Silk thread winding machine

Abstract

The invention provides a yarn winding machine, which can restrain deviation of contact pressure among a plurality of packages even if the setting of the contact pressure applied to the plurality of packages is changed. A yarn winding machine (4) is provided with a machine body (20), a bobbin holder (24), a contact roller (25), a cylinder (35), a tilting mechanism (40), a displacement sensor (66), and a control unit (26). The control unit (26) controls the tilting mechanism (40) so that the actual angle-related value detected by the displacement sensor (66) becomes a target value that is determined on the basis of the weight of the yarn wound on each of the bobbins (B) and that is determined independently of the set value of the contact pressure.

Description

Technical Field

[0001] This invention relates to a yarn winding machine. Background Technology

[0002] The yarn winding machines disclosed in Patent Documents 1 and 2 include bobbin supports and contact rollers. The bobbin supports are cantilevered in an axial direction that is approximately parallel to the horizontal direction, and multiple bobbins are arranged along the axial direction to support them. The contact rollers apply contact pressure to the surfaces of multiple packages formed by winding multiple yarns onto the multiple bobbins, thereby shaping the multiple packages.

[0003] Patent Document 1 also discloses a tilting mechanism (angle changing unit) with a cylinder for adjusting the tilt angle of the contact roller relative to the horizontal direction. The rationale is to allow the contact roller to follow the deflection of the bobbin support caused by the thickening of the windings of multiple rolls (i.e., the increase in the weight of the rolls), thus suppressing deviations in contact pressure between the multiple rolls. More specifically, the angle changing unit adjusts the vertical position of the aforementioned axial end of the contact roller according to the thrust of the cylinder. This adjusts the tilt angle of the contact roller.

[0004] Patent Document 2 also discloses a contact pressure cylinder (contact pressure changing unit) that applies a force to the contact roller in at least the vertical direction. The resultant force of the variable force applied to the contact roller by the contact pressure cylinder and the force caused by the weight of the contact roller acts as a contact pressure on multiple rolls. The setting of the contact pressure changing unit can be arbitrarily switched on the user side according to the type of roll, etc.

[0005] Existing technical documents

[0006] Patent documents

[0007] Patent Document 1: Japanese Patent Application Publication No. 2018-203472

[0008] Patent Document 2: Japanese Patent Application Publication No. 2000-281266 Summary of the Invention

[0009] The problem that the invention aims to solve

[0010] The inventors of this application conducted research on the application of the contact pressure changing unit described in Patent Document 2 to the wire winding machine described in Patent Document 1. It was found that the relationship between the thrust of the cylinder of the angle changing unit and the tilt angle of the contact roller varies depending on the setting of the contact pressure. In this case, it was discovered that although the angle changing unit is provided, the contact pressure may deviate axially between multiple windings.

[0011] The object of the present invention is to suppress the deviation of contact pressure between multiple rolls even if the setting of the contact pressure applied to multiple rolls is changed.

[0012] Methods for solving problems

[0013] The first invention discloses a yarn winding machine comprising: a body; a bobbin support that holds a plurality of bobbins arranged in a predetermined axial direction having a horizontal component and cantilevered on the body; a contact roller that extends at least along the axial direction and applies contact pressure to a plurality of packages formed by winding a plurality of yarns onto the plurality of bobbins respectively; a contact pressure changing unit that can change the contact pressure by applying a first force to the contact roller that can at least change the magnitude in the vertical direction; an angle changing unit that can change the tilt angle of the contact roller relative to the horizontal direction by applying a second force, different from the first force, that can at least change the magnitude in the vertical direction; a detection unit that detects information of an actual angle correlation value related to the actual tilt angle of the contact roller; and a control unit; the control unit controls the angle changing unit in such a way that the actual angle correlation value becomes a target value, the target value being determined based on the weight of the yarns wound onto the plurality of bobbins respectively and independently of the set value of the contact pressure.

[0014] In the structure of this invention, the relationship between the second force and the tilt angle of the contact roller can vary depending on the contact pressure. Therefore, in this invention, the angle changing unit is controlled such that the actual angle correlation value, which is related to the actual tilt angle, becomes a target value determined independently of the set value of the contact pressure. Thus, regardless of the set value of the contact pressure, deviation of the actual angle correlation value from the target value can be suppressed. Therefore, even if the setting of the contact pressure applied to multiple rolls is changed, deviation of the contact pressure between multiple rolls can be suppressed.

[0015] The second invention's thread winding machine is characterized in that, in the first invention, it includes a moving part integral with the contact roller and capable of moving at least in the vertical direction, and the detection part is configured to detect information related to the amount of displacement of the moving part in the vertical direction as information of the actual angle correlation value.

[0016] Because the deflection angle of the bobbin support and the change in the tilt angle of the contact roller relative to the horizontal direction are extremely small, the detection accuracy is low in structures that detect the tilt angle itself. In this regard, the contact roller generally extends relatively long in the horizontal direction, so even if the change in tilt angle is small, the vertical displacement of the moving part is easily detected. Therefore, the displacement of the moving part is effective as a physical quantity to be detected instead of the tilt angle. Moreover, by controlling the angle-changing part by detecting the displacement of the moving part, the tilt angle of the contact roller can be substantially controlled. Therefore, deviations in contact pressure between multiple rolls can be effectively suppressed.

[0017] The third invention's thread winding machine is characterized by comprising: a machine body; a bobbin support that holds a plurality of bobbins arranged in a predetermined axial direction having a horizontal component and is cantilevered on the machine body; a contact roller that extends at least along the axial direction and applies contact pressure to a plurality of packages formed by winding a plurality of threads onto the plurality of bobbins respectively; a contact pressure changing unit that can change the contact pressure by applying a first force to the contact roller that can at least change the magnitude in the vertical direction; an angle changing unit that can change the tilt angle of the contact roller relative to the horizontal direction by applying a second force, different from the first force and capable of at least changing the magnitude in the vertical direction; and a control unit that controls the angle changing unit using force adjustment information related to the adjustment amount of the second force and corresponding to a set value of the contact pressure.

[0018] In this invention, by using force adjustment information corresponding to a set value of the contact pressure, an appropriate second force corresponding to the weight of the multiple rolls can be applied to the contact roller. This allows for appropriate adjustment of the tilt angle. Therefore, similar to the first invention, even if the setting of the contact pressure applied to the multiple rolls is changed, deviations in the contact pressure between the multiple rolls can be suppressed.

[0019] The fourth invention is characterized in that, in any of the first to third inventions, the angle changing unit has: a fluid pressure cylinder as a drive source for applying the second force to the contact roller; and a pressure adjusting unit configured to adjust the pressure of the fluid supplied to the fluid pressure cylinder.

[0020] In this invention, a fluid pressure cylinder is used as the drive source for the angle changing unit, and the output of the fluid pressure cylinder is adjusted by a pressure adjustment unit, thereby simplifying the construction of the wire winding machine.

[0021] The fifth invention is characterized in that, in the fourth invention, the fluid pressure cylinder is a pneumatic cylinder.

[0022] In this invention, for example by using a pneumatic cylinder which is cheaper than a hydraulic cylinder, the increase in component costs of the wire winding machine can be suppressed.

[0023] The sixth invention is characterized in that, in the fifth invention, the pressure adjustment unit is an electro-pneumatic pressure regulating valve.

[0024] In this invention, the cylinder output can be reliably adjusted with a simple structure.

