thread winding machine

Abstract

This technology suppresses variations in contact pressure between multiple packages, even when the contact pressure settings applied to multiple packages are changed. [Solution] The yarn winding machine 4 comprises a machine base 20, a bobbin holder 24, a contact roller 25, an air cylinder 35, a tilting mechanism 40, a displacement sensor 66, and a control unit 26. The control unit 26 controls the tilting mechanism 40 to set the actual angle-related value detected by the displacement sensor 66 to a target value determined according to the weight of the yarn wound onto each of the multiple bobbins B and independently of the contact pressure setting value.

Description

Technical Field

[0001] The present invention relates to a yarn winder.

Background Art

[0002] The yarn winders disclosed in Patent Documents 1 and 2 include a bobbin holder and a contact controller. The bobbin holder is supported in a cantilever manner in an axial direction substantially parallel to the horizontal direction, and supports a plurality of bobbins arranged in the axial direction. The contact controller applies contact pressure to the surface of each of a plurality of packages formed by winding a plurality of yarns around the plurality of bobbins, and shapes the plurality of packages.

[0003] Patent Document 1 further discloses a tilting mechanism (angle changing portion) having an air cylinder for adjusting the tilt angle of the contact controller with respect to the horizontal direction. The reason for this is to make the contact controller follow the deflection of the bobbin holder caused by the winding thickness of the plurality of packages (i.e., the increase in the weight of the packages), and to suppress the variation in the contact pressure between the plurality of packages. More specifically, the angle changing portion adjusts the position of the end portion of the contact controller in the vertical direction in the above axial direction according to the thrust of the air cylinder. Thereby, the tilt angle of the contact controller is adjusted.

[0004] Patent Document 2 further discloses a contact pressure cylinder (contact pressure changing portion) that applies at least a vertical force to the contact controller. The combined force of the variable force applied to the contact controller by the contact pressure cylinder and the force caused by the self-weight of the contact controller acts on the plurality of packages as contact pressure. The setting of the contact pressure changing portion can be arbitrarily switched on the user side according to the type of package or the like.

Prior Art Documents

Patent Documents

[0005]

Patent Document 1

Patent Document 2

[0006] The inventors of this application have been investigating the application of the contact pressure changing section described in Patent Document 2 to the thread winding machine described in Patent Document 1. In doing so, they found that the relationship between the thrust from the air cylinder of the angle changing section and the inclination angle of the contact roller changes depending on the setting of the magnitude of the contact pressure. In this case, it was found that even though the angle changing section is provided, there is a risk that the contact pressure may vary between multiple packages in the axial direction.

[0007] The objective of the present invention is to suppress variations in contact pressure among multiple packages, even when the contact pressure settings applied to multiple packages are changed. [Means for solving the problem]

[0008] The first invention's yarn winding machine comprises a machine base, a bobbin holder cantilevered to the machine base for holding a plurality of bobbins in a predetermined axial direction having a horizontal component, a contact roller extending at least in the axial direction and applying contact pressure to a plurality of packages formed by winding a plurality of threads onto each of the plurality of bobbins, a contact pressure changing unit capable of changing the contact pressure by applying a first force to the contact roller whose magnitude is at least changeable in the vertical direction, an angle changing unit capable of changing the inclination angle of the contact roller with respect to the horizontal direction by applying a second force to the contact roller, which is different from the first force and whose magnitude is at least changeable in the vertical direction, a detection unit for detecting information on an actual angle-related value relating to the actual inclination angle of the contact roller, and a control unit, wherein the control unit controls the angle changing unit so that the actual angle-related value is set to a target value determined according to the weight of the thread wound onto each of the plurality of bobbins and independently of the set value of the contact pressure.

[0009] In the configuration of the present invention, the relationship between the second force and the inclination angle of the contact roller may change depending on the contact pressure. Therefore, in the present invention, the angle changing unit is controlled so that the actual angle-related value relating to the actual inclination angle is set to a target value that is determined independently of the set value of the contact pressure. This makes it possible to suppress deviations of the actual angle-related value from the target value, regardless of the set value of the contact pressure. Consequently, even if the contact pressure settings applied to multiple packages are changed, it is possible to suppress variations in contact pressure among the multiple packages.

[0010] The thread winding machine of the second invention is characterized in that, in the first invention, it comprises a movable part that is integral with the contact roller and is movable at least in the vertical direction, and the detection unit is configured to detect information regarding the amount of vertical displacement of the movable part as information regarding the actual angle-related value.

[0011] Because the angle of deflection of the bobbin holder and the change in the tilt angle of the contact roller relative to the horizontal direction are very small, a configuration that detects the tilt angle itself will result in low detection accuracy. In this respect, since the contact roller generally extends long in the horizontal direction, the amount of displacement of the moving part in the vertical direction is easily detected even if the change in the tilt angle is small. For this reason, the amount of displacement of the moving part is effective as a physical quantity to be detected instead of the tilt angle. Then, by detecting the amount of displacement of the moving part and controlling the angle changing part, the tilt angle of the contact roller can be substantially controlled. Consequently, variations in contact pressure between multiple packages can be effectively suppressed.

[0012] The third invention's yarn winding machine comprises a machine base, a bobbin holder that cantilever-supported on the machine base and holds a plurality of bobbins arranged in a predetermined axial direction having a horizontal component, a contact roller that extends at least in the axial direction and applies contact pressure to a plurality of packages formed by winding a plurality of threads onto the plurality of bobbins, a contact pressure changing unit that can change the contact pressure by applying a first force to the contact roller whose magnitude is at least changeable in the vertical direction, an angle changing unit that can change the inclination angle of the contact roller with respect to the horizontal direction by applying a second force to the contact roller, which is different from the first force and whose magnitude is at least changeable in the vertical direction, and a control unit, wherein the control unit controls the angle changing unit using force adjustment information relating to the adjustment amount of the second force according to the set value of the contact pressure.

[0013] In this invention, force control information corresponding to the set value of the contact pressure allows an appropriate second force corresponding to the weight of multiple packages to 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 multiple packages is changed, variations in contact pressure among multiple packages can be suppressed.

[0014] The fourth invention is characterized in that, in any of the first to third inventions, the angle changing section comprises a fluid pressure cylinder as a drive source for applying the second force to the contact roller, and a pressure adjustment section configured to adjust the pressure of the fluid supplied to the fluid pressure cylinder.

[0015] In this invention, the structure of the yarn winding machine can be simplified by applying a fluid pressure cylinder as the drive source for the angle changing section and adjusting the output of the fluid pressure cylinder in the pressure adjustment section.

[0016] The fifth invention is a thread winding machine characterized in that, in the fourth invention, the fluid pressure cylinder is an air cylinder.

[0017] In this invention, for example, by applying an air cylinder, which is less expensive than a hydraulic cylinder, the increase in component costs for a thread winding machine can be suppressed.

