a circumferential speed slower than the yarn's travel speed, ensuring that the frictional characteristics between the fulcrum guide and the yarn remain almost constant compared to the case where the fulcrum guide is fixed. Therefore, even slight variations in the rotational speed of the fulcrum guide can suppress changes in yarn quality. As described above, according to the present invention, variations in yarn quality can be suppressed at low cost.

[0011] In this invention, the aforementioned rotational resistance applying mechanism may apply rotational resistance to the aforementioned fulcrum guide wire, so that the circumferential speed of the aforementioned fulcrum guide wire is preferably less than 5% of the traveling speed of the aforementioned wire, more preferably less than 3.5%.

[0012] If the circumferential speed of the fulcrum guide is slow enough to be less than 5% of the yarn's travel speed, then changes in yarn quality can be suppressed more effectively.

[0013] In this invention, the aforementioned rotational resistance applying mechanism may apply rotational resistance to the aforementioned pivot wire guide so that the rotational speed of the aforementioned pivot wire guide is preferably 7400 rpm or less, more preferably 5000 rpm.

[0014] When the pivot wire guide rotates at a high speed, the pivot wire guide and other components in contact with it are prone to wear, which may hinder the smooth rotation of the pivot wire guide. Therefore, as mentioned above, by reducing the rotation speed of the pivot wire guide to below 7400 rpm, the wear of the pivot wire guide and other components in contact with it can be suppressed, allowing the pivot wire guide to rotate smoothly and continuously.

[0015] In this invention, the rotational resistance applying mechanism may include: a pressed portion disposed on one side of the axial direction of the fulcrum guide wire; and a pressing member that presses the fulcrum guide wire toward the pressed portion.

[0016] With this configuration, rotational resistance can be applied to the fulcrum wire guide by the pressing force of the pressing component.

[0017] In this invention, a clamping member may be provided between the fulcrum guide wire guide and the pressed part and / or between the fulcrum guide wire guide and the pressing member.

[0018] Based on this configuration, the pressing force applied to the fulcrum wire guide can be adjusted by changing the shape, size, and material of the clamping components, making it easy to adjust the rotational speed and circumferential speed of the fulcrum wire guide.

[0019] In this invention, the clamping component may include: a thrust bearing portion that abuts against the end face of the fulcrum wire guide; and a radial bearing portion that abuts against the inner circumferential surface of the fulcrum wire guide.

[0020] By incorporating a thrust bearing and a radial bearing in the clamping components, the fulcrum wire guide can rotate more smoothly.

[0021] In this invention, the pressing component can be a spring.

[0022] By using a spring as the pressing component, the pressing force applied to the fulcrum wire guide can be easily adjusted, as can the rotational speed and circumferential speed of the fulcrum wire guide.

[0023] In this invention, the pressing portion may be integrally formed on a shaft component that supports the fulcrum guide and is rotatable.

[0024] With this configuration, the guidewire can be manufactured with a smaller number of components.

[0025] In this invention, the aforementioned rotational resistance applying mechanism may be a contact portion formed between other components that contact the aforementioned fulcrum guide and the aforementioned fulcrum guide, wherein the frictional force in the aforementioned contact portion is adjusted such that the circumferential speed of the aforementioned fulcrum guide is slower than the traveling speed of the aforementioned wire.

[0026] With this configuration, the aforementioned pressing component is not required, and the guide wire can be manufactured with a smaller number of components.

[0027] In this invention, the contact portion, which serves as the aforementioned rotational resistance application mechanism, may be formed between the inner circumferential surface of the fulcrum guide and other components that are in contact with the inner circumferential surface of the fulcrum guide.

[0028] Generally, the area of ​​the inner circumferential surface of the pivot wire guide is larger than the area of ​​the end face. Therefore, by using the inner circumferential surface of the pivot wire guide as a mechanism for applying rotational resistance, the friction force can be easily adjusted.

[0029] In this invention, a clamping member may be disposed between the shaft component that supports the fulcrum guide as a rotatable component and the fulcrum guide, and the contact portion that serves as the rotational resistance application mechanism is formed between the inner circumferential surface of the fulcrum guide and the clamping member.

[0030] Based on this configuration, the friction of the contact part can be adjusted by changing the shape, size, and material of the clamping components, making it easy to adjust the rotational speed and circumferential speed of the fulcrum wire guide.

[0031] The present invention is a wire winding machine that winds multiple wires on multiple bobbins mounted on a winding shaft, characterized in that multiple guide bodies of any of the above are arranged axially on the winding shaft.