[0025] The seventh invention is characterized in that, in any of the fourth to sixth inventions, the angle changing part comprises: a roller support member that supports the contact roller for rotational movement; and a lifting part driven by the fluid pressure cylinder to lift one end of the roller support member in the axial direction.

[0026] In this invention, compared to structures that, for example, raise or lower the axial inner portion of the roller support member, the change in tilt angle relative to the displacement of the roller support member can be suppressed to a smaller extent. Therefore, fine adjustments to the tilt angle are possible.

[0027] The silk winding machine of the eighth invention is characterized in that, in the seventh invention, the lifting part has a clamping mechanism, which is arranged between the fluid pressure cylinder and the roller support member in the direction of force transmission of the fluid pressure cylinder, so that the greater the displacement of the axial end of the roller support member relative to the initial position in the vertical direction, the greater the force required to further increase the displacement.

[0028] In this invention, a greater force is required to increase the displacement of the roller support component. Therefore, even when it is difficult to precisely adjust the thrust of the fluid pressure cylinder, the displacement of the roller support component can be controlled with high precision. Consequently, the tilt angle of the contact roller can be controlled with high precision.

[0029] The thread winding machine of the ninth invention is characterized in that, in the seventh or eighth invention, the contact pressure changing unit is configured to apply the first force to the contact roller by applying a force to the other end of the axial direction of the roller support member.

[0030] In this invention, the roller support component can be supported stably with dual supports by means of a lifting section and a contact pressure changing section. Therefore, the contact pressure can be adjusted stably. Attached Figure Description

[0031] Figure 1 This is a side view of the spinning traction machine of the yarn winding machine of this embodiment.

[0032] Figure 2 This is the front view of a wire winding machine.

[0033] Figure 3 This is a perspective view of the rear of the contact roller and the tilting mechanism.

[0034] Figure 4 This is a diagram showing the tilting mechanism from the rear.

[0035] Figure 5 (a)~ Figure 5 (c) is a diagram showing the action of the tilting mechanism.

[0036] Figure 6 (a)~ Figure 6 (c) is a diagram showing the change in the posture of the contact roller.

[0037] Figure 7 yes Figure 5 Supplementary diagram to (a).

[0038] Figure 8 It is a graph showing the relationship between the displacement of the roller support component and the load on the cylinder.

[0039] Figure 9 This is a table showing the relationship between the weight of each roll and the target value of the displacement of the roll support components.

[0040] Figure 10 This is a flowchart showing the control of the displacement of the roller support components during wire winding.

[0041] Figure 11 Table (a) shows the relationship between the weight of each roll in the modified example and the target value of the compressed air pressure. Figure 11 (b) is a table showing the relationship between the contact pressure and the adjustment amount of the compressed air pressure.

[0042] Figure 12 This is a flowchart illustrating the pressure control of compressed air in the winding of a modified thread.

[0043] Explanation of reference numerals in the attached figures

[0044] 4. Wire winding machine; 20. Machine body; 24. Boll tube support; 25. Contact roller; 26. Control unit; 30. Roller support component; 35. Cylinder (contact pressure changing unit); 40. Tilting mechanism (angle changing unit); 41. Cylinder (fluid pressure cylinder); 42. Clamping mechanism (lifting unit); 47. Electro-pneumatic pressure regulating valve (pressure adjusting unit); 61. Second main body (moving unit); 66. Displacement sensor (detection unit); B. Boll tube; P. Coil; Y. Wire. Detailed Implementation

[0045] Next, embodiments of the present invention will be described. Figure 1 This is a side view of the spinning traction machine 1 having the yarn winding machine 4 (described later) of this embodiment. Figure 1 The vertical direction on the paper is defined as the up-down direction. The up-down direction is parallel to the vertical direction of gravity. The direction orthogonal to the up-down direction is... Figure 1 The left-right direction of the paper is defined as the front-back direction (the axial direction of this invention). The direction orthogonal to both the front-back and up-down directions (the direction perpendicular to the paper) is defined as the left-right direction.

[0046] (Overview of spinning traction machine)

[0047] The spinning traction machine 1 draws multiple filaments Y spun from the spinning device 3 and winds them onto multiple bobbins B to form multiple packages P. The spinning traction machine 1 includes a first guide roller 11, a second guide roller 12, and a filament winding machine 4.

[0048] The first guide roller 11 is a roller whose axial direction is approximately parallel to the left-right direction. The first guide roller 11 is positioned above the front end of the yarn winding machine 4. The first guide roller 11 is driven to rotate by a motor (not shown). The second guide roller 12 is a roller whose axial direction is approximately parallel to the left-right direction. The second guide roller 12 is positioned above and behind the first guide roller 11. The second guide roller 12 is driven to rotate by a motor (not shown).

[0049] The thread winding machine 4 performs a winding action that winds multiple threads Y onto multiple bobbins B to form multiple packages P. (Refer to...) Figures 1-4 A more detailed description of the structure of the thread winding machine 4 will be provided. Figure 2 This is the front view of the thread winding machine 4. Figure 3 This is a perspective view of the rear of the contact roller 25, which will be described later, and the tilting mechanism 40, which will be described later. Figure 4 This is a view of the tilting mechanism 40 from the rear. The yarn winding machine 4 has a body 20, multiple fulcrum guides 21, multiple traverse guides 22, a turntable 23, two bobbin supports 24, contact rollers 25, and a control unit 26.

[0050] like Figure 1 As shown, the machine body 20 has a main body section 27 and a frame 28. The main body section 27 is erected at the rear of the wire winding machine 4. A turntable 23 and the like are supported on the main body section 27. The frame 28 is, for example, a hollow columnar component. The frame 28 is fixed to the upper part of the main body section 27 and extends forward from the main body section 27. A contact roller 25 is supported on the frame 28. Figure 3 As shown, a notch is formed on the upper part of the rear end portion of the frame 28 via sides 28a, 28b, and 28c. Side 28a is formed at the right end of the frame 28. Side 28b is formed at the left end of the frame 28. Side 28c faces the rear. A tilting mechanism 40, described later, is provided at the rear end of the frame 28.

[0051] Multiple fulcrum guides 21 are respectively provided for multiple yarns Y. Each of the multiple fulcrum guides 21 serves as a fulcrum for the corresponding yarn Y during lateral movement. The multiple fulcrum guides 21 are arranged in the front-to-back direction.

[0052] Multiple traverse guides 22 are respectively arranged corresponding to multiple yarns Y. Each traverse guide 22 is used to traverse the corresponding yarn Y. The multiple traverse guides 22 are arranged in the front-to-back direction. The multiple traverse guides 22 are driven by a traverse motor (not shown). The yarn Y suspended on the traverse guide 22 traverses with the pivot guide 21 as the pivot point.

[0053] The turntable 23 is a circular plate-shaped component whose axial direction is approximately parallel to the front-rear direction. The turntable 23 is rotatably supported on the main body 27. The turntable 23 is driven to rotate by a turntable motor (not shown). The turntable 23 cantileverly supports two bobbin supports 24. The two bobbin supports 24 move by rotating the turntable 23 around a rotation axis approximately parallel to the front-rear direction. The turntable 23 is configured to rotate as the amount of bobbin Y wound increases when winding yarn into bobbin B (see reference). Figure 2 (Solid arrowhead).