[0018] The sixth invention is a thread winding machine characterized in that, in the fifth invention, the pressure adjustment unit is an electro-pneumatic regulator.

[0019] This invention allows for reliable adjustment of the air cylinder output with a simple configuration.

[0020] The thread winding machine of the seventh invention is characterized in that, in any of the fourth to sixth inventions, the angle changing section comprises a roller support member that rotatably supports the contact roller, and a lifting section driven by the fluid pressure cylinder that raises and lowers one end of the roller support member in the axial direction.

[0021] In this invention, compared to a configuration in which, for example, the inner portion of the roller support member in the axial direction is raised and lowered, the change in the tilt angle with respect to the displacement of the roller support member can be kept small. Therefore, fine adjustment of the tilt angle can be performed.

[0022] The eighth invention is a thread winding machine, characterized in that, in the seventh invention, the lifting section is positioned between the fluid pressure cylinder and the roller support member in the transmission direction in which the force of the fluid pressure cylinder is transmitted, and has an intervening mechanism configured such that the greater the displacement of one end of the roller support member in the axial direction relative to its initial vertical position, the greater the force required to further increase the displacement.

[0023] In this invention, a greater force is required to increase the displacement of the roller support member. Therefore, even when it is difficult to precisely adjust the thrust of the fluid pressure cylinder, the displacement of the roller support member can be controlled with high precision. Consequently, the tilt angle of the contact roller can be controlled with high precision.

[0024] The thread take-up machine according to 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 roller support member in the axial direction.

[0025] In the present invention, the lifting part and the contact pressure changing part can stably support the roller support member in a two-sided manner. Therefore, the contact pressure can be stably adjusted.

Brief Description of Drawings

[0026] [Figure 1] It is a side view of a spinning and drawing machine having a thread take-up machine according to the present embodiment. [Figure 2] It is a front view of the thread take-up machine. [Figure 3] It is a perspective view of the rear part of the contact roller and the tilting mechanism. [Figure 4] It is a view of the tilting mechanism seen from the rear. [Figure 5] (a) to (c) are diagrams showing the operation of the tilting mechanism. <​​​​​​​​​​​​​​​​​​​​​[Modes for carrying out the invention]

[0027] Next, embodiments of the present invention will be described. Figure 1 is a side view of a spinning take-up machine 1 having a yarn winding machine 4 (described later) according to this embodiment. The vertical direction in Figure 1 is defined as the vertical direction. The vertical direction is parallel to the vertical direction in which gravity acts. The left-right direction in Figure 1, which is perpendicular to the vertical direction, is defined as the front-back direction (axial direction of the present invention). The direction perpendicular to both the front-back direction and the vertical direction (perpendicular direction in the paper) is defined as the left-right direction.

[0028] (Outline of a spinning take-up machine) The spinning take-up machine 1 takes up multiple threads Y spun from the spinning device 3 and winds them onto multiple bobbins B to form multiple packages P. The spinning take-up machine 1 comprises a first godet roller 11, a second godet roller 12, and a yarn winding machine 4.

[0029] The first godet roller 11 is a roller whose axial direction is approximately parallel to the left-right direction. The first godet roller 11 is located above the front end of the yarn winding machine 4. The first godet roller 11 is rotationally driven by a motor (not shown). The second godet roller 12 is a roller whose axial direction is approximately parallel to the left-right direction. The second godet roller 12 is located above and behind the first godet roller 11. The second godet roller 12 is rotationally driven by a motor (not shown).

[0030] The yarn winding machine 4 performs a winding operation in which multiple threads Y are wound onto multiple bobbins B to form multiple packages P. The more specific configuration of the yarn winding machine 4 will be described with reference to Figures 1 to 4. Figure 2 is a front view of the yarn winding machine 4. Figure 3 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 is a view of the tilting mechanism 40 from the rear. The yarn winding machine 4 includes a machine base 20, multiple pivot guides 21, multiple traverse guides 22, a turret 23, two bobbin holders 24, a contact roller 25, and a control unit 26.

[0031] As shown in Figure 1, the machine base 20 has a machine base body 27 and a frame 28. The machine base body 27 is erected at the rear of the thread winding machine 4. The machine base body 27 supports a turret 23, etc. The frame 28 is, for example, a hollow columnar member. The frame 28 is fixed to the upper part of the machine base body 27 and extends forward from the machine base body 27. The frame 28 supports a contact roller 25. As shown in Figure 3, a notch is formed at the upper part of the rear end of the frame 28 by 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, which will be described later, is provided at the rear end of the frame 28.

[0032] Multiple pivot guides 21 are provided, each corresponding to one of the multiple threads Y. Each of the multiple pivot guides 21 is a guide that acts as a pivot point when the corresponding thread Y is spun. The multiple pivot guides 21 are arranged in the front-to-back direction.

[0033] Multiple traverse guides 22 are provided, each corresponding to one of the multiple threads Y. Each traverse guide 22 is a guide for traversing the corresponding thread Y. The multiple traverse guides 22 are arranged in a row in the front-to-back direction. The multiple traverse guides 22 are driven by a traverse motor (not shown). The thread Y placed on the traverse guides 22 is traversed with the pivot guide 21 as the pivot point.

[0034] The turret 23 is a disc-shaped member whose axial direction is approximately parallel to the front-rear direction. The turret 23 is rotatably supported on the machine base body 27. The turret 23 is rotationally driven by a turret motor (not shown). The turret 23 cantilever-supports two bobbin holders 24. The turret 23 moves the two bobbin holders 24 by rotating around a pivot axis approximately parallel to the front-rear direction. The turret 23 is configured to rotate in accordance with the increase in the amount of yarn Y wound onto the bobbin B during yarn winding (see solid arrow in Figure 2).

[0035] Each of the two bobbin holders 24 is configured to rotatably hold (support) multiple bobbins B arranged in the front-to-back direction. The two bobbin holders 24 are positioned point-symmetrically with respect to the rotation axis center of the turret 23. Each bobbin holder 24 extends forward from the turret 23. In other words, the two bobbin holders 24 are cantilevered by the machine base body 27 via the turret 23. The axial directions of the two bobbin holders 24 are approximately parallel to the front-to-back direction. The front end of the bobbin holder 24 is generally the working side where operations such as mounting bobbins B onto the bobbin holder 24 are performed. Multiple bobbins B are mounted on each bobbin holder 24 in the front-to-back direction. The number of bobbins B mounted on one bobbin holder 24 is, for example, 16, but is not limited to this. Each of the two bobbin holders 24 is rotated by an individual winding motor (not shown).

[0036] The contact roller 25 is a roller positioned directly above the upper bobbin holder 24. The axial direction of the contact roller 25 is approximately parallel to the front-rear direction. The contact roller 25 contacts the surfaces of multiple packages P supported by the upper bobbin holder 24, thereby applying contact pressure to the surfaces of the packages P being formed and shaping the packages P.