[0032] With such a yarn winding machine, it is possible to suppress changes in yarn quality at a low cost. Attached Figure Description

[0033] Figure 1 This is a side view of the spinning traction device of this embodiment.

[0034] Figure 2 This is a side view of the guidewire unit.

[0035] Figure 3 This is a cross-sectional view of the guidewire.

[0036] Figure 4 This is a graph showing the results of a verification experiment on the physical properties of the silk thread.

[0037] Figure 5 This is a cross-sectional view of the guide wire in a modified example.

[0038] Figure 6 This is a graph showing the results of a verification experiment for a modified example.

[0039] Explanation of symbols

[0040] 10: Thread winding machine; 13: Boll tube support (winding shaft); 16: Thread guide body; 31: Pivot guide; 33a: Shaft; 33b: Flange (pressed part); 34, 35: Clamping parts; 34a, 35a: Thrust bearing parts; 34b, 35b: Radial bearing parts; 36: Spring (pressing part); 37: Rotational resistance application mechanism; 41, 42: Contact parts (rotational resistance application mechanism); B: Boll tube; Y: Thread. Detailed Implementation

[0041] Hereinafter, with reference to the accompanying drawings, an embodiment of applying a yarn winding machine having the guide body of the present invention to a spinning traction device will be described.

[0042] (Spinning traction device)

[0043] Figure 1 This is a side view of the spinning traction device 1 according to this embodiment. In this specification, [the following will be described]. Figure 1 The directions shown are defined as front, back, left, right, up, and down of the spinning traction device 1.

[0044] The spinning traction device 1 is a device for drawing multiple (16 in this embodiment) filaments Y spun from the spinning device 2, and includes guide rollers 3 and 4 and a filament winding machine 10. The spinning device 2 is positioned above the spinning traction device 1 and spins multiple filaments Y formed of synthetic resin. The guide rollers 3 and 4 are positioned below the spinning device 2 and are driven to rotate by a motor (not shown). The multiple filaments Y spun from the spinning device 2 are conveyed to the filament winding machine 10 via the guide rollers 3 and 4.

[0045] The thread winding machine 10 is positioned below the guide rollers 3 and 4. The thread winding machine 10 has two bobbin supports 13 (the winding shafts of the present invention) cantilevered by a turntable 12 built into the machine body 11. The bobbin supports 13 extend in the front-rear direction, and their rear ends are supported by the turntable 12. Multiple bobbins B can be mounted on the bobbin supports 13 in the front-rear direction. The bobbin supports 13 are driven to rotate about an axis by a motor (not shown).

[0046] The turntable 12 is a circular plate-shaped component with a rotation axis parallel to the front-rear direction. Two bobbin supports 13 are mounted at an upper position and a lower position, 180 degrees apart in the circumferential direction. By rotating the turntable 12, the two bobbin supports 13 move between the upper and lower positions. In the upper position of the bobbin support 13, multiple threads Y are wound onto multiple bobbins B to form multiple rolls P. Conversely, in the lower position of the bobbin support 13, the multiple rolls P are retrieved and new multiple bobbins B are installed.

[0047] The thread winding machine 10 has a support frame 14 cantilevered and supported by the machine body 11. The rear end of the support frame 14 is supported by the machine body 11. A guide unit 15 is arranged above the support frame 14. The guide unit 15 has a number of guide bodies 16 arranged in the front-back direction, the same number as the number of threads Y. The support frame 14 has a number of traverse devices 17 arranged in the front-back direction, the same number as the number of threads Y. The traverse devices 17 use the corresponding guide bodies 16 as fulcrums to traverse the threads Y in the front-back direction.

[0048] A contact roller 18, supported by the support frame 14 and capable of rotation, is disposed below the support frame 14. The contact roller 18 contacts the outer peripheral surfaces of a plurality of packages P held by the upper bobbin support 13. During yarn winding, the contact roller 18 rotates while applying a predetermined contact pressure to the packages P, thereby adjusting the shape of the packages P.

[0049] (guidewire unit)

[0050] The structure of the guide wire unit 15 will be explained. Figure 2 This is a side view of the guidewire unit 15. Figure 2 Figure (a) shows the state of multiple guidewires 16 in the winding position. Figure 2 Figure (b) shows the state of multiple guide wire bodies 16 in the wire-hanging position. The winding position refers to the position of the multiple guide wire bodies 16 when multiple bobbins B wind up multiple wires Y. The wire-hanging position refers to the position of the multiple guide wire bodies 16 when they hook multiple wires Y. The multiple guide wire bodies 16 are configured to move between the winding position and the wire-hanging position.