[0054] Two bobbin supports 24 are configured to arrange and support multiple bobbins B in the front-to-back direction, allowing them to rotate. The two bobbin supports 24 are arranged symmetrically about the rotation axis of the turntable 23. Each bobbin support 24 extends forward from the turntable 23. In other words, the two bobbin supports 24 are cantilevered by the main body 27 via the turntable 23. The axes of the two bobbin supports 24 are approximately parallel to the front-to-back direction. Furthermore, the front end of the bobbin support 24 is generally the working side where operations such as installing bobbins B onto the bobbin support 24 are performed. Multiple bobbins B are arranged and installed on each bobbin support 24 in the front-to-back direction. The number of bobbins B installed on one bobbin support 24 is, for example, 16, but is not limited to this. Each of the two bobbin supports 24 is driven to rotate by a separate take-up motor (not shown).

[0055] The contact roller 25 is a roller positioned directly above the upper bobbin support 24. The axial direction of the contact roller 25 is approximately parallel to the front-to-back direction. The contact roller 25 applies contact pressure to the surface of the multiple rolls P supported by the upper bobbin support 24, thereby adjusting the shape of the rolls P.

[0056] In this embodiment, the contact roller 25 is supported on the frame 28 in a swingable manner by means of the roller support member 30. Figures 1-3As shown, the roller support member 30 includes, for example, a support portion 31, an arm portion 32, and a swing shaft 33. The support portion 31 supports the contact roller 25 at both ends in the front-rear direction, allowing it to rotate freely. The arm portion 32 is, for example, a rod-shaped component. One end of the arm portion 32 is connected to the support portion 31 and extends toward the frame 28 in a direction orthogonal to the front-rear direction. The swing shaft 33 is connected to the other end of the arm portion 32 and extends in the front-rear direction, with its front and rear ends swingably supported on the frame 28. The rear end of the swing shaft 33 is supported by a tilting mechanism 40, described later. The total weight of the contact roller 25 and the roller support member 30 is, for example, about 200 kg, but is not limited thereto.

[0057] like Figure 2 As shown, the wire winding machine 4 of this embodiment also includes a cylinder 35 (the contact pressure changing unit of the present invention). The cylinder 35 is used to change the contact pressure of the contact roller 25 on the plurality of windings P according to the pressure of the supplied compressed air. The cylinder 35 has a cylinder body 37 and a rod end 36. The rod end 36 is supported in a swingable manner on a support portion 28L, for example, fixed to the lower part of the front end of the frame 28, via a swing shaft 36a extending in the front-rear direction. The rod end 36 is fixed to the top end of the piston rod (reference numerals omitted) of the cylinder 35 and is movable relative to the cylinder body 37. The cylinder body 37 is swingably connected to the middle portion of the arm 32 in the extending direction of the arm portion 32 via a joint 38. An electro-pneumatic pressure regulating valve 39 is connected to the cylinder body 37. The electro-pneumatic pressure regulating valve 39 is electrically connected to the control unit 26. The electro-pneumatic pressure regulating valve 39 adjusts the pressure of the compressed air supplied to the cylinder body 37 according to the command from the control unit 26. The cylinder 35 applies a force F (referring to) to the roller support member 30, which has at least a vertical component. Figure 2 Thus, a force (the first force of the invention) having at least a vertical component is applied to the contact roller 25 via the roller support member. The magnitude of the force F varies depending on the pressure of the compressed air. The pressure of the compressed air generally remains unchanged midway through the winding of the yarn Y onto the bobbin B. Information related to the pressure of the compressed air (i.e., information on the contact pressure) is pre-stored, for example, in the control unit 26 according to the specifications of the package P. The contact pressure information is pre-set in the control unit 26, for example, by an operator monitoring the operation of the yarn winding machine 4.

[0058] The control unit 26 includes a CPU, ROM, and RAM. The control unit 26 controls each component via the CPU according to a program stored in the ROM. Additionally, the control unit 26 has an input unit (not shown) for operator input (keyboard, touch panel, mouse, etc.).

[0059] In the yarn winding machine 4 with the above structure, if the upper bobbin support 24 is driven to rotate, the yarn Y, which is traversed by the traversing guide 22, is wound onto the bobbin B to form a roll P. Furthermore, when the roll P becomes a full roll, the turntable 23 is rotated. This causes the vertical positions of the two bobbin supports 24 to be reversed. That is, the lower bobbin support 24 moves upward. Then, multiple yarns Y are transferred from multiple rolls P to multiple bobbins B (multiple new bobbins B) mounted on the upper bobbin support 24 (bobbin switching) (not shown). After bobbin switching, multiple yarns Y are wound onto multiple new bobbins B to form multiple rolls P. Additionally, the bobbin support 24, which is mounted with multiple full rolls P, moves downward. The multiple full rolls P are recovered, for example, by a roll recovery device (not shown). The winding action of the wire winding machine 4, from the moment it starts winding multiple threads Y onto multiple bobbins B until the winding ends, is the winding action described above.

[0060] (Tilting Mechanism)

[0061] Reference Figure 3 and Figure 4 The structure of the tilting mechanism 40 (the angle changing part of the present invention) will be described. For example... Figure 3 and Figure 4 As shown, the tilting mechanism 40 includes a cylinder 41 (the fluid pressure cylinder of the present invention) and a clamping mechanism 42 (the lifting part of the present invention). The cylinder 41 is the driving source of the clamping mechanism 42. The clamping mechanism 42 is clamped between the rear end of the roller support member 30 and the cylinder 41 in the direction of force transmission of the cylinder 41. The cylinder 41 and the clamping mechanism 42 are located at the rear end of the frame 28 (i.e., the end on the base end side of the tube support 24 in the front-rear direction). The rear end of the roller support member 30 corresponds to one end of the axial direction of the present invention. The front end of the roller support member 30 corresponds to the other end of the axial direction of the present invention.

[0062] Cylinder 41 is used to displace the rear end of the roller support member 30 in the vertical direction via clamping mechanism 42. Cylinder 41 is a drive source for applying a force (the second force of the invention) with at least a vertical component to the contact roller 25. Cylinder 41 is housed in and supported on the rear end of frame 28. Figure 4As shown, cylinder 41 has a cylinder body 43 and a piston rod 45. A working chamber 44 for supplying compressed air (the fluid of the present invention) is formed in the cylinder body 43. The piston rod 45 extends and retracts by the supply and discharge of compressed air to the working chamber 44. An electro-pneumatic pressure regulating valve 47 (the pressure adjustment unit of the present invention) is connected to the working chamber 44. The electro-pneumatic pressure regulating valve 47 is electrically connected to the control unit 26. The electro-pneumatic pressure regulating valve 47 adjusts the pressure of the compressed air supplied to the working chamber 44 according to the instructions from the control unit 26. The piston rod 45 protrudes upward from the upper end of the cylinder body 43. The piston rod 45 is received in the aforementioned notch of the frame 28 and can extend and retract in the vertical direction. An upper end face 46 arranged substantially parallel to the horizontal direction is formed at the front end of the piston rod 45.

[0063] The clamping mechanism 42 is located between the rear end of the roller support member 30 and the cylinder 41, and is used to transmit the thrust of the cylinder 41 to the rear end of the roller support member 30. The clamping mechanism 42 includes, for example, a first clamping part 50 and a second clamping part 60.

[0064] The first clamping part 50 is directly pressed by the piston rod 45, which is used to transmit the thrust of the cylinder 41 to the second clamping part 60. For example... Figure 4 As shown, the first clamping part 50 is supported on the frame 28 in a swingable manner by means of a first fulcrum shaft 51 extending in the front-rear direction. The first clamping part 50 has a first main body part 52, a first roller 53, and a support part 54.