[0037] In this embodiment, the contact roller 25 is pivotably supported on the frame 28 via a roller support member 30. As shown in Figures 1 to 3, the roller support member 30 has, for example, a support portion 31, an arm portion 32, and a pivot shaft 33. The support portion 31 rotatably supports the contact roller 25 at both ends in the front-rear direction. The arm portion 32 is, for example, a rod-shaped member. One end of the arm portion 32 is connected to the support portion 31 and extends toward the frame 28 in a direction perpendicular to the front-rear direction. The pivot 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 pivotably supported on the frame 28. The rear end of the pivot shaft 33 is supported by a tilting mechanism 40, which will be 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 to this.

[0038] As shown in Figure 2, the thread winding machine 4 of this embodiment further includes an air cylinder 35 (contact pressure changing unit of the present invention). The air cylinder 35 is for changing the contact pressure on a plurality of packages P by the contact roller 25 according to the pressure of the supplied compressed air. The air cylinder 35 has a cylinder body 37 and a rod end 36. The rod end 36 is pivotably supported by a support part 28L fixed to the lower part of the front end of the frame 28, for example, via a pivot shaft 36a extending along the front-rear direction. The rod end 36 is fixed to the tip of the piston rod (not shown in numerals) of the air cylinder 35 and is movable relative to the cylinder body 37. The cylinder body 37 is pivotably connected via a joint 38 to the intermediate part of the arm part 32 in the extending direction of the arm part 32. An electro-pneumatic regulator 39 is connected to the cylinder body 37. The electro-pneumatic regulator 39 is electrically connected to a control unit 26. The electro-pneumatic regulator 39 adjusts the pressure of the compressed air supplied to the cylinder body 37 according to commands from the control unit 26. The air cylinder 35 applies a force F (see Figure 2) to the roller support member 30 having at least a vertical component. This applies a force (the first force of the present invention) to the contact roller 25 via the roller support member, having at least a vertical component. The magnitude of the force F varies depending on the compressed air pressure. The compressed air pressure is not typically changed while the yarn Y is being wound onto the bobbin B. Information regarding the compressed air pressure (i.e., contact pressure information) is pre-stored in the control unit 26, for example, 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.

[0039] The control unit 26 includes a CPU, ROM, RAM, etc. The control unit 26 controls each part using the CPU according to a program stored in the ROM. The control unit 26 also has an input unit (not shown) for the operator to perform input tasks (keyboard, touch panel, mouse, etc.).

[0040] In the yarn winding machine 4 having the above configuration, when the upper bobbin holder 24 is rotated, the yarn Y spun by the traverse guide 22 is wound onto the bobbin B to form a package P. When the package P is fully wound, the turret 23 is rotated. This swaps the upper and lower positions of the two bobbin holders 24. That is, the bobbin holder 24 that was on the lower side moves to the upper side. Subsequently, the yarn Y is transferred from the multiple packages P to the multiple bobbins B (multiple new bobbins B) mounted on the upper bobbin holder 24 (bobbin switching). (Figure not shown). After the bobbin switching, the yarn Y is wound onto the multiple new bobbins B, thereby forming multiple packages P. The bobbin holder 24 with the multiple fully wound packages P mounted on it is moved to the lower side. The multiple fully wound packages P are collected, for example, by a package recovery device (not shown). The operation of the yarn winding machine 4 from the start of winding multiple threads Y onto multiple bobbins B until the winding is completed is the winding operation described above.

[0041] (tilting mechanism) The configuration of the tilting mechanism 40 (angle changing section of the present invention) will be described with reference to Figures 3 and 4. As shown in Figures 3 and 4, the tilting mechanism 40 comprises an air cylinder 41 (fluid pressure cylinder of the present invention) and an intervening mechanism 42 (lifting section of the present invention). The air cylinder 41 is the driving source for the intervening mechanism 42. The intervening mechanism 42 is interposed between the rear end of the roller support member 30 and the air cylinder 41 in the direction of force transmission of the air cylinder 41. The air cylinder 41 and the intervening mechanism 42 are provided at the rear end of the frame 28 (i.e., the end on the base side of the bobbin holder 24 in the front-rear direction). The rear end of the roller support member 30 corresponds to one end in the axial direction of the present invention. The front end of the roller support member 30 corresponds to the other end in the axial direction of the present invention.

[0042] The air cylinder 41 is used to displace the rear end of the roller support member 30 in the vertical direction via an intervening mechanism 42. The air cylinder 41 is a drive source for applying a force having at least a vertical component (the second force of the present invention) to the contact roller 25. The air cylinder 41 is housed at the rear end of the frame 28 and is supported by the frame 28. As shown in Figure 4, the air cylinder 41 has a cylinder body 43 and a piston rod 45. The cylinder body 43 has an operating chamber 44 to which compressed air (the fluid of the present invention) is supplied. The piston rod 45 expands and contracts with the supply and discharge of compressed air to the operating chamber 44. An electro-pneumatic regulator 47 (pressure adjustment unit of the present invention) is connected to the operating chamber 44. The electro-pneumatic regulator 47 is electrically connected to a control unit 26. The electro-pneumatic regulator 47 adjusts the pressure of the compressed air supplied to the operating chamber 44 according to commands 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 housed in the aforementioned notch of the frame 28 and is extendable and retractable in the vertical direction. An upper end surface 46 is formed at the tip of the piston rod 45, which is positioned approximately parallel to the horizontal direction.

[0043] The intervening mechanism 42 is interposed between the rear end of the roller support member 30 and the air cylinder 41 to transmit the thrust of the air cylinder 41 to the rear end of the roller support member 30. The intervening mechanism 42 includes, for example, a first intervening portion 50 and a second intervening portion 60.

[0044] The first intervening part 50 is directly pressed by the piston rod 45 and is intended to transmit the thrust of the air cylinder 41 to the second intervening part 60. As shown in Figure 4, the first intervening part 50 is pivotably supported on the frame 28 via a first pivot shaft 51 that extends along the front-rear direction. The first intervening part 50 has a first main body part 52, a first roller 53, and a support part 54.

[0045] The first main body 52 is a roughly rectangular member when viewed from the rear. The first main body 52 is pivotably supported on the side surface 28c of the frame 28 via the first pivot shaft 51 and is configured to support the first roller 53 and the support part 54. The first roller 53 is positioned at a predetermined distance to the left (right side of the paper in Figure 4) from the first pivot shaft 51. The first roller 53 is a roller rotatably supported on the first main body 52 with an axis 59 that is roughly parallel to the first pivot shaft 51 as its axis of rotation, and is in contact with the upper end surface 46 of the piston rod 45. The support part 54 is for supporting the second intervening part 60 from below. The support part 54 is a roughly T-shaped member when viewed from the rear. The lower part of the support part 54 is detachably attached to the first main body 52 by a fixing member 55. The support portion 54 has a roughly U-shaped notch formed in it, as viewed from the rear, so as to cover the circumferential surface of the first roller 53 except for the lower part. The support portion 54 has an upper surface 56. The upper surface 56 has a support surface 57 (see the thick line in Figure 4). The support surface 57 supports the second intervening portion 60 by contacting the second roller 62, which will be described later, from below. In other words, the support surface 57 is the part of the upper surface 56 that can come into contact with the second roller 62. The part of the support surface 57 that comes into contact with the second roller 62 is called the contact point 58.