[0051] The wire guide unit 15 includes multiple wire guides 16, multiple sliders 21, a guide rail 22, and a cylinder 23. The same number of sliders 21 as the number of wire guides 16 are provided, with each wire guide 16 mounted on a corresponding slider 21. The guide rail 22 is a component extending in the front-to-back direction and is fixed to the support frame 14 via a bracket (not shown). Multiple sliders 21 are slidably mounted on the guide rail 22 in a front-to-back arrangement. Adjacent sliders 21 are connected to each other by a belt (not shown). The cylinder 23 is a drive device for moving the multiple wire guides 16 between a winding position and a wire-hanging position. The rod 23a of the cylinder 23 is connected to the last slider 21. However, the drive device for moving the multiple wire guides 16 is not limited to the cylinder 23; it can also be other actuators such as a motor.

[0052] like Figure 2 As shown in Figure (a), when the rod 23a of cylinder 23 retracts, multiple sliders 21 are arranged in a separated state along the front-back direction. At this time, the positions of the multiple guide wires 16 are the winding positions. On the other hand, as... Figure 2 As shown in Figure (b), when the rod 23a of cylinder 23 extends, multiple sliders 21 gather at the front end of guide rail 22. At this time, the multiple guide wire bodies 16 are in the wire-hanging position.

[0053] like Figure 2As shown in Figure (a), the thread channels for multiple threads Y distributed from the guide roller 4 to the multiple guide bodies 16 located at the winding position are approximately symmetrical in the front-back direction with respect to the vertical plane passing through the center of the multiple guide bodies 16. The front half of the eight threads Y are hooked on the front side of the guide body 16, and the rear half of the eight threads Y are hooked on the rear side of the guide body 16. Furthermore, the closer the guide body is to the end of the multiple guide bodies 16, the larger the contact angle (winding angle) with the thread Y, and the closer the guide body is to the center, the smaller the contact angle (winding angle) with the thread Y.

[0054] (guidewire)

[0055] The details of guidewire 16 are explained below. Figure 3 This is a cross-sectional view of the wire guide 16. The wire guide 16 has a pivot wire guide 31, a fixing member 32, and a shaft member 33. The pivot wire guide 31 has a cylindrical shape extending in the left-right direction and is supported by the shaft member 33 so that it can rotate about a central axis. The wire Y is hooked on the outer peripheral surface of the pivot wire guide 31 and travels in contact with the outer peripheral surface of the pivot wire guide 31 during wire winding. The pivot wire guide 31 is driven to rotate at a circumferential speed slower than the traveling speed of the wire Y when it receives a torque of more than a predetermined value from the wire Y traveling while in contact with the outer peripheral surface of the pivot wire guide 31.

[0056] The fixing member 32 has a small-diameter portion 32a in the shape of a cylinder and a large-diameter portion 32b in the shape of a cylinder. The small-diameter portion 32a is inserted into a circular mounting hole 21a formed on the slider 21. An annular recess 32c is formed at the right end of the large-diameter portion 32b. A spring 36 (the pressing member of the present invention) is disposed in the recess 32c. An internal thread 32d extending in the left-right direction is formed on the fixing member 32. The fixing member 32 is fixed to the slider 21 by a bolt (not shown) with the small-diameter portion 32a inserted from the right side of the mounting hole 21a and the flange surface of the large-diameter portion 32b abutting against the slider 21.

[0057] The shaft component 33 is a component integrally formed with a shaft portion 33a and a flange portion 33b (the pressing portion of the present invention). The shaft portion 33a has a cylindrical shape extending in the left-right direction. The shaft portion 33a supports the pivot wire guide 31, which is externally fitted into the shaft portion 33a, so that it can rotate. The flange portion 33b is an annular portion extending radially outward from the right end of the shaft portion 33a. A through hole 33c extending in the left-right direction is formed on the shaft component 33. The right end of the through hole 33c has a tapered surface 33d that increases in inner diameter towards the right and is formed for the head of the bolt 39 to abut.

[0058] On both sides of the axial direction of the pivot wire guide 31, resin clamping members 34 and 35 are disposed adjacent to the pivot wire guide 31. The clamping members 34 and 35 are annular components with an L-shaped cross-section, having thrust bearing portions 34a and 35a extending radially along the pivot wire guide 31, and radial bearing portions 34b and 35b extending axially along the pivot wire guide 31. By providing such resin clamping members 34 and 35, wear on the pivot wire guide 31 and the shaft component 33 can be suppressed. Furthermore, the clamping members 34 and 35 may be made of POM (polyacetal), for example.