[0065] The first main body 52 is a generally rectangular component when viewed from the rear. The first main body 52 is configured to be pivotally supported on the side 28c of the frame 28 via a first fulcrum shaft 51, and to support the first roller 53 and the support portion 54. The first roller 53 is positioned to the left of the first fulcrum shaft 51. Figure 4 The first roller 53 is a roller supported on the first main body 52 in such a way that it can rotate about an axis 59 that is approximately parallel to the first fulcrum axis 51, and is in contact with the upper end face 46 of the piston rod 45. The support part 54 is used to support the second clamping part 60 from below. The support part 54 is a component that is approximately T-shaped when viewed from the rear. The lower part of the support part 54 is detachably mounted to the first main body 52 by means of a fixing member 55. A notch that is approximately U-shaped when viewed from the rear is formed on the circumferential surface of the support part 54 in such a way that it covers the lower part of the first roller 53. The support part 54 has an upper surface 56. The upper surface 56 has a support surface 57 (see reference). Figure 4 (The thicker line). The support surface 57 supports the second clamping part 60 by contacting the second roller 62 (described later) from below. In other words, the support surface 57 is the part of the upper surface 56 that can contact the second roller 62. The part of the support surface 57 that contacts the second roller 62 is designated as the contact part 58.

[0066] For ease of explanation, the position of the roller support member 30 when it is approximately horizontal is referred to as the initial position of the roller support member 30. Furthermore, for ease of explanation, the amount of vertical displacement of the rear end of the roller support member 30 relative to the initial position is simply referred to as the displacement. For example, when the displacement of the rear end of the roller support member 30 is zero, the support surface 57 extends upward in the left-right direction as it moves away from the first fulcrum axis 51. The upward side is the side where the piston rod 45 protrudes. The support surface 57 is a curved surface whose inclination relative to the horizontal direction increases as it approaches the first fulcrum axis 51 in the horizontal direction. The support surface 57 is disposed between the first roller 53 and the first fulcrum axis 51 in the left-right direction.

[0067] The second clamping part 60 is used to transmit the thrust of the cylinder 41 transmitted via the first clamping part 50 to the rear end of the roller support member 30. The second clamping part 60 has a second main body part 61 (the moving part of the present invention) and a second roller 62.

[0068] The second main body 61 is a roughly rectangular component when viewed from the rear. The second main body 61 extends in the left-right direction. The second main body 61 is located at its left end ( Figure 4 The right end of the paper (the part of the paper) is supported on the frame 28 by a second fulcrum 63, which is positioned differently from the first fulcrum 51. The right end of the second main body 61 ( Figure 4 The left end of the paper surface of the contact roller 25 is provided with a connecting part 64 that connects to the rear end of the roller support member 30 and supports the roller support member 30 in a swingable manner. In other words, the contact roller 25 is connected to the second main body 61 via the roller support member 30. The second main body 61 is integral with the contact roller 25 and can move (swing) at least in the vertical direction. The second main body 61 is driven by a cylinder 41 to raise and lower the rear end of the roller support member 30.

[0069] The second roller 62 is positioned between the second fulcrum shaft 63 and the connecting portion 64 in the left-right direction, and behind the second main body portion 61. Figure 4 The second roller 62 is located near the front side of the paper surface. It is supported on the second main body 61 in a manner that allows it to rotate about an axis 65 approximately parallel to the second fulcrum axis 63, and is directly supported by the support part 54 through contact with the support surface 57 of the first clamping part 50. In other words, the rear end of the roller support member 30 is indirectly supported by the support part 54 via the second roller 62. The second roller 62 can swing up and down integrally with the second main body 61. That is, the second roller 62 can be displaced at least in the vertical direction.

[0070] (The movement of the tilting mechanism and the posture of the contact roller)

[0071] Next, refer to Figure 5 (a)~ Figure 6(c) explains the operation of the tilting mechanism 40 and the change in the posture of the contact roller 25 caused by the operation of the tilting mechanism 40. Figure 5 (a)~ Figure 5 (c) is an explanatory diagram showing the operation of the tilting mechanism 40. Figure 6 (a)~ Figure 6 (c) is an explanatory diagram showing the change in the posture of the contact roller 25.

[0072] First, a summary of the operation of the tilting mechanism 40 will be given. The electro-pneumatic pressure regulating valve 47 is controlled by the control unit 26, thereby supplying compressed air at a predetermined pressure to the working chamber 44 of the cylinder 41. The piston rod 45 extends due to the compressed air, pressing the first roller 53 of the first clamping part 50 upwards. The first clamping part 50 is pressed upwards via the first roller 53. When the first clamping part 50 is pressed upwards, the second roller 62 of the second clamping part 60, which contacts the support surface 57, is also pressed upwards. If the force pressing the second roller 62 upwards is balanced by the downward force generated by the weight of the contact roller 25, the postures of the first clamping part 50 and the second clamping part 60 are determined, as are the postures of the roller support member 30 and the contact roller 25. On the other hand, if the upward pressing force of the second roller 62 exceeds the downward force, the first clamping part 50 and the second clamping part 60 swing upward, and the connecting part 64 of the second clamping part 60 and the rear end of the roller support member 30 are displaced upward (see reference). Figure 5 (a)~ Figure 5 (c)). When the rear end of the roller support member 30 is displaced upward, the contact roller 25 tilts, and the posture of the contact roller 25 changes so that the rear end of the contact roller 25 is above and the front end is relatively below (see reference). Figure 6 (a)~ Figure 6 (c)).

[0073] Next, use Figure 5 The specific forces acting on the clamping mechanism 42, centered on the first clamping part 50, will be explained. With the first fulcrum shaft 51 as the fulcrum, the upward torque generated by the cylinder 41 and the downward torque generated by the weight of the contact roller 25 act on the first clamping part 50. When these two torques are balanced, the first clamping part 50 stops; when the upward torque is greater than the downward torque, the first clamping part 50 swings upward. In other words, the first clamping part 50 moves using the lever principle, with the first fulcrum shaft 51 as the fulcrum, the point of contact with the upper end face 46 of the first roller 53 as the point of force application, and the contact part 58 of the support surface 57 as the point of action.

[0074] Figure 5Figure (a) shows the state of the tilting mechanism 40 before the yarn Y begins to be wound onto the bobbin B. In this state, the torque of the force that moves the first clamping part 50 upward is balanced with the torque of the force that moves the first clamping part downward, thereby keeping the second main body 61 of the second clamping part 60 in a generally horizontal position. In addition, the upward displacement of the rear end of the roller support member 30 (hereinafter also referred to as the displacement of the roller support member 30) is zero at this time. The torques of these two forces will be explained in detail below.

[0075] First, let's explain the torque of the upward force. As described above, the piston rod 45 presses the first roller 53 upward. Figure 5 As shown in (a), the thrust F1a of the cylinder 41 acts on the first roller 53, and the torque of the upward force with the first fulcrum shaft 51 as the fulcrum acts on the first clamping part 50. When the horizontal distance (i.e., the distance of the point of force application) between the part of the first roller 53 that contacts the upper end face 46 of the piston rod 45 and the first fulcrum shaft 51 is set as distance L1a, the magnitude of the torque of the force is F1a × L1a.

[0076] Next, the torque of the downward force will be explained. The downward force generated by the weight of the contact roller 25, etc., acts on the second clamping part 60. As a result, the downward force F2a acts on the contact part 58a of the support surface 57 via the second roller 62. Therefore, as will be described later, if the horizontal distance between the contact part 58a and the first fulcrum axis 51 is defined as distance L2a, then the magnitude of the torque of the force that moves the first clamping part 50 downward is F2a × L2a.

