JP2006298547A - Rotary equipment and belt driving device using the same, and flexible member winding device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent meandering and bias running of a long-size flexible member such as a belt and a tape 3. <P>SOLUTION: A roller body 5 to be wound with the tape 3 and run the tape is rotatably supported by a shaft member 7, and they are arranged on the inner peripheral side of an annular holding member 8 so as to be extended in the diameter direction, and both ends of the shaft member 7 are held by the holding member 8. The holding member 8 is turnably installed on a support plate member 10 through a bearing 9, and the rotary center shaft (pivotal shaft) C2 of the bearing 9 is tilted at the predetermined angle α forward in the rotating direction of the roller body 5 against a direction of an axial load L in a view along the rotary center shaft C1 of the roller body 5. In a view along the rotary center shaft C1, the bearing 9 is positioned to include a cross point of the rotary center shaft C1 and the pivotal shaft C2. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a rotating device such as a pulley or a roller, and also relates to a belt driving device using the rotating device or a winding device such as a thread or a tape.

  In general, in a belt transmission device using a flat belt, the belt may meander while the vehicle travels, or may travel slightly toward the one side of the pulley. This is because the flat belt is more sensitive to changes in equipment components than other belts, such as deviation from the normal position of the pulley shaft, pulley shaft deflection due to changes in shaft load, and pulley swing. . When such meandering / offset running occurs, the flat belt comes into contact with the flange of the flat pulley, causing fluffing of the side surface of the flat belt and fraying of the core.

  In order to solve this problem, it is known to attach a crown to the outer peripheral surface of the flat pulley (form a medium-high curved surface). There is also a proposal that the crown on the outer peripheral surface of the pulley is formed in a spherical shape centered on the rotation center of the pulley (see Patent Document 1). This is because when there is a tension difference between the left and right sides of the flat belt and the pulley shaft is tilted, and the flat belt is offset on the pulley, a rotational moment acts on the pulley due to the tension of the flat belt. By utilizing this, the inclination of the pulley shaft and the deviation of the flat belt are eliminated.

  Moreover, what formed many groove | channels in the outer peripheral surface of the flat pulley at intervals in the circumferential direction is known (refer patent document 2). In other words, the groove extends symmetrically from the center of the width of the pulley so as to form a “<” shape on both sides, and a frictional force that moves the flat belt to the center between the flat belt and the pulley. By generating the belt, meandering or deviation of the belt is prevented.

Furthermore, it is also known that guide pulleys are arranged on both sides of the flat belt to restrict the travel position of the flat belt (see Patent Document 3).
Japanese Utility Model Publication No.59-45351 JP-A-6-307521 Japanese Utility Model Publication No. 63-6520

  However, when the crown is formed on the pulley, if the radius of curvature of the crown is reduced with an emphasis on the running stability of the flat belt (preventing meandering and shifting), the stress concentrates in the center of the belt width, and the belt width The whole cannot be used effectively for transmission, leading to early fatigue of the core and a reduction in transmission capability.

  In addition, when the pulley crown is formed in a spherical shape with the rotation center of the pulley as the center, even if the effect of preventing the belt from shifting is enhanced, the problem is that stress is concentrated at the center of the belt width by the pulley crown. Still remains.

  If the flat pulley is grooved as described above, the manufacturing cost of the flat pulley increases, and it is difficult to reliably prevent meandering and shifting of the flat belt only by the groove processing.

  Furthermore, when a guide pulley or the like is arranged on both sides of the flat belt to restrict its running position, both sides of the flat belt always come into contact with such restriction members. Line fraying is likely to occur. Therefore, it is necessary to specially process the flat belt for preventing them, which is disadvantageous in reducing the production cost of the flat belt.

  For these reasons, flat belt transmissions are not fully utilized despite the fact that they have less loss due to belt bending and very high transmission efficiency compared to other belts such as V-belts. It is. This can be said for all belt drive devices using flat belts, including not only belt transmission devices but also belt conveyance devices.

  In response to such a problem, the inventors of the present application make use of the fact that the position of the axial load applied to the shaft of the roller is shifted by the tension of the belt when the flat belt is displaced. Developed a roller body that is inclined with respect to the belt so as to be inclined with respect to the load, thereby returning the belt offset (hereinafter also referred to as a centering roller). (For example, Japanese Patent Application No. 2004-119122).