[0059] The thrust bearing portion 34a of the right-side clamping member 34 is positioned axially between the fulcrum guide 31 and the flange portion 33b of the shaft member 33, abutting against the right end face of the fulcrum guide 31. The thrust bearing portion 35a of the left-side clamping member 35 is positioned axially between the fulcrum guide 31 and the spring 36, abutting against the left end face of the fulcrum guide 31. The radial bearing portions 34b and 35b are positioned radially between the fulcrum guide 31 and the shaft portion 33a of the shaft member 33, abutting against the inner circumferential surface of the fulcrum guide 31.

[0060] With the pivot wire guide 31 externally fitted onto the shaft component 33, when a bolt 39 is inserted into the through hole 33c and tightened into the internal thread 32d of the fixing component 32, the shaft component 33 is fixed to the fixing component 32. At this time, the pivot wire guide 31 is pressed toward the flange 33b by the force applied by the spring 36 disposed in the recess 32c of the fixing component 32.

[0061] Previously, the yarn continuously contacted the same portion of the outer circumference of the fulcrum guide. To avoid localized wear on the fulcrum guide, fulcrum guides that could rotate freely—that is, rotate at a circumferential speed approximately the same as the yarn's travel speed—were commonly used. However, using freely rotating fulcrum guides requires precision bearing structures such as ball bearings. As the bearing structure deteriorates, the rotational speed of the fulcrum guide may decrease during yarn winding. Consequently, the yarn quality may unexpectedly change.

[0062] To avoid such changes in yarn quality, this embodiment includes a rotational resistance application mechanism 37 that applies rotational resistance to the fulcrum guide 31, ensuring that the circumferential speed of the fulcrum guide 31 is slower than the travel speed of the yarn Y. The rotational resistance application mechanism 37 is adjusted so that when the fulcrum guide 31 receives a torque exceeding a predetermined value from the yarn Y, it drives the fulcrum guide 31 to rotate at a circumferential speed slower than the travel speed of the yarn Y. Specifically, the rotational resistance application mechanism 37 consists of a spring 36 and a flange 33b of the shaft member 33. The spring 36 presses the fulcrum guide 31 towards the flange 33b, thereby increasing the frictional resistance during rotation of the fulcrum guide 31 and applying rotational resistance. As a result, the rotational speed of the fulcrum guide 31 can be reduced.

[0063] The magnitude of the rotational resistance applied to the fulcrum guide 31 can be adjusted by changing the clamping components 34, 35 or the spring 36. Alternatively, the applied force generated by the spring 36 can be adjusted by placing a washer at an appropriate position between the recess 32c of the fixing component 32 and the flange 33b of the shaft component 33. The circumferential speed of the fulcrum guide 31 is preferably adjusted to 5% or less, more preferably 3.5% or less, of the travel speed of the wire Y by the rotational resistance application mechanism 37. Alternatively, the rotational speed of the fulcrum guide 31 is preferably adjusted to 7400 rpm or less, more preferably 5000 rpm or less by the rotational resistance application mechanism 37.

[0064] By rotating the fulcrum guide 31 slowly at a low speed, the frictional characteristics between the fulcrum guide 31 and the yarn Y remain almost constant compared to the case where the fulcrum guide 31 is fixed. Therefore, even if the rotational speed of the fulcrum guide 31 varies slightly during the winding of the yarn Y, significant changes in yarn quality can be avoided. Furthermore, when the rotational speed of the fulcrum guide 31 is low, a precision bearing structure such as a ball bearing is not required, and a simple bearing structure such as a sliding bearing can be used, thus further reducing costs.

[0065] Additionally, the guide wire 16 with a larger contact angle (winding angle) with the wire Y (refer to the guide wire near the end among the multiple guide wires 16) Figure 2 In this process, the friction between the yarn Y and the fulcrum guide 31 is relatively large. Therefore, the torque acting on the fulcrum guide 31 from the very beginning exceeds the aforementioned specified value, and the fulcrum guide 31 often rotates passively at a circumferential speed slower than the travel speed of the yarn Y. However, the guide body 16 (the guide body near the center among multiple guide bodies 16, see reference 16) has a smaller contact angle (winding angle) with the yarn Y. Figure 2In this configuration, the friction between the yarn Y and the fulcrum guide 31 is relatively small. Therefore, sometimes the torque acting on the fulcrum guide 31 will not exceed the aforementioned specified value. However, this is not particularly problematic.