[0077] use Figure 7 The details of the downward force torque are explained below. The component of force F2a that rotates the first clamping part 50 is the component orthogonal to the line segment connecting the first fulcrum axis 51 and the contact part 58a, i.e., force F2aa. The direction of force F2aa is inclined at an angle θ relative to the direction of force F2a (vertical direction). Furthermore, if the length of the line segment connecting the first fulcrum axis 51 and the contact part 58a is L, then the magnitude of the torque of the force that moves the first clamping part 50 downward is F2aa × L, i.e., F2a × cosθ × L. On the other hand, the line segment connecting the first fulcrum axis 51 and the contact part 58a is inclined at the same angle θ relative to the horizontal direction. Therefore, the magnitude of the distance L2a is L2a = L × cosθ. That is, the magnitude of the torque of the force is F2a × cosθ × L = F2a × L2a. This distance L2a is called the point of application distance.

[0078] exist Figure 5In (a), the magnitudes of the torques of the two forces mentioned above are balanced. That is, F1a × L1a = F2a × L2a. In other words, F1a = F2a × L2a / L1a. The magnitude of F1a is the magnitude of the upward thrust generated by cylinder 41, and simultaneously the magnitude of the downward load acting on cylinder 41. Since L1a > L2a, the thrust F1a of cylinder 41 is smaller compared to the downward force F2a.

[0079] Since the torques of the two forces mentioned above are balanced, the postures of the first clamping part 50 and the second clamping part 60 are determined, and the second main body part 61 of the second clamping part 60 remains in a generally horizontal posture. Consequently, the contact roller 25 also remains in a generally horizontal posture (see reference). Figure 6 (a)

[0080] Next, the displacement of the roller support component 30 during the process of winding multiple filaments Y onto multiple bobbins B will be explained. Figure 5 (b) is a diagram showing the state of the tilting mechanism 40 when the displacement of the roller support component 30 is between zero and the maximum displacement.

[0081] When the thrust of cylinder 41 is greater than F1a (refer to...) Figure 5 When (a) occurs, the first clamping part 50 swings upward about the first fulcrum axis 51. At this time, the inclination of the first clamping part 50 relative to the horizontal direction increases, so the horizontal distance L1b between the first roller 53 and the first fulcrum axis 51 is smaller than the distance L1a. The first roller 53 contacts the upper end face 46 of the piston rod 45 and rotates, smoothly following the change in the horizontal distance. That is, the distance of the point of force changes smoothly with the swinging of the first clamping part 50. Figure 5 As shown in (b), if the thrust of cylinder 41 is set as thrust F1b, and the distance of the point of force application is set as distance L1b, then the magnitude of the torque of the upward force is F1b × L1b. Distance L1b is greater than distance L1a (refer to...). Figure 5 (a)) small.

[0082] As described above, the first clamping part 50 swings, and the support surface 57 also swings. The second roller 62, which is in contact with the support surface 57, begins to move upward about the second fulcrum axis 63. Here, since the direction of the swing of the second roller 62 is different from the direction of the swing of the support surface 57, the second roller 62 moves relative to the support surface 57 when the support surface 57 swings. As a result, the contact part 58b is more than... Figure 5 The contact portion 58a in (a) is moved away from the first fulcrum axis 51 (i.e., the distance between the points of action increases). The second roller 62 rotates in contact with the support surface 57, thus smoothly following the swing of the first clamping portion 50.

[0083] Here, as described above, the support surface 57 extends upward beyond the first fulcrum axis 51 as it moves away from the first fulcrum axis 51 in the left-right direction. Therefore, when the contact portion 58 moves away from the first fulcrum axis 51 by displacing upward through the first clamping portion 50, the second roller 62 reliably moves upward along the support surface 57. Furthermore, the closer the support surface 57 is to the first fulcrum axis 51, the larger its inclination angle relative to the horizontal direction. Therefore, even when the distance between the points of action is relatively small, the vertical displacement of the second roller 62 accompanying the displacement of the first clamping portion 50 increases due to the large inclination of the curved surface. Moreover, when the distance between the points of action is relatively large, even if the inclination angle of the support surface 57 is gentle, the second roller 62 is easily displaced vertically by the displacement of the first clamping portion 50.

[0084] When the downward force acting on the contact portion 58b is defined as force F2b, and the distance between the points of application is defined as distance L2b, the magnitude of the torque of the downward force is F2b × L2b. Figure 5 In (b), F1b × L1b = F2b × L2b, and the postures of the first clamping part 50 and the second clamping part 60 are determined. In other words, F1b = F2b × L2b / L1b. At this time, the rear end of the roller support member 30 is displaced upward, and the contact roller 25 is tilted relative to the horizontal direction (see reference). Figure 6 (b)). At this time, multiple threads Y are being wound onto multiple bobbins B respectively, and the diameter of multiple rolls P becomes approximately half of the maximum diameter.

[0085] Here, even if the rear end of the roller support member 30 is slightly displaced upward from the state where the displacement of the roller support member 30 is zero (the second main body 61 is approximately horizontal), the magnitude of force F2b is similar to that of force F2a (refer to...). Figure 5 The magnitude of (a) also remains almost unchanged. On the other hand, the distance from L2b (distance to the point of application) is greater than the distance from L2a (distance to the reference point). Figure 5 (a) is larger. Furthermore, as mentioned above, the distance L1b (distance to the point of application) is greater than the distance L1a (distance to the reference point). Figure 5 (a) is small. That is, if the displacement of the roller support component 30 is increased, the load acting on the cylinder 41 will increase due to the increase in the distance between the points of action and the decrease in the distance between the points of force application. In other words, in order to further increase the displacement of the roller support component 30, a larger cylinder thrust is required.

[0086] The greater the displacement of the roller support component 30, the greater the load. For example... Figure 5As shown in (c) thereof, in a state where the displacement amount of the roller support member 30 is maximized, the distance L1c as the distance of the acting point becomes further smaller (L1c < L1b < L1a), and the distance L2c as the distance of the acting point becomes further larger (L2c > L2b > L2a). When the thrust of the air cylinder 41 at this time is set as the thrust F1c and the downward force acting on the contact portion 58c is set as the force F2c, the relationship of F1c × L1c = F2c × L2c holds. At this time, the rear end portion of the roller support member 30 is further displaced upward, and the contact roller 25 is further inclined with respect to the horizontal direction (see Figure 6 (c) thereof). In addition, at this time, the plurality of packages P are in a full-wound state.

[0087] (Relationship between displacement amount and load)

[0088] Refer to Figure 8 The relationship between the displacement amount of the above-described roller support member 30 and the load acting on the air cylinder 41 will be described with reference to the curve graph. Here, for simplicity, it is assumed that the above-described contact pressure is in the "medium" state. The horizontal axis of the curve graph represents the displacement amount of the roller support member 30. The vertical axis of the curve graph represents the load acting on the air cylinder 41 (that is, the thrust required to further displace the rear end portion of the roller support member 30). As described above, when the displacement amount is zero, the magnitude of the load acting on the air cylinder 41 is F1a.