  The aligning roller according to the prior application can automatically adjust the running position of the belt as described above. For example, as shown in FIG. 10, the roller a is a roller body c around which the belt b is wound. (Rotary body), a shaft member d inserted into the roller body c and rotatably supported by a bearing or the like, and the shaft member d is viewed along the rotation center axis C1 of the roller body c, and an axial load is seen. A support mechanism e that swingably supports a pivot C2 tilted by a predetermined angle to the front side in the rotation direction of the roller body c with respect to the direction L.

  When the position of the axial load L shifts in the width direction on the roller body c as the belt b is shifted, the rotational load around the pivot C2 acts on the roller body c and the shaft member d due to the axial load L. Rotating displacement (oscillating) and tilting so that the height of the shaft load L is high, and the belt b is in an oblique contact with the belt b. It gives the power to return.

  However, in the roller a according to the above-mentioned prior application, both ends of the shaft member d are held by the U-shaped arm f as a support mechanism e that supports the shaft member d so as to be swingable around the pivot C2, and the arms The shaft of f is supported on the base by a bearing g (sliding portion), and the bearing g is separated from the shaft member d in the direction of the pivot C2 as shown in the figure, so that the bearing g is squeezed. Moment force acts on this, and resistance due to sliding friction increases.

  In particular, in the case of a belt conveying device or a belt feeding device having a relatively low load, since the belt tension is small, the axial load is naturally reduced, and if the frictional resistance of the sliding portion is large as described above, the pulley In some cases, the rotational displacement (swing) of a rotating body such as a roller or a roller may be delayed or may not rotate smoothly, so that the deviation of the belt cannot be returned.

  Further, when the aligning roller according to the previous application is not limited to a belt conveying device or a transmission device, for example, when applied to a winding device that winds a fiber product such as a thread or string, or a tape on a reel, normally, Since the tension of the thread or tape is considerably smaller than that of the belt, it is unavoidable that the above-mentioned problems occur in this case.

  Accordingly, an object of the present invention is to provide a rotating device (pulley, roller, etc.) that travels by winding a long flexible member including a belt, a thread, a tape and the like, as in the prior application. When the rotating body is swung by the axial load, thereby returning the offset of the flexible member, the rotating body is smoothly rotated and displaced (swung) without delay even when the axial load is small, It is to make it possible to return the offset of the flexible member more reliably.

  In order to achieve the above object, according to the present invention, in the support mechanism of the shaft member, the sliding portion between the member on the shaft member side and the member that supports the rotation around the pivot shaft is provided with the direction of the pivot shaft. As much as possible, it is as close as possible to the point of application of the axial load to suppress the generation of moment force that twists the sliding part.

Specifically, the invention of claim 1 includes a cylindrical rotating body on which a flexible member is wound, a shaft member inserted into the rotating body and rotatably supporting the shaft, and the shaft member. A rotation mechanism comprising: a support mechanism that swingably supports a pivot that is tilted at a predetermined angle to the front of the rotation direction of the rotating body with respect to the axial load direction when viewed along the rotation center axis of the rotating body; Equipment,
The support mechanism has a sliding portion in which the supported member on the shaft member side and the supporting member supporting the shaft member slide around the pivot, and the sliding portion is the rotation center of the rotating body. It is arranged so as to overlap with the shaft member as viewed along the axis.

  The basic operation of the rotating device is the same as that of the roller according to the prior application. That is, for example, when a flexible member such as a belt is wound around a rotating body such as a roller main body and travels along with the rotation, the traveling position of the flexible member is shifted and the axial load is When the shaft member deviates from the position in the direction of the rotation center axis of the rotating body and acts on the shaft member, the axial load acts on the shaft member around the pivot axis due to the axial load. Rotating displacement (swing).

  The rotating body thus rotated and displaced is such that the side on which the flexible member is displaced moves in the direction of the axial load, that is, if the level in the direction of the axial load is high, the side on which the flexible member has been displaced is low, Inclined so that the opposite side is higher. That is, since the outer peripheral surface of the rotating body is inclined in the same manner as a crown in a conventional pulley, a return force in a direction opposite to the above-described offset direction acts on the flexible member. .