[0066] Assuming that the torque acting on the fulcrum guide 31 due to friction with the yarn Y does not reach the aforementioned predetermined value—that is, when the fulcrum guide 31 does not rotate due to the movement of the yarn Y—the yarn Y continues to contact the same portion of the outer peripheral surface of the fulcrum guide 31, resulting in localized wear. When the fulcrum guide 31 wears, the friction between it and the yarn Y increases, the torque acting on the fulcrum guide 31 reaches the aforementioned predetermined value, and the fulcrum guide 31 rotates slightly. Then, when the yarn Y contacts the unworn portion of the fulcrum guide 31, the fulcrum guide 31 again stops rotating. Even with this behavior of the fulcrum guide 31, changes in yarn quality caused by the continuous contact of the yarn Y with the worn portion of the fulcrum guide 31 can be suppressed.

[0067] (Experiment to verify the physical properties of the silk thread)

[0068] Using the guide wire 16 of this embodiment, an experiment was conducted to verify whether changes in the quality of the yarn were actually suppressed. Specifically, the following was verified: when rotational resistance was applied by the rotational resistance application mechanism 37, and the fulcrum guide 31 was rotated by the movement of the yarn Y, compared to when the fulcrum guide 31 was fixed, whether the changes in the physical parameters of the yarn Y, such as tension, strength, and elongation, remained unchanged. The yarn Y used in the experiment had a thickness of 83 dtex, and the outer diameter of the fulcrum guide 31 was 10 mm. When the travel speed of the yarn Y was set to 4600 m / min, the rotational speed of the fulcrum guide 31 was 120 rpm, and the circumferential speed was 3.8 m / min (0.08% of the travel speed of the yarn Y).

[0069] Figure 4 This is a graph showing the results of verification experiments on the physical properties of the yarn. The numbers recorded in each bar chart represent average values. Regarding strength and elongation, there are also correlations with the bar chart. Figure 1The diagram illustrates the deviation. "No rotation" indicates the case where the fulcrum guide 31 is fixed, and "rotation" indicates the case where the fulcrum guide 31 is rotated passively while rotational resistance is applied by the rotational resistance application mechanism 37. Regardless of the physical properties of the yarn, there is almost no difference compared to the case where the fulcrum guide 31 is fixed, and deviations in yarn quality are suppressed. Based on these experimental results, it can be said that by applying rotational resistance to the fulcrum guide 31 to make it rotate at a low speed, changes in yarn quality during yarn winding can be suppressed. Furthermore, the application scope of the present invention is not limited to the scope of its effectiveness verified in this verification experiment. For example, if the circumferential speed of the fulcrum guide 31 is less than 5% of the travel speed of the yarn Y, changes in yarn quality during yarn winding can be sufficiently suppressed. In addition, under the conditions of this verification experiment, when the circumferential speed of the fulcrum guide 31 is 5% of the travel speed of the yarn Y, the rotational speed of the fulcrum guide 31 is approximately 7400 rpm.

[0070] (Effect)

[0071] In this embodiment, the fulcrum guide 31 rotates passively when it receives a torque exceeding a predetermined value from the yarn Y. Therefore, the portion of the fulcrum guide 31 in contact with the yarn Y can be varied on its outer circumferential surface, suppressing localized wear of the fulcrum guide 31. Furthermore, a drive unit such as a motor for rotating the fulcrum guide 31 is not required, thus reducing costs. Moreover, the fulcrum guide 31 is rotated at a circumferential speed slower than the travel speed of the yarn Y by the rotational resistance application mechanism 37. As a result, the frictional characteristics between the fulcrum guide 31 and the yarn Y remain almost constant compared to the case where the fulcrum guide 31 is fixed. Therefore, even slight variations in the rotational speed of the fulcrum guide 31 can suppress changes in yarn quality. Thus, variations in yarn quality can be suppressed at low cost.

[0072] In this embodiment, the rotational resistance applying mechanism 37 applies rotational resistance to the fulcrum guide 31 so that the circumferential speed of the fulcrum guide 31 is preferably less than 5% of the travel speed of the yarn Y, more preferably less than 3.5%. If the circumferential speed of the fulcrum guide 31 is slow enough to be less than 5% of the travel speed of the yarn Y, changes in yarn quality can be suppressed more effectively.