[0089] When the plurality of silk threads Y are respectively wound around the plurality of bobbins B, the control unit 26 performs the following control in order to make the inclination of the contact roller 25 follow the change in the inclination of the bobbin holder 24 caused by the winding thickening of the package P. That is, the control unit 26 controls the electro-pneumatic pressure regulating valve 47 so that the pressure of the compressed air supplied to the air cylinder 41 gradually increases with the passage of time. Information related to the time change of the above-described pressure is stored in, for example, a ROM or the like. As the above-described pressure increases, the thrust of the air cylinder 41 gradually increases from F1a. Along with this, as described above, the tilting mechanism 40 operates, and the rear end portion of the roller support member 30 is gradually displaced upward.

[0090] For example, when the maximum displacement amount of the roller support member 30 is set as X, when the roller support member 30 is displaced by half of it, that is, X / 2, the magnitude of the load acting on the air cylinder 41 becomes the aforementioned F1b. Similarly, when the roller support member 30 is displaced by X, the magnitude of the load acting on the air cylinder 41 becomes the aforementioned F1c. In other words, the load of the weight of the contact roller 25 on the air cylinder 41 is amplified by the clamping mechanism 42 as the above-described displacement amount increases. Therefore, the larger the above-described displacement amount, the larger the thrust of the air cylinder 41 required to further displace the roller support member 30. In addition, the relationship between the above-described displacement amount and the load can be adjusted by, for example, adjusting the shape of the support surface 57, the positional relationship between the first clamping portion 50 and the second clamping portion 60, etc. as Figure 8It can be set as a straight line as shown. However, it is not limited to this, as long as the above displacement and load can reliably correspond one-to-one.

[0091] However, it is known that the relationship between the thrust of the cylinder 41 of the tilting mechanism 40 and the tilt angle of the contact roller 25 depends on the setting of the contact pressure (controlled by the control unit 26 on the electro-pneumatic pressure regulating valve). (Refer to...) Figure 8 To explain in more detail. Figure 8 The figure shows the relationship between displacement and load for various contact pressures of "small", "medium" and "large".

[0092] The roller support component 30 is supported at both ends in the front-rear direction by the cylinder 35 and the clamping mechanism 42. When the contact pressure is "small," which is lower than "medium," the force by which the winding P pushes the contact roller 25 upward is relatively small according to the law of action and reaction. Therefore, the force required for the clamping mechanism 42 to support the roller support component 30 is relatively large. Consequently, the thrust required to increase the displacement is also relatively large. More specifically, the thrust required to displace the roller support component 30 in the vertical direction by X / 2 is a thrust F1L that is larger than the thrust F1b required when the contact pressure is "medium." Furthermore, if the cylinder 41 outputs thrust F1b when the contact pressure is "medium," the roller support component 30 displaces by X / 2 in the vertical direction. However, when the contact pressure is "small," the displacement of the roller support component 30 when outputting thrust F1b is XL, which is smaller than X / 2. On the other hand, when the contact pressure is "large," which is relatively high, the force by which the winding P pushes the contact roller 25 upward is relatively large. Therefore, the force required to support the roller support member 30 by the clamping mechanism 42 is relatively small. Consequently, the thrust required to increase the displacement is also relatively small. More specifically, the thrust required to displace the roller support member 30 in the vertical direction by X / 2 is a thrust F1H that is smaller than the thrust F1b. Furthermore, when the contact pressure is "large", the displacement of the roller support member 30 when the output thrust F1b is XH that is larger than X / 2. Thus, the relationship between the thrust of the cylinder 41 and the displacement of the roller support member 30 (i.e., the relationship between the thrust and the tilt angle of the contact roller 25) changes. Therefore, it is found that even though the tilting mechanism 40 is provided, the contact pressure may deviate in the axial direction between the multiple rolls P. Therefore, in order to suppress the deviation of the contact pressure between the multiple rolls P even if the setting of the contact pressure applied to the multiple rolls P is changed, the yarn winding machine 4 is configured as follows.

[0093] (More details about thread winding machines)

[0094] Reference Figure 4 as well as Figure 9 A more detailed description of the thread winding machine 4 is provided below. Figure 9 This is a table showing the relationship between the weight of each roll P and the target value of the displacement of the roll support component 30.

[0095] like Figure 4 As shown, the thread winding machine 4 includes a displacement sensor 66 (the detection unit of this invention). The displacement sensor 66 is a sensor used to detect the amount of displacement of the roller support member 30. Examples of displacement sensors 66 include known optical displacement sensors, linear proximity sensors, and ultrasonic displacement sensors. The displacement sensor 66 is, for example, disposed on the lower side of the right end of the second main body 61. The displacement sensor 66 is, for example, mounted on the right end of the rear end of the frame 28. The displacement sensor 66 is configured to detect the amount of displacement of the right end of the second main body 61. The displacement sensor 66 is electrically connected to the control unit 26. The displacement sensor 66 sends a detection signal related to the amount of displacement of the right end of the second main body 61 to the control unit 26. The displacement sensor 66 may also be mounted at a location other than the right end of the second main body 61.

[0096] The control unit 26, for example, displays a table showing the relationship between the weight of the roll P and the target value of the displacement of the roll support member 30 (see reference). Figure 9 The weight of the roll P here refers to the weight of one roll P. Furthermore, the weight of the roll P refers to the weight after deducting the weight of the bobbin (i.e., the weight of the yarn Y contained in the roll P). More precisely, the displacement of the roller support member 30 is the displacement of the right end of the second main body 61. Figure 9 In the example shown, when the weight of roll P (hereinafter referred to as weight) is 0 kg, the target value of the displacement of the roll support member 30 (hereinafter referred to as displacement) is 0 mm. When the weight is W / 200 (in kg), the target value of the displacement is X / 50 (in mm). When the weight is 6W / 25, the target value of the displacement is 2X / 5. When the weight is W, the target value of the displacement is X. The relationship between the weight of roll P and the target value of the displacement is determined independently of the set value of the contact pressure. For example, the value of W representing the weight of roll P is 16 kg, and the value of X representing the target value of the displacement of the roll support member 30 is 8.0 mm, but is not limited to this.

[0097] (Displacement control)

[0098] The control unit 26 controls the displacement during the winding operation. (See reference...) Figure 10 The flowchart illustrates the sequence of displacement control during the winding operation. As an initial state, the state of the wire winding machine 4 is, for example, the state before starting to wind the wire Y into multiple bobbins B respectively. The state before winding can also be, for example, the state before hooking multiple wires onto the wire winding machine 4 (illustration omitted). Alternatively, the state before winding can also be, for example, the state before the aforementioned bobbin switching (illustration omitted).

[0099] First, the operator inputs the set value of the contact pressure applied by the contact roller 25 to each roll P into the control unit 26. Figure 10 (See step S101). The operator can, for example, input a set value to the control unit 26 via the input section (not shown). Alternatively, the operator can select a set value for the contact pressure from a pre-defined selection. During the winding operation performed after step S101, the control unit 26 controls the contact pressure based on the input set value. The control unit 26 controls the electro-pneumatic pressure regulating valve 39 (see step S101) according to the set value of the contact pressure. Figure 2 This controls the pressure of the compressed air supplied to the cylinder 35. Furthermore, during this winding operation, the control unit 26 controls the amount of displacement as follows.