  Further, the pivot that becomes the center of the rotational displacement as described above is tilted forward in the rotational direction of the rotating body with respect to the axial load direction (that is, the tilt angle is more than 0 degree and less than 90 degrees). Therefore, the rotational displacement of the rotating body includes not only the component in the axial load direction but also the front-rear direction perpendicular to the axial load direction (the direction in which the flexible member is in contact with the rotating body). Ingredients will be included. For this reason, the rotating body not only inclines in the direction of the axial load as described above, but also the side where the flexible member is offset moves to the front side in the traveling direction, and is oblique to the flexible member. As a result, the flexible member is also given a force in a direction to return the offset.

  In other words, when the axial load deviates from the position of the pivot due to the deviation of the flexible member during travel, the rotating body is rotationally displaced around the pivot due to the rotational moment generated thereby, and increases or decreases in the direction of the axial load. It is inclined so as to be attached, and the flexible member is obliquely crossed. Then, both the return force due to the inclination and the return force due to the oblique state act on the flexible member, and the traveling position is returned.

  Here, as described above, the fact that the pivot is tilted with respect to the direction of the axial load when viewed along the central axis of the rotating body means that the axial load acts obliquely with respect to the pivot. In the support mechanism for pivotally supporting the shaft member around the pivot shaft, a moment force is applied to the sliding portion between the supported member on the shaft member side and the member supporting the shaft member so as to squeeze it by the axial load. There is a possibility of acting, and there is a concern about an increase in sliding frictional resistance.

  However, in the above configuration, the supported member and the sliding portion of the support member in the support mechanism are overlapped with the shaft member when viewed along the rotation center axis of the rotating body, that is, the action of the axial load. Since it is positioned in the vicinity of the point, even if an axial load acts obliquely with respect to the pivot as described above, the twisting moment acting on the sliding portion due to this axial load becomes very small.

  Therefore, the sliding frictional resistance between the supported member and the supporting member is reduced, and even when the axial load is small, the rotation delay of the rotating body can be reduced and smoothly displaced. Thereby, it is possible to return the traveling position of the flexible member by applying a returning force while the deviation is small, and it is possible to quickly eliminate the meandering and deviation movement. In this case, it is particularly preferable that the sliding portion is arranged so as to include an intersection of the rotation center axis and the pivot axis when viewed along the rotation center axis of the rotating body. Invention).

  Further, as a more specific configuration of the rotating device, it is preferable that both ends of the shaft member are held by the supported member outside the both ends in the rotation center axis direction of the rotating body. (Invention of claim 3) By holding both end portions of the shaft member in this way, it is possible to reduce the deflection of the shaft member as compared to holding one end portion in a cantilever state, and the positioning accuracy of the rotating body is improved. improves. Therefore, it is advantageous in accurately adjusting the traveling position of the flexible member on the rotating body.

  In this case, it is more preferable that the supported member and the supporting member are respectively annular, and the shaft member is disposed so as to extend in the diametrical direction on the inner peripheral side, and the rolling member is rolled between the supported member and the supporting member. A bearing is provided to constitute a sliding portion (invention of claim 4). If it carries out like this, a sliding part can be easily comprised with a general annular rolling bearing, and the sliding friction can be reduced reliably.

  According to another aspect, the present invention is a belt drive device in which a pulley, which is a rotating device having the above-described configuration, is provided so as to run around a belt that is a flexible member. In this belt drive device, as described above, the meandering and the offset travel of the belt can be quickly eliminated by swinging the main body (rotating body) of the pulley, and the belt transmission device can sufficiently exhibit the belt transmission capability. Will be advantageous.

  The belt may be of any type, such as a flat belt or a toothed belt (timing belt). In the case of a flat belt, either the inner peripheral surface or the outer peripheral surface may be brought into contact with the pulley body. In the case of a toothed belt, the rear surface of the transmission surface is brought into contact with the pulley body.

  According to another aspect, the present invention provides a pulley, a roller, a reel, etc., which are rotating devices as described above, wound around any one of a flexible member, such as a thread, a string, a rope, and a tape. It is the winding device provided so that it may run. In this winding device, similar to the belt driving device, meandering and offset running of yarns and tapes can be quickly eliminated by swinging the rotating body, and their running positions can be stabilized.

  As described above, according to the rotating device of the present invention, the rotating body around which the flexible member such as the belt is wound is rotatably supported by the shaft member, and the shaft member is supported with respect to the direction of the axial load. Since it is supported so as to be swingable around a pivot axis tilted in a predetermined direction, the rotating body is tilted so as to produce a height difference in the direction of the axial load when the travel position of the flexible member is offset, and is flexible. It