[0073] In this embodiment, the rotational resistance applying mechanism 37 applies rotational resistance to the pivot guide 31 so that the rotational speed of the pivot guide 31 is preferably 7400 rpm or less. When the rotational speed of the pivot guide 31 is high, the pivot guide 31 and other components in contact with it are prone to wear, which may hinder the smooth rotation of the pivot guide 31. Therefore, as described above, by keeping the rotational speed of the pivot guide 31 below 7400 rpm, wear on the pivot guide 31 and other components in contact with it can be suppressed, and the pivot guide 31 can continue to rotate smoothly.

[0074] In this embodiment, the rotational resistance application mechanism 37 has a flange portion 33b (pressed portion) disposed on one side of the axial direction of the pivot wire guide 31, and a spring 36 (pressing member) that presses the pivot wire guide 31 toward the flange portion 33b. With this configuration, rotational resistance can be applied to the pivot wire guide 31 by the pressing force generated by the spring 36.

[0075] In this embodiment, clamping members 34 and 35 are arranged between the fulcrum guide 31 and the flange portion 33b, and between the fulcrum guide 31 and the spring 36. With this configuration, the pressing force acting on the fulcrum guide 31 can be adjusted by the shape, size, material, etc. of the clamping members 34 and 35, and the rotational speed and circumferential speed of the fulcrum guide 31 can be easily adjusted.

[0076] In this embodiment, the clamping members 34 and 35 have thrust bearing portions 34a and 35a that abut against the end face of the fulcrum guide 31, and radial bearing portions 34b and 35b that abut against the inner circumferential surface of the fulcrum guide 31. By providing thrust bearing portions 34a and 35a and radial bearing portions 34b and 35b in the clamping members 34 and 35, the fulcrum guide 31 can rotate more smoothly.

[0077] In this embodiment, the pressing component is a spring 36. By using a spring 36 as the pressing component, the pressing force acting on the fulcrum guide 31 can be easily adjusted, as can the rotational speed and circumferential speed of the fulcrum guide 31.

[0078] In this embodiment, a flange 33b is integrally formed on the shaft member 33 that supports the fulcrum guide wire 31 so that it can rotate. With this configuration, the guide wire body 16 can be manufactured with a smaller number of components.

[0079] (Other implementation methods)

[0080] This section describes variations of the above-described implementation with various modifications.

[0081] In the above embodiments, a shaft portion 33a and a flange portion 33b corresponding to the pressed portion of the present invention are integrally formed on the shaft member 33 of the present invention. However, the pressed portion of the present invention may also be configured as a different component from the shaft portion 33a. Furthermore, the shaft portion 33a may also be integrally formed with the fixing member 32. In this case, the fixing member 32 corresponds to the shaft member of the present invention.

[0082] In the above embodiment, the pressing member of the present invention is constituted by a spring 36. However, the pressing member may also be constituted by an elastomer such as an O-ring.

[0083] In the above embodiment, the spring 36 is disposed in the recess of the fixing member 32. However, the placement of the spring 36 is not limited to this. For example, the spring 36 may also be disposed between the fulcrum guide 31 and the flange 33b. In this case, the fixing member 32 functions as the pressed part of the present invention.

[0084] In the above embodiment, clamping components 34 and 35 are provided. However, clamping components 34 and 35 can be omitted, or only one of clamping components 34 and 35 can be provided. Furthermore, the specific shape and material of clamping components 34 and 35 are not limited to the above embodiment.

[0085] In the above embodiment, the plurality of guide wire bodies 16 are movable between the winding position and the wire-hanging position. However, it is not necessary for the plurality of guide wire bodies 16 to be configured to be movable.

[0086] In the above embodiment, the rotational resistance application mechanism 37 is composed of a spring 36 and a flange 33b. However, the specific configuration of the rotational resistance application mechanism is not limited to this. Figure 5 This is a cross-sectional view of the guide wire body 16 in a modified example. In this modified example, the rotational resistance application mechanism is composed of a fulcrum guide wire 31 and contact portions 41 and 42 between clamping members 34 and 35 that contact the fulcrum guide wire 31. A detailed description will follow.