[0046] For the sake of explanation, the position of the roller support member 30 when it is approximately horizontal will be referred to as the initial position of the roller support member 30. Also for the sake of explanation, the amount of vertical displacement of the rear end of the roller support member 30 relative to its initial position will be referred to simply as the displacement amount. The support surface 57 extends upward as it moves away from the first pivot axis 51 in the left-right direction, for example, when the displacement of the rear end of the roller support member 30 is zero. The upper side is, that is, the side from which the piston rod 45 protrudes. The support surface 57 is a curved surface whose inclination with respect to the horizontal increases as it approaches the first pivot axis 51 in the horizontal direction. The support surface 57 is located between the first roller 53 and the first pivot axis 51 in the left-right direction.

[0047] The second intervening portion 60 is for transmitting the thrust of the air cylinder 41, transmitted via the first intervening portion 50, to the rear end of the roller support member 30. The second intervening portion 60 has a second main body portion 61 (movable portion of the present invention) and a second roller 62.

[0048] The second main body 61 is a roughly rectangular member when viewed from the rear. The second main body 61 extends in the left-right direction. At its left end (right end of Figure 4), the second main body 61 is supported by the frame 28 so as to be able to swing up and down by a second pivot shaft 63, which is positioned differently from the first pivot shaft 51. At the right end of the second main body 61 (left end of Figure 4), there is a connecting portion 64 that is connected to the rear end of the roller support member 30 and supports the roller support member 30 so as to be able to swing. 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 movable (swingable) at least vertically, integrally with the contact roller 25. The second main body 61 is driven by an air cylinder 41 to raise and lower the rear end of the roller support member 30.

[0049] The second roller 62 is positioned between the second pivot axis 63 and the connecting portion 64 in the left-right direction, and is located behind the second main body portion 61 (towards the front of the page in Figure 4). The second roller 62 is rotatably supported on the second main body portion 61 with an axis 65 substantially parallel to the second pivot axis 63 as its axis of rotation, and is directly supported by the support portion 54 by contacting the support surface 57 of the first intervening portion 50. In other words, the rear end of the roller support member 30 is indirectly supported by the support portion 54 via the second roller 62. The second roller 62 can swing up and down integrally with the second main body portion 61. That is, the second roller 62 is displaceable at least in the vertical direction.

[0050] (Operation of the tilting mechanism and the position of the contact rollers) Next, the operation of the tilting mechanism 40 and the change in the posture of the contact roller 25 due to the operation of the tilting mechanism 40 will be explained with reference to Figures 5(a) to 6(c). Figures 5(a) to 5(c) are explanatory diagrams showing the operation of the tilting mechanism 40. Figures 6(a) to 6(c) are explanatory diagrams showing the change in the posture of the contact roller 25.

[0051] First, an overview of the operation of the tilting mechanism 40 will be described. The control unit 26 mentioned above controls the electro-pneumatic regulator 47, supplying compressed air at a predetermined pressure to the working chamber 44 of the air cylinder 41. The compressed air extends the piston rod 45, pressing the first roller 53 of the first intervening part 50 upward. The first intervening part 50 is pressed upward via the first roller 53. When the first intervening part 50 is pressed upward, the second roller 62 of the second intervening part 60, which is in contact with the support surface 57, is also pressed upward. If the upward force pressing the second roller 62 is balanced by the downward force due to the weight of the contact roller 25, etc., the positions of the first intervening part 50 and the second intervening part 60 are determined, and the positions of the roller support member 30 and the contact roller 25 are determined. On the other hand, if the upward force pressing the second roller 62 exceeds the downward force, the first intervening portion 50 and the second intervening portion 60 will swing upward, and the connecting portion 64 of the second intervening portion 60 and the rear end of the roller support member 30 will be displaced upward (see Figures 5(a) to 5(c)). When the rear end of the roller support member 30 is displaced upward, the contact roller 25 will tilt, and its posture will change so that the rear end of the contact roller 25 is positioned upward and the front end is positioned relatively downward (see Figures 6(a) to 6(c)).

[0052] Next, the specific forces acting on the intervening mechanism 42 will be explained using Figure 5, focusing on the first intervening part 50. The first intervening part 50 is subjected to an upward force moment from the air cylinder 41 and a downward force moment from the weight of the contact roller 25, with the first fulcrum shaft 51 as the fulcrum. When these two force moments are balanced, the first intervening part 50 remains stationary, and when the upward force moment is greater than the downward force moment, the first intervening part 50 swings upward. In other words, the first intervening part 50 moves using the principle of a lever, with the first fulcrum shaft 51 as the fulcrum, the point of contact with the upper end surface 46 of the first roller 53 as the point of effort, and the point of contact 58 on the support surface 57 as the point of application.

[0053] Figure 5(a) shows the state of the tilting mechanism 40 before the thread Y begins to be wound onto the bobbin B. In this state, the moment of force attempting to move the first intervening part 50 upward and the moment of force attempting to move the first intervening part downward are balanced, so that the second main body 61 of the second intervening part 60 is kept in a nearly horizontal position. Also, the amount of upward displacement of the rear end of the roller support member 30 at this time (hereinafter also simply referred to as the amount of displacement of the roller support member 30) is zero. The moments of these two forces will be explained in detail below.

[0054] First, let's explain the upward force moment. As described above, the piston rod 45 presses the first roller 53 upward. As shown in Figure 5(a), the thrust F1a of the air cylinder 41 acts on the first roller 53, causing an upward force moment to act on the first intervening part 50 with the first pivot shaft 51 as the pivot point. If the horizontal distance (i.e., the distance at the point of force application) between the point on the first roller 53 that is in contact with the upper end surface 46 of the piston rod 45 and the first pivot shaft 51 is L1a, then the magnitude of the above force moment is F1a × L1a.

[0055] Next, the downward force moment will be explained. A downward force acts on the second intervening part 60 due to the weight of the contact roller 25, etc. As a result, a downward force F2a acts on the contact point 58a of the support surface 57 via the second roller 62. As a result, the magnitude of the force moment that tries to move the first intervening part 50 downward is F2a × L2a, where L2a is the horizontal distance between the contact point 58 and the first support axis 51, as will be described later.