[0100] Next, the control unit 26 controls each component of the yarn winding machine 4 as needed to begin winding the yarn Y into multiple new bobbins B (winding operation) (step S102). During the winding operation, the control unit 26 continuously calculates the weight of each package P being formed and detects the actual displacement (step S103). Regarding the calculation of the weight of each package P, more specifically, the control unit 26, for example, pre-stores information on the amount of yarn Y ejected from the spinning device 3 per unit time. In addition, the control unit 26 counts the elapsed time (winding time) from the start of the winding operation. The product of the amount ejected per unit time and the winding time is calculated as the current value of the weight of each package P (i.e., the weight of the yarn Y wound into each bobbin B) (hereinafter referred to as the current weight). The detection of the actual displacement is continuously performed by the displacement sensor 66. The information on the actual displacement is information related to the actual tilt angle of the contact roller 25, including the influence of the contact pressure. The value of the actual displacement corresponds to the actual angle correlation value of the present invention.

[0101] Next, the control unit 26 obtains the target value of the displacement (step S104). More specifically, the control unit 26 performs the following processing. The control unit 26 considers the relationship between the weight of the roll P included in the above table and the target value of the displacement, and calculates the target value of the displacement based on the current weight value, for example, by a known linear interpolation. Next, the control unit 26 calculates the change value of the displacement based on the difference between the target value of the displacement and the actual displacement (step 105). As a method for calculating the change value of the displacement, known control methods, such as PID control, can also be used. However, it is not limited to this; as a known control method, for example, known on / off control can also be used. Next, the control unit 26 calculates the displacement to cylinder 41 (refer to...) based on the change value of the displacement. Figure 4The control unit 26 calculates the target value based on the current and changed value of the compressed air pressure (step S106). Next, the control unit 26 controls the electro-pneumatic pressure regulating valve 47 (refer to step S107) based on the target value of the compressed air pressure. Figure 4 Therefore, the pressure of the compressed air is updated (step S108). After the above processing, the control unit 26 determines, for example, whether the roll P is full based on the winding time (step S109). If the control unit 26 determines that the roll P is not yet full (step S109: No), it returns to step S103. If the control unit 26 determines that the roll P is full (step S109: Yes), it ends the winding operation of the currently formed roll P (step S110). As described above, the tilting mechanism 40 is controlled based on information of the actual angle correlation value (see reference). Figure 4 This is done so that the tilt angle becomes the target value. The target value is uniquely determined based on the target value of the displacement obtained according to the current weight.

[0102] As described above, the tilting mechanism 40 is controlled so that the tilt angle reaches a predetermined target value, based on information about the actual angle correlation value related to the actual tilt angle of the contact roller 25. Therefore, regardless of the set value of the contact pressure, deviation of the tilt angle from the target value can be suppressed. Thus, even if the setting of the contact pressure applied to multiple rolls P is changed, deviation of the contact pressure between the multiple rolls P can be suppressed.

[0103] Furthermore, since the contact roller 25 generally extends relatively long in the horizontal direction, it is easy to detect the amount of displacement in the vertical direction of the second main body 61 even if the change in the tilt angle of the contact roller 25 is small. Therefore, the amount of displacement of the second main body 61 is effective as a physical quantity to be detected instead of the tilt angle. Moreover, by controlling the tilting mechanism 40 by detecting the amount of displacement of the second main body 61, the tilt angle of the contact roller 25 can be substantially controlled. Therefore, it is possible to effectively suppress deviations in contact pressure between multiple rolls P.

[0104] Furthermore, by using cylinder 41 as the drive source for tilting mechanism 40 and adjusting the output of cylinder 41 using electro-pneumatic pressure regulating valve 47, the construction of the thread winding machine 4 can be simplified. Additionally, the output of the cylinder can be reliably adjusted with a simple structure.

[0105] In addition, by using a cylinder 41, which is cheaper than a hydraulic cylinder (not shown), the increase in component cost of the wire winding machine 4 can be suppressed.

[0106] Furthermore, the second main body 61 of the tilting mechanism 40 is driven by the cylinder 41 to raise and lower the rear end of the roller support member 30. Therefore, compared to a structure that raises and lowers the inner portion of the roller support member 30 in the axial direction, the change in the tilt angle relative to the displacement of the roller support member 30 can be suppressed to a smaller extent. Thus, fine adjustments to the tilt angle are possible.

[0107] Furthermore, the tilting mechanism 40 has a clamping mechanism 42. Therefore, a greater force is required to increase the displacement of the roller support member 30. Thus, even when it is difficult to precisely adjust the thrust of the cylinder 41, the displacement of the roller support member 30 can be controlled with high precision. Therefore, the tilt angle of the contact roller 25 can be controlled with high precision.

[0108] Furthermore, the roller support member 30 can be supported stably with double support via the second main body 61 and the cylinder 35. Therefore, the contact pressure can be adjusted stably.

[0109] Next, variations of the aforementioned embodiments will be described. However, for parts having the same structure as the aforementioned embodiments, the same reference numerals will be used and their descriptions will be omitted as appropriate.

[0110] (1) In the aforementioned embodiment, the thread winding machine 4 has a displacement sensor 66, and the control unit 26 controls the displacement amount. However, it is not limited to this. Hereinafter, refer to Figure 11 (a)~ Figure 12 Please provide a detailed explanation. Figure 11 (a) is a table showing the relationship between the weight of each roll P in the modified example and the target value of the compressed air pressure. Figure 11 (b) is a table showing the relationship between the contact pressure and the adjustment amount of the compressed air pressure. Figure 12 This is a flowchart illustrating the control of compressed air pressure during the winding of the modified yarn. The control unit 26, for example, displays a table (see reference) showing the relationship between the weight of each roll P and the target value of the pressure of the compressed air supplied to the cylinder 41 (hereinafter simply referred to as the compressed air pressure). Figure 11 (a) is stored in RAM. Figure 11In the example shown in (a), when the weight of roll P (hereinafter simply referred to as weight) is 0 kg, the target value of the compressed air pressure is 2A / 5 (in kPa, the same below). When the weight is W / 200 (in kg, the same below), the target pressure value is 3A / 4. When the weight is 6W / 25, the target pressure value of the compressed air is 4A / 5. When the weight is W, the target pressure value of the compressed air is A. The value of W, representing the weight of roll P, is, for example, 16 kg, and the value of A, representing the target pressure value, is, for example, 465 kPa, but is not limited to these. Furthermore, the control unit 26 displays a table showing the relationship between the set value of the contact pressure and the adjustment amount of the compressed air pressure (see...). Figure 11 (b) is stored in RAM. Figure 11 In the example shown in (b), when the contact pressure setting is 2C / 3 (in N, the same below), which is C / 3 lower than the standard, the adjustment amount for the target value of the compressed air pressure is +ΔA (in kPa, the same below). When the contact pressure setting is C (equal to the standard), the adjustment amount for the target value of the compressed air pressure is zero. When the contact pressure setting is 4C / 3 (C / 3 higher than the standard), the adjustment amount for the target value of the compressed air pressure is -ΔA. The value of C, representing the contact pressure setting, is, for example, 150 N, and the value of ΔA, representing the adjustment amount for the target value of the compressed air pressure, is, for example, 30 kPa, but is not limited to these.