[0087] Contact portions 41 and 42 are formed between the inner circumferential surface of the fulcrum guide 31 and the radial bearing portions 34b and 35b of the clamping members 34 and 35. The frictional force at the contact portions 41 and 42 is adjusted so that when the fulcrum guide 31 rotates passively through the travel of the wire Y, the circumferential speed of the fulcrum guide 31 is slower than the travel speed of the wire Y. In addition, the two end faces of the fulcrum guide 31 make loose contact with the thrust bearing portions 34a and 35a of the clamping members 34 and 35 to a degree that generates almost no frictional resistance. However, instead of the contact portions 41 and 42 between the inner circumferential surface of the fulcrum guide 31 and the radial bearing portions 34b and 35b, or based on this, the contact portions formed between the end faces of the fulcrum guide 31 and the thrust bearing portions 34a and 35a may function as a rotational resistance application mechanism. Alternatively, clamping components 34 and 35 can be omitted, allowing the contact portion between the fulcrum guide 31 and the shaft component 33 to function as a rotational resistance application mechanism.

[0088] Using the guide wire 16 of this modified example, an experiment was conducted to verify whether changes in the quality of the wire were actually suppressed. Specifically, the following was verified: when rotational resistance was applied through the contacts 41 and 42, and the fulcrum guide 31 was rotated by the movement of the wire Y, compared to when the fulcrum guide 31 was fixed, whether the changes in the physical parameters of the wire Y, such as tension, strength, and elongation, remained unchanged. The wire Y used in the experiment had a thickness of 33 dtex, and the outer diameter of the fulcrum guide 31 was 10 mm. When the travel speed of the wire Y was set to 4500 m / min, the rotational speed of the fulcrum guide 31 was 3000–5000 rpm, and the circumferential speed was 94–157 m / min (2.1–3.5% of the travel speed of the wire Y).

[0089] Figure 6 This is a graph showing the results of verification experiments on the physical properties of the silk thread. The numbers recorded in each bar chart represent average values, and are also related to the bar... Figure 1 The diagram illustrates the deviation. "No rotation" indicates the case where the fulcrum guide 31 is fixed, and "rotation" indicates the case where the fulcrum guide 31 is rotated passively under the condition that rotational resistance is applied by the rotational resistance application mechanism 37. As described above, although the rotational speed and circumferential speed of the fulcrum guide 31 are slightly varied, there is almost no difference in the physical properties of the yarn compared to the case where the fulcrum guide 31 is fixed, and the deviation in yarn quality is also suppressed. Based on the experimental results, it can be said that by applying rotational resistance to the fulcrum guide 31 to make it rotate at a low speed, it is possible to suppress changes in yarn quality during yarn winding. In addition, under the conditions of this verification experiment, when the circumferential speed of the fulcrum guide 31 is 5% of the travel speed of the yarn Y, the rotational speed of the fulcrum guide 31 is approximately 7200 rpm.

[0090] In this variation, the spring 36 of the above embodiment is not required, and the guide wire 16 can be manufactured with a smaller number of components.

[0091] In this modified example, the contact portions 41 and 42, which serve as the rotational resistance application mechanism, are formed between the inner circumferential surface of the fulcrum guide 31 and other components (clamping components 34 and 35) that contact the inner circumferential surface of the fulcrum guide 31. Generally, the area of ​​the inner circumferential surface of the fulcrum guide 31 is larger than the area of ​​the end face. Therefore, by utilizing the inner circumferential surface of the fulcrum guide 31 as the rotational resistance application mechanism, it is easy to adjust the friction force.

[0092] In this modified example, clamping members 34 and 35 are arranged between the shaft member 33 that supports the fulcrum wire guide 31 to be rotatable and the fulcrum wire guide 31. Contact portions 41 and 42, which serve as a rotational resistance application mechanism, are formed between the inner circumferential surface of the fulcrum wire guide 31 and the clamping members 34 and 35. With this configuration, the frictional force at the contact portions 41 and 42 can be adjusted by changing the shape, size, and material of the clamping members 34 and 35, and the rotational speed and circumferential speed of the fulcrum wire guide 31 can be easily adjusted.

Claims

1. A wire guide body, comprising a fulcrum wire guide that serves as a fulcrum for winding a wire onto a bobbin while it is moving laterally, characterized in that, The aforementioned pivot wire guide has a cylindrical shape and is capable of rotating about a central axis. The aforementioned guide wire body is provided with a rotational resistance application mechanism. When the fulcrum guide wire receives a torque of more than a predetermined value from the wire traveling on one side in contact with the outer peripheral surface of the fulcrum guide wire, the rotational resistance application mechanism applies rotational resistance to the fulcrum guide wire, so that the fulcrum guide wire rotates passively at a circumferential speed slower than the traveling speed of the wire. When the torque received from the wire does not reach the predetermined value, the fulcrum guide wire does not rotate passively.