[0056] The details of the downward force moment will be explained using Figure 7. Of the force F2a, the component of the force that rotates the first intervening part 50 is the component perpendicular to the line segment connecting the first pivot axis 51 and the contact point 58a, i.e., force F2aa. The direction of force F2aa is inclined by an angle θ with respect to the direction of force F2a (vertical direction). Furthermore, if the length of the line segment connecting the first pivot axis 51 and the contact point 58a is L, then the magnitude of the force moment that tries to move the first intervening part 50 downward is F2aa × L, i.e., F2a × cosθ × L. On the other hand, the line segment connecting the first pivot axis 51 and the contact point 58a is inclined with respect to the horizontal by the same angle θ as above. Therefore, the magnitude of the distance L2a mentioned above is L2a = L × cosθ. In other words, the magnitude of the force moment is F2a × cosθ × L = F2a × L2a. This distance L2a is the distance at the point of application.

[0057] In Figure 5(a), the magnitudes of the moments of the two forces described 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 by the air cylinder 41, and at the same time, the magnitude of the downward load acting on the air cylinder 41. Since L1a > L2a, the thrust F1a of the air cylinder 41 is small compared to the downward force F2a.

[0058] Since the magnitudes of the moments of the two forces described above are balanced, the positions of the first intervening part 50 and the second intervening part 60 are fixed, and the second main body 61 of the second intervening part 60 is kept in a substantially horizontal position. As a result, the contact roller 25 is also kept in a substantially horizontal position (see Figure 6(a)).

[0059] Next, we will describe the displacement of the roller support member 30 while multiple threads Y are being wound onto multiple bobbins B. Figure 5(b) shows the state of the tilting mechanism 40 when the displacement of the roller support member 30 is exactly halfway between zero and the maximum displacement.

[0060] When the thrust of the air cylinder 41 becomes greater than F1a (see Figure 5(a)), the first intervening part 50 swings upward around the first pivot shaft 51. At this time, as the inclination of the first intervening part 50 with respect to the horizontal increases, the horizontal distance L1b between the first roller 53 and the first pivot shaft 51 becomes smaller than the distance L1a. The first roller 53 rotates in contact with the upper end surface 46 of the piston rod 45 and smoothly follows the fluctuation in the horizontal distance. In other words, the force application distance changes smoothly with the swing of the first intervening part 50. As shown in Figure 5(b), if the thrust of the air cylinder 41 is the thrust F1b and the force application distance is the distance L1b, the magnitude of the upward force moment is F1b × L1b. The distance L1b is smaller than the distance L1a (see Figure 5(a)).

[0061] As described above, the oscillation of the first intervening part 50 causes the support surface 57 to oscillate, and the second roller 62, which is in contact with the support surface 57, begins to be displaced upward with the second pivot axis 63 as its pivot point. Here, since the direction of oscillation of the second roller 62 and the direction of oscillation of the support surface 57 are different, when the support surface 57 oscillates, the second roller 62 moves relative to the support surface 57. As a result, the contact point 58b moves further away from the first pivot axis 51 than the contact point 58a in Figure 5(a) (i.e., the distance to the point of action becomes larger). Since the second roller 62 rotates in contact with the support surface 57, it smoothly follows the oscillation of the first intervening part 50.

[0062] As described above, the support surface 57 extends upward above the first pivot axis 51 as it moves further away from the first pivot axis 51 in the left-right direction. Therefore, when the first intervening part 50 is displaced upward and the contact point 58 moves further away from the first pivot axis 51, the second roller 62 is reliably displaced upward along the support surface 57. Also, the angle of inclination relative to the horizontal direction is larger at the part of the support surface 57 that is closer to the first pivot axis 51. Therefore, even when the distance to the point of application is relatively small, the large inclination of the curved surface results in a large amount of vertical displacement of the second roller 62 due to the displacement of the first intervening part 50. Note that when the distance to the point of application is relatively large, even if the angle of inclination of the support surface 57 is gentle, the second roller 62 is easily displaced vertically by the displacement of the first intervening part 50.

[0063] When the downward force acting on the contact point 58b is denoted as force F2b and the distance at the point of application is distance L2b, the magnitude of the moment of the downward force is F2b × L2b. In Figure 5(b), F1b × L1b = F2b × L2b, and the positions of the first intervening part 50 and the second intervening part 60 are fixed. 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 with respect to the horizontal direction (see Figure 6(b)). At this time, multiple threads Y are being wound onto multiple bobbins B, and the diameter of the multiple packages P is approximately half of the maximum diameter.

[0064] Here, even if the rear end portion of the roller support member 30 is displaced slightly upward from the state where the displacement amount of the roller support member 30 is zero (the state where the second main body portion 61 is substantially horizontal), the magnitude of the force F2b is almost the same as the magnitude of the force F2a (see FIG. 5(a)). On the other hand, the distance L2b (the distance of the point of action) is larger than the distance L2a (see FIG. 5(a)). Further, as described above, the distance L1b (the distance of the force point) is smaller than the distance L1a (see FIG. 5(a)). That is, when the displacement amount of the roller support member 30 is increased, the load acting on the air cylinder 41 increases due to the increase in the distance of the point of action and the decrease in the distance of the force point. That is, in order to further increase the displacement amount of the roller support member 30, a larger thrust of the air cylinder is required.

[0065] The above load increases as the displacement amount of the roller support member 30 increases. As shown in FIG. 5(c), in the state where the displacement amount of the roller support member 30 is maximized, the distance L1c, which is the distance of the force point, becomes even smaller (L1c < L1b < L1a), and the distance L2c, which is the distance of the point of action, becomes even larger (L2c > L2b > L2a). When the thrust of the air cylinder 41 at this time is the thrust F1c and the downward force acting on the contact portion 58c is the force F2c, the relationship 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 controller 25 is further inclined with respect to the horizontal direction (see FIG. 6(c)). Also, at this time, the plurality of packages P are in a fully wound state.

[0066] (Relationship between displacement amount and load) The relationship between the displacement amount of the roller support member 30 described above and the load acting on the air cylinder 41 will be described while referring to the graph of FIG. 8. Here, for simplicity, it is assumed that the contact pressure described above is "medium". The horizontal axis of the graph indicates the displacement amount of the roller support member 30. The vertical axis of the graph indicates 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.

[0067] When multiple threads Y are wound onto multiple bobbins B, the control unit 26 performs the following control to make the tilt of the contact roller 25 follow the change in the tilt of the bobbin holder 24 due to the expansion of the package P. Specifically, the control unit 26 controls the electro-pneumatic regulator 47 to gradually increase the pressure of the compressed air supplied to the air cylinder 41 over time. Information regarding the time change of the above pressure is stored in, for example, ROM. As the above pressure increases, the thrust of the air cylinder 41 gradually increases from F1a. Accordingly, as described above, the tilting mechanism 40 operates and the rear end of the roller support member 30 is gradually displaced upward.