[0111] The control unit 26 controls the compressed air pressure by taking into account the set value of the contact pressure during the winding operation. (See reference...) Figure 12 The flowchart illustrates the sequence of compressed air pressure control during the winding operation. As an initial state, the state of the wire winder 4 is, for example, before starting to wind wire Y into multiple bobbins B. First, the operator inputs the contact pressure setpoint into the control unit 26. Figure 12 (See step S201). In the winding operation performed after step S201, the control unit 26 controls the contact pressure based on the input set value. Furthermore, in this winding operation, the control unit 26 controls the compressed air pressure as follows: The control unit 26 starts the winding operation (step S202). During the winding operation, the control unit 26 continuously calculates the weight of each roll P being formed (step S203). Next, the control unit 26 obtains the target value for the compressed air pressure (step S204). More specifically, the control unit 26 considers... Figure 11 The table shown in (a) contains the relationship between the weight of package P and the target value of compressed air pressure. Based on the current weight value, the target value of compressed air pressure is calculated, for example, by linear interpolation. This target value is a provisional target value before considering the contact pressure. Next, the control unit 26 reads... Figure 11The table shown in (b) obtains information on the adjustment amount of the compressed air pressure corresponding to the current set value of the contact pressure (step S205). The information on the adjustment amount of the compressed air pressure is equivalent to the force adjustment information of the present invention. The control unit 26 updates the target value of the compressed air pressure by adding the adjustment amount to the temporary target value (step S206). Then, the control unit 26 controls the electro-pneumatic pressure regulating valve 47 based on the updated target value to update the compressed air pressure (step S207). After that, the control unit 26 determines whether the roll P is full (step S208). If the control unit 26 determines that the roll P is not yet full (step S208: No), it returns to step S203. If the control unit 26 determines that the roll P is full (step S208: Yes), it ends the winding operation of the currently formed roll P (step S209). As described above, by using the force adjustment information corresponding to the set value of the contact pressure, an appropriate force (the second force of the present invention) corresponding to the weight of the multiple rolls P can be applied to the contact roller 25. Therefore, the tilt angle can be adjusted appropriately. Thus, similar to the above embodiment, even if the setting of the contact pressure applied to the multiple rolls P is changed, it is possible to suppress the deviation of the contact pressure between the multiple rolls P.

[0112] (2) In the embodiments described above, the pressure of the compressed air supplied to the cylinder 41 is adjusted by the electro-pneumatic pressure regulating valve 47. However, this is not a limitation. The pressure of the compressed air can also be adjusted, for example, by an electrically operated valve (not shown). This valve can also be configured to adjust its opening continuously or discontinuously. In this case, the valve corresponds to the pressure regulating unit of the present invention.

[0113] (3) In the embodiments described above, the tilting mechanism 40 (angle adjustment unit) has a cylinder 41. However, it is not limited to this. A hydraulic cylinder, for example not shown, may be provided instead of the cylinder 41. In this case, the hydraulic cylinder is equivalent to the fluid pressure cylinder of the present invention.

[0114] (4) In the embodiments described above, the angle adjustment unit has a fluid pressure cylinder. However, it is not limited to this. The angle adjustment unit may also not have a fluid pressure cylinder. Instead of a fluid pressure cylinder, a magnetic cylinder may be provided, for example, to change the thrust by means of an adjustable magnetic force. Alternatively, instead of a fluid pressure cylinder, a gear and rack mechanism, for example, not shown, may be provided.

[0115] (5) In the embodiments described above, the clamping mechanism 42 has a first clamping portion 50 and a second clamping portion 60. However, it is not limited to this. Instead of the clamping mechanism 42, for example, it can be configured such that a cylinder 41 directly raises and lowers the right end of the second main body portion 61. In this case, a tension coil spring (not shown) is preferably positioned, for example, between the frame 28 and the second main body portion 61. Thus, the greater the displacement of the right end of the second main body portion 61 relative to its initial position in the vertical direction, the greater the force required to further increase the displacement. In this case, the tension coil spring corresponds to the clamping mechanism of the present invention. Alternatively, the clamping mechanism may not be provided.

[0116] (6) In the embodiments described above, the tilting mechanism 40 is disposed at the rear end of the frame 28, and the cylinder 35 applies force to the front end of the roller support member 30. However, this is not a limitation. Alternatively, the tilting mechanism 40 may be disposed at the front end of the frame 28, and the cylinder 35 may be disposed to apply force to the rear end of the roller support member 30. Alternatively, the tilting mechanism 40 may be disposed at the midpoint in the front-rear direction of the frame 28 as long as it is configured to change the tilt angle of the roller support member 30. In addition, the cylinder 35 may be disposed at the midpoint in the front-rear direction of the roller support member 30 as long as it is configured to change the contact pressure.

Claims

1. A thread winding machine, characterized in that, have: Organism; A tube support, which holds multiple tubes arranged in a predetermined axial direction having a horizontal component, and is cantilevered and supported on the body; A contact roller, which extends at least along the axial direction, applies contact pressure to multiple packages formed by winding multiple filaments onto the plurality of bobbins respectively; The contact pressure changing unit can change the contact pressure by applying a first force to the contact roller that can at least change the magnitude in the vertical direction; An angle-changing unit can change the tilt angle of the contact roller relative to the horizontal direction by applying a second force, which is different from the first force and can at least change the magnitude in the vertical direction, to the contact roller. The detection unit detects information about the actual angle correlation value related to the actual tilt angle of the contact roller; as well as Control Department; The control unit controls the angle change unit in such a way that the actual angle correlation value becomes a target value, the target value being determined based on the weight of the yarn wound onto the plurality of bobbins respectively and independently of the set value of the contact pressure.

2. The thread winding machine according to claim 1, characterized in that, It has a movable part integral with the contact roller and capable of moving at least in the vertical direction. The detection unit is configured to detect information related to the amount of displacement of the moving part in the vertical direction as information of the actual angle correlation value.

3. A thread winding machine, characterized in that, have: Organism; A tube support, which holds multiple tubes arranged in a predetermined axial direction having a horizontal component, and is cantilevered and supported on the body; A contact roller, which extends at least along the axial direction, applies contact pressure to multiple packages formed by winding multiple filaments onto the plurality of bobbins respectively; The contact pressure changing unit can change the contact pressure by applying a first force to the contact roller that can at least change the magnitude in the vertical direction; An angle-changing unit can change the tilt angle of the contact roller relative to the horizontal direction by applying a second force, which is different from the first force and can at least change the magnitude in the vertical direction, to the contact roller. as well as Control Department; The control unit uses force adjustment information, which corresponds to the set value of the contact pressure and is related to the adjustment amount of the second force, to control the angle changing unit.

4. The thread winding machine according to any one of claims 1 to 3, characterized in that, The angle changing unit has: A fluid pressure cylinder, serving as a drive source, is used to apply the second force to the contact roller; and The pressure adjustment unit is configured to adjust the pressure of the fluid supplied to the fluid pressure cylinder.

5. The thread winding machine according to claim 4, characterized in that, The fluid pressure cylinder is a pneumatic cylinder.

6. The thread winding machine according to claim 5, characterized in that, The pressure adjustment unit is an electro-pneumatic pressure regulating valve.

7. The thread winding machine according to any one of claims 4 to 6, characterized in that, The angle changing unit has: A roller support component supports the contact roller so that it can rotate freely; as well as The lifting unit, driven by the fluid pressure cylinder, raises and lowers one end of the roller support component along its axial direction.

8. The thread winding machine according to claim 7, characterized in that, The lifting part has a clamping mechanism that is arranged between the fluid pressure cylinder and the roller support member in the direction of force transmission of the fluid pressure cylinder. The larger the displacement of one end of the roller support member in the axial direction relative to the initial position in the vertical direction, the greater the force required to further increase the displacement.

9. The thread winding machine according to claim 7 or 8, characterized in that, The contact pressure changing unit is configured to apply the first force to the contact roller by applying a force to the other end of the roller support member in the axial direction.

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