2. The guidewire according to claim 1, characterized in that, The aforementioned rotational resistance applying mechanism applies rotational resistance to the aforementioned pivot wire guide so that the circumferential speed of the aforementioned pivot wire guide is less than 5% of the traveling speed of the aforementioned wire.

3. The guidewire according to claim 2, characterized in that, The aforementioned rotational resistance applying mechanism applies rotational resistance to the aforementioned pivot wire guide so that the circumferential speed of the aforementioned pivot wire guide is less than 3.5% of the traveling speed of the aforementioned wire.

4. The guidewire according to claim 1, characterized in that, The aforementioned rotational resistance applying mechanism applies rotational resistance to the aforementioned pivot wire guide so that the rotational speed of the aforementioned pivot wire guide is below 7400 rpm.

5. The guidewire according to claim 2, characterized in that, The aforementioned rotational resistance applying mechanism applies rotational resistance to the aforementioned pivot wire guide so that the rotational speed of the aforementioned pivot wire guide is below 7400 rpm.

6. The guidewire according to claim 3, characterized in that, The aforementioned rotational resistance applying mechanism applies rotational resistance to the aforementioned pivot wire guide so that the rotational speed of the aforementioned pivot wire guide is below 7400 rpm.

7. The guidewire according to claim 4, characterized in that, The aforementioned rotational resistance applying mechanism applies rotational resistance to the aforementioned pivot wire guide so that the rotational speed of the aforementioned pivot wire guide is less than 5000 rpm.

8. The guidewire according to claim 5, characterized in that, The aforementioned rotational resistance applying mechanism applies rotational resistance to the aforementioned pivot wire guide so that the rotational speed of the aforementioned pivot wire guide is less than 5000 rpm.

9. The guidewire according to claim 6, characterized in that, The aforementioned rotational resistance applying mechanism applies rotational resistance to the aforementioned pivot wire guide so that the rotational speed of the aforementioned pivot wire guide is less than 5000 rpm.

10. The guidewire according to any one of claims 1 to 9, characterized in that, The above-mentioned rotational resistance application mechanism has: The pressed part is disposed on one side of the axial direction of the aforementioned pivot wire guide; and The pressing component presses the fulcrum guide wire toward the pressed part.

11. The guidewire according to claim 10, characterized in that, A clamping component is provided between the aforementioned fulcrum guide wire and the aforementioned pressed part, and / or between the aforementioned fulcrum guide wire and the aforementioned pressing component.

12. The guidewire according to claim 11, characterized in that, The aforementioned clamping component has: The thrust bearing portion abuts against the end face of the aforementioned pivot wire guide; and The radial bearing portion abuts against the inner circumferential surface of the aforementioned pivot wire guide.

13. The guidewire according to claim 10, characterized in that, The aforementioned pressing component is a spring.

14. The guidewire according to claim 11 or 12, characterized in that, The aforementioned pressing component is a spring.

15. The guidewire according to claim 10, characterized in that, The pressing portion is integrally formed on the shaft component that supports the aforementioned fulcrum guide as a rotatable component.

16. The guidewire according to any one of claims 11 to 13, characterized in that, The pressing portion is integrally formed on the shaft component that supports the aforementioned fulcrum guide as a rotatable component.

17. The guidewire according to claim 14, characterized in that, The pressing portion is integrally formed on the shaft component that supports the aforementioned fulcrum guide as a rotatable component.

18. The guidewire according to any one of claims 1 to 9, characterized in that, The aforementioned rotational resistance application mechanism is formed at the contact portion between other components that contact the aforementioned pivot wire guide and the aforementioned pivot wire guide. In the aforementioned contact portion, the frictional force is adjusted such that the circumferential speed of the aforementioned pivot guide is slower than the traveling speed of the aforementioned wire.

19. The guidewire according to claim 18, characterized in that, The contact portion, which serves as the aforementioned rotational resistance application mechanism, is formed between the inner circumferential surface of the aforementioned pivot wire guide and other components that contact the inner circumferential surface of the aforementioned pivot wire guide.

20. The guidewire according to claim 19, characterized in that, A clamping component is provided between the shaft component that supports the aforementioned pivot wire guide and the aforementioned pivot wire guide. The contact portion, which serves as the aforementioned rotational resistance application mechanism, is formed between the inner circumferential surface of the aforementioned fulcrum wire guide and the aforementioned clamping member.

21. A thread winding machine, comprising winding multiple threads onto multiple bobbins mounted on a winding shaft, characterized in that, The guide wire body according to any one of claims 1 to 20 has a plurality of such guide wires arranged axially along the winding shaft.

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