[0068] For example, if the maximum displacement of the roller support member 30 is X, then when the roller support member 30 is displaced by half of that amount, i.e., X / 2, the magnitude of the load acting on the air cylinder 41 will be F1b as described above. Similarly, when the roller support member 30 is displaced by X, the magnitude of the load acting on the air cylinder 41 will be F1c as described above. In other words, the load on the air cylinder 41 due to the weight of the contact roller 25 is amplified by the intervening mechanism 42 as the amount of displacement increases. Therefore, the larger the amount of displacement, the greater the thrust of the air cylinder 41 required to further displace the roller support member 30. Furthermore, the relationship between the amount of displacement and the load can be made linear, for example, as shown in Figure 8, by adjusting the shape of the support surface 57 and the positional relationship between the first intervening part 50 and the second intervening part 60. However, it is not necessarily limited to this, and it is sufficient as long as the amount of displacement and the load correspond in a reliable one-to-one relationship.

[0069] Incidentally, it was found that the relationship between the thrust from the air cylinder 41 of the tilting mechanism 40 and the tilt angle of the contact roller 25 changes depending on the setting of the contact pressure (control of the electro-pneumatic regulator by the control unit 26) as described above. This will be explained in more detail with reference to Figure 8. Figure 8 shows the relationship between the amount of displacement and the load in each case of "small," "medium," and "large" contact pressure.

[0070] The roller support member 30 is supported by both sides in the front-rear direction by the air cylinder 35 and the intervening mechanism 42. When the contact pressure is "low," which is lower than "medium," the force with which the package P pushes the contact roller 25 upward is relatively small according to the law of action and reaction. Therefore, the force required for the intervening mechanism 42 to support the roller support member 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 member 30 vertically by X / 2 is a thrust F1L, which is greater than the thrust F1b required when the contact pressure is "medium." Also, when the contact pressure is "medium" and the air cylinder 41 outputs thrust F1b, the roller support member 30 is displaced vertically by X / 2. However, when the contact pressure is "low," the displacement of the roller support member 30 when thrust F1b is output is XL, which is less than X / 2. On the other hand, when the contact pressure is relatively high ("large"), the force with which the package P pushes the contact roller 25 upward is relatively large. Therefore, the force required for the intervening mechanism 42 to support the roller support member 30 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 vertically by X / 2 is a thrust F1H, which is smaller than the thrust F1b. Also, when the contact pressure is "large", the displacement of the roller support member 30 when the thrust F1b is output is XH, which is larger than X / 2. In this way, the relationship between the thrust from the air cylinder 41 and the displacement of the roller support member 30 (i.e., the relationship between the thrust and the inclination angle of the contact roller 25) changes. Therefore, it was found that even though the tilting mechanism 40 is provided, there is a risk that the contact pressure will vary among multiple packages P in the axial direction. To suppress variations in contact pressure among multiple packages P even when the setting of the contact pressure applied to multiple packages P is changed, the thread winding machine 4 is configured as follows.

[0071] (Further details on the thread winding machine) Further details of the thread winding machine 4 will be explained with reference to Figures 4 and 9. Figure 9 is a table showing the relationship between the weight of each package P and the target value of the displacement of the roller support member 30.

[0072] As shown in Figure 4, the thread winding machine 4 has a displacement sensor 66 (detection unit of the present invention). The displacement sensor 66 is a sensor for detecting the amount of displacement of the roller support member 30. Examples of types of displacement sensors 66 include known optical displacement sensors, linear proximity sensors, ultrasonic displacement sensors, etc. The displacement sensor 66 is located, for example, below the right end of the second main body 61. The displacement sensor 66 is attached, for example, to 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, for example. The displacement sensor 66 is electrically connected to the control unit 26. The displacement sensor 66 sends a detection signal regarding the amount of displacement of the right end of the second main body 61 to the control unit 26. The displacement sensor 66 may be attached to a location other than the right end of the second main body 61.

[0073] The control unit 26 stores in RAM a table (see Figure 9) that shows, for example, the relationship between the weight of the package P and the target value of the displacement of the roller support member 30. Here, the weight of the package P refers to the weight of one package P. Also, the weight of the package P refers to the weight excluding the weight of the bobbin (i.e., the weight of the yarn Y contained in the package P). More precisely, the displacement of the roller support member 30 is the displacement of the right end of the second main body 61. In the example shown in Figure 9, when the weight of the package P (hereinafter simply referred to as weight) is 0 kg, the target value of the displacement of the roller support member 30 (hereinafter simply referred to as displacement) is 0 mm. When the weight is W / 200 (unit is kg; the same applies hereinafter), the target value of the displacement is X / 50 (unit is mm; the same applies hereinafter). 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 package P and the target value of the displacement is determined independently of the set value of the contact pressure. The value of W, which represents the weight of package P, is for example 16 kg, and the value of X, which represents the target value of the displacement of the roller support member 30, is for example 8.0 mm, but is not limited to these values.

[0074] (Control of displacement) The control unit 26 controls the amount of displacement during the winding operation. The procedure for controlling the amount of displacement during the winding operation will be explained with reference to the flowchart in Figure 10. As an initial state, the state of the yarn winder 4 is assumed to be, for example, the state before winding of yarn Y onto each of the multiple bobbins B begins. The state before winding begins may be, for example, the state before multiple yarns are placed on the yarn winder 4 (not shown). Alternatively, the state before winding begins may be, for example, the state before the bobbin switching described above takes place (not shown).

[0075] First, the operator inputs a set value for the contact pressure applied to each package P by the contact roller 25 into the control unit 26 (step S101 shown in Figure 10). The operator may input the numerical value of the set value into the control unit 26, for example, via the input unit (not shown) described above. Alternatively, the operator may select a set value for the contact pressure from a predetermined selection. In 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 regulator 39 (see Figure 2) according to the set value of the contact pressure to control the pressure of the compressed air supplied to the air cylinder 35. In addition, in the winding operation, the control unit 26 controls the amount of displacement as follows.

[0076] Next, the control unit 26 controls each component of the yarn winding machine 4 as needed and starts winding the yarn Y onto multiple new bobbins B (winding operation) (step S102). During the winding operation, the control unit 26 calculates the weight of each package P being formed and detects the actual displacement as needed (step S103). More specifically regarding the calculation of the weight of each package P, the control unit 26 has, for example, pre-stored information on the amount of yarn Y discharged per unit time from the spinning machine 3. The control unit 26 also counts the elapsed time (winding time) from the start of the winding operation. The product of the discharge amount per unit time and the winding time is calculated as the current weight (hereinafter, current weight) of each package P (i.e., the weight of yarn Y wound onto each bobbin B). The actual displacement is detected as needed by the displacement sensor 66. The information on the actual displacement is information on the actual inclination angle of the contact roller 25, including the effect of contact pressure. The value of the actual displacement corresponds to the actual angle-related value of the present invention.

[0077] Next, the control unit 26 obtains a target value for the displacement (step S104). More specifically, the control unit 26 performs the following processing: The control unit 26 takes into account the relationship between the weight of package P included in the table above and the target value for the displacement, and calculates the target value for the displacement based on the current weight, for example, by known linear interpolation. Next, the control unit 26 calculates the change in the displacement based on the difference between the target value for the displacement and the actual displacement (step 105). Known control methods, such as PID control, may be used as the method for calculating the change in the displacement. However, it is not limited to this, and known on / off control may be used as a known control method, for example. Next, the control unit 26 calculates the change in the pressure of the compressed air supplied to the air cylinder 41 (see Figure 4) from the change in the displacement (step S106). Next, the control unit 26 calculates a target value from the current value and the change in the compressed air (step S107). Next, the control unit 26 controls the electro-pneumatic regulator 47 (see Figure 4) based on the target value of the compressed air pressure. This updates the compressed air pressure (step S108). After the above process, the control unit 26 determines whether the package P is fully wound, for example, based on the winding time (step S109). If the control unit 26 determines that the package P is not yet fully wound (step S109: No), it returns to step S103. If the control unit 26 determines that the package P is fully wound (step S109: Yes), it terminates the winding operation for the currently formed package P (step S110). In this way, the tilting mechanism 40 (see Figure 4) is controlled so that the tilt angle reaches the target value based on the information of the actual angle-related values. The target value is uniquely determined based on the target value of the displacement amount obtained according to the current weight.

[0078] As described above, the tilting mechanism 40 is controlled so that the tilt angle reaches a predetermined target value based on information regarding the actual angle-related value of the actual tilt angle of the contact roller 25. This prevents the tilt angle from deviating from the target value, regardless of the contact pressure setting. Therefore, even if the contact pressure setting applied to multiple packages P is changed, variations in contact pressure among the multiple packages P can be suppressed.

[0079] Furthermore, since the contact roller 25 generally extends horizontally, the vertical displacement of the second main body 61 is easily detected even if the change in the inclination angle of the contact roller 25 is small. For this reason, the displacement of the second main body 61 is effective as a physical quantity to be detected instead of the inclination angle. By detecting the displacement of the second main body 61 and controlling the tilting mechanism 40, the inclination angle of the contact roller 25 can be substantially controlled. Therefore, variations in contact pressure between multiple packages P can be effectively suppressed.

[0080] Furthermore, by applying the air cylinder 41 as the drive source for the tilting mechanism 40 and adjusting the output of the air cylinder 41 with the electro-pneumatic regulator 47, the structure of the thread winding machine 4 can be simplified. In addition, the output of the air cylinder can be reliably adjusted with a simple configuration.

[0081] Furthermore, by using an air cylinder 41, which is less expensive than a hydraulic cylinder (not shown), the increase in component costs for the thread winding machine 4 can be suppressed.

[0082] Furthermore, the second main body 61 of the tilting mechanism 40 is driven by the air cylinder 41 to raise and lower the rear end of the roller support member 30. This makes it possible to keep the change in the tilt angle with respect to the displacement of the roller support member 30 smaller compared to a configuration in which the inner portion of the roller support member 30 in the axial direction is raised and lowered. Therefore, fine adjustment of the tilt angle can be performed.

[0083] Furthermore, the tilting mechanism 40 has an intervening mechanism 42. This means that a greater force is required when increasing the displacement of the roller support member 30. Therefore, even when it is difficult to precisely adjust the thrust of the air cylinder 41, the displacement of the roller support member 30 can be controlled with high precision. Consequently, the tilt angle of the contact roller 25 can be controlled with high precision.

[0084] Furthermore, the roller support member 30 can be stably supported by both the second main body 61 and the air cylinder 35. Therefore, the contact pressure can be stably adjusted.

[0085] Next, modified examples of the above embodiments will be described. However, components having the same configuration as the above embodiments will be denoted by the same reference numerals and their descriptions will be omitted as appropriate.

[0086] (1) In the above embodiment, the yarn winding machine 4 has a displacement sensor 66, and the control unit 26 controls the amount of displacement. However, it is not limited to this. The following will be explained in detail with reference to Figures 11(a) to 12. Figure 11(a) is a table showing the relationship between the weight of each package P and the target value of the compressed air pressure in a modified example. Figure 11(b) is a table showing the relationship between the contact pressure and the adjustment amount of the compressed air pressure. Figure 12 is a flowchart showing the control of the compressed air pressure during yarn winding in a modified example. The control unit 26 stores in RAM, for example, a table (see Figure 11(a)) showing the relationship between the weight of each package P and the target value of the compressed air pressure supplied to the air cylinder 41 (hereinafter simply referred to as the compressed air pressure). In the example shown in Figure 11(a), when the weight of the package P (hereinafter simply referred to as weight) is 0 kg, the target value of the compressed air pressure is 2 A / 5 (unit is kPa; the same applies hereinafter). When the weight is W / 200 (unit: kg; same applies hereafter), the target pressure is 3A / 4. When the weight is 6W / 25, the target compressed air pressure is 4A / 5. When the weight is W, the target compressed air pressure is A. The value of W, which indicates the weight of package P, is for example 16 kg, and the value of A, which indicates the target pressure, is for example 465 kPa, but is not limited to these values. Furthermore, the control unit 26 stores a table in RAM that shows the relationship between the contact pressure setting value and the amount of adjustment for the compressed air pressure (see Figure 11(b)). In the example shown in Figure 11(b), when the contact pressure setting value is 2C / 3 (unit: N; same applies hereafter), that is, C / 3 lower than the standard, the amount of adjustment for the target compressed air pressure is +ΔA (unit: kPa; same applies hereafter). When the contact pressure setting value is C (equal to the standard value), the amount of adjustment for the target compressed air pressure is zero. When the set value of the contact pressure is 4C / 3 (a value C / 3 higher than the standard), the adjustment amount for the target value of the compressed air pressure is -ΔA. The value of C, which indicates the set value of the contact pressure, is for example 150N, and the value of ΔA, which indicates the adjustment amount for the target value of the compressed air pressure, is for example 30kPa, but is not limited to these values.

[0087] The control unit 26 controls the compressed air pressure during the winding operation, taking into account the set value of the contact pressure. The procedure for controlling the compressed air pressure during the winding operation will be explained with reference to the flowchart in Figure 12. Initially, the state of the yarn winder 4 is, for example, the state before winding the yarn Y onto each of the multiple bobbins B begins. First, the operator inputs the set value of the contact pressure to the control unit 26 (step S201 shown in Figure 12). In the winding operation executed after step S201, the control unit 26 controls the contact pressure based on the input set value. In addition, during the 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 calculates the weight of each package P being formed as needed (step S203). Next, the control unit 26 obtains the target value of the compressed air pressure (step S204). More specifically, the control unit 26 takes into account the relationship between the weight of package P and the target value of compressed air pressure, as shown in the table in Figure 11(a), and calculates the target value of compressed air pressure based on the current weight value, for example, by linear interpolation. This target value is a provisional target value before taking contact pressure into consideration. Next, the control unit 26 reads the table shown in Figure 11(b) and obtains information on the amount of adjustment for compressed air pressure according to the current set value of contact pressure (step S205). The information on the amount of adjustment for compressed air pressure corresponds to the force adjustment information of the present invention. The control unit 26 updates the target value of compressed air pressure by adding the adjustment amount to the provisional target value (step S206). Next, the control unit 26 controls the electro-pneumatic regulator 47 based on the updated target value and updates the compressed air pressure (step S207). After that, the control unit 26 determines whether or not package P is fully wound (step S208). If the control unit 26 determines that the package P is not yet fully wound (step S208: No), it returns to step S203. If the control unit 26 determines that the package P is fully wound (step S208: Yes), it terminates the winding operation for the currently formed package P (step S209).As described above, the contact roller 25 can be fitted with an appropriate force (the second force of the present invention) corresponding to the weight of multiple packages P, based on force control information corresponding to the set value of the contact pressure. This allows the tilt angle to be adjusted appropriately. Therefore, similar to the above embodiment, even if the setting of the contact pressure applied to multiple packages P is changed, it is possible to suppress variations in contact pressure among the multiple packages P.

[0088] (2) In the embodiments described above, the pressure of the compressed air supplied to the air cylinder 41 was adjusted by the electro-pneumatic regulator 47. However, the invention is not limited to this. The pressure of the compressed air may be adjusted by, for example, an electrically operated valve (not shown). The valve may be configured to allow continuous or discontinuous adjustment of its opening. In this case, the valve corresponds to the pressure adjustment unit of the present invention.

[0089] (3) In the embodiments described above, the tilting mechanism 40 (angle adjustment section) has an air cylinder 41. However, it is not limited to this. Instead of the air cylinder 41, for example, a hydraulic cylinder (not shown) may be provided. In this case, the hydraulic cylinder corresponds to the fluid pressure cylinder of the present invention.

[0090] (4) In the embodiments described above, the angle adjustment section has a fluid pressure cylinder. However, it is not limited to this. The angle adjustment section does not have to have a fluid pressure cylinder. Instead of a fluid pressure cylinder, a magnetic cylinder that changes the thrust by an adjustable magnetic force may be provided. Alternatively, instead of a fluid pressure cylinder, a rack and pinion mechanism (not shown) may be provided.

[0091] (5) In the embodiments described above, the intervening mechanism 42 has a first intervening part 50 and a second intervening part 60. However, it is not limited to this. Instead of the intervening mechanism 42, for example, an air cylinder 41 may be configured to directly raise and lower the right end of the second main body 61. In this case, it is preferable that, for example, a tension coil spring (not shown) is intervened between the frame 28 and the second main body 61. This means that the greater the displacement of the right end of the second main body 61 relative to its initial vertical position, the greater the force required to further increase the displacement. In this case, the tension coil spring corresponds to the intervening mechanism of the present invention. The intervening mechanism is not required to be provided.

[0092] (6) In the embodiments described above, the tilting mechanism 40 is positioned at the rear end of the frame 28 and the air cylinder 35 applies force to the front end of the roller support member 30. However, this is not the only configuration. The tilting mechanism 40 may be positioned at the front end of the frame 28 and the air cylinder 35 may be positioned to apply force to the rear end of the roller support member 30. Alternatively, the tilting mechanism 40 may be positioned in the middle of the frame 28 in the front-rear direction, provided that the tilting angle of the roller support member 30 can be changed. Furthermore, the air cylinder 35 may be provided in the middle of the roller support member 30 in the front-rear direction, provided that the contact pressure can be changed. [Explanation of Symbols]

[0093] 4. Thread winding machine 20 machines 24 Bobbin Holder 25 Contact rollers 26 Control Unit 30 Roller support member 35. Air cylinder (contact pressure changing section) 40. Tilting mechanism (angle change section) 41. Air cylinder (fluid pressure cylinder) 42 Intervention mechanism (lifting part) 47 Electro-pneumatic regulator (pressure regulating unit) 61. Second main body (movable part) 66 Displacement Sensor B Bobbin P Package Y thread

Claims

1. The aircraft base and A bobbin holder is cantilevered to the machine base and holds multiple bobbins in a predetermined axial direction having a horizontal component, A contact roller that extends at least in the axial direction and applies contact pressure to a plurality of packages formed by winding a plurality of threads onto a plurality of bobbins, By applying a first force to the contact roller whose magnitude can be changed at least in the vertical direction, a contact pressure changing unit is provided that can change the contact pressure, An angle-changing unit is provided that can change the inclination angle of the contact roller with respect to the horizontal direction by applying a second force, separate from the first force, whose magnitude can be changed at least in the vertical direction, to the contact roller. A detection unit that detects information on the actual angle-related value concerning the actual tilt angle of the contact roller, It comprises a control unit and, The control unit, A yarn winding machine characterized by controlling the angle changing unit so that the actual angle-related value is set to a target value determined according to the weight of the yarn wound onto each of the plurality of bobbins and independently of the contact pressure setting value.

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

3. The aircraft base and A bobbin holder is cantilevered to the machine base and holds multiple bobbins in a predetermined axial direction having a horizontal component, A contact roller that extends at least in the axial direction and applies contact pressure to a plurality of packages formed by winding a plurality of threads onto a plurality of bobbins, By applying a first force to the contact roller whose magnitude can be changed at least in the vertical direction, a contact pressure changing unit is provided that can change the contact pressure, An angle-changing unit is provided that can change the inclination angle of the contact roller with respect to the horizontal direction by applying a second force, separate from the first force, whose magnitude can be changed at least in the vertical direction, to the contact roller. It comprises a control unit and, The control unit, A thread winding machine characterized by controlling the angle changing section using force adjustment information relating to the second force adjustment amount corresponding to the set value of the contact pressure.

4. The angle changing section is, A fluid pressure cylinder as a drive source for applying the second force to the contact roller, The thread winding machine according to any one of claims 1 to 3, further comprising a pressure adjustment unit configured to adjust the pressure of the fluid supplied to the fluid pressure cylinder.

5. The yarn winding machine according to claim 4, characterized in that the fluid pressure cylinder is an air cylinder.

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

7. The angle changing section is, A roller support member that rotatably supports the aforementioned contact roller, The thread winding machine according to any one of 4 to 6, characterized in that it has a lifting mechanism driven by the fluid pressure cylinder for raising and lowering one end of the roller support member in the axial direction.

8. The aforementioned lifting mechanism is The thread winding machine according to claim 7, characterized in that it has an intervening mechanism disposed between the fluid pressure cylinder and the roller support member in the transmission direction in which the force of the fluid pressure cylinder is transmitted, and configured such that the greater the displacement of one end of the roller support member in the axial direction relative to its initial vertical position, 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 section is configured to apply the first force to the contact roller by applying force to the other end of the roller support member in the axial direction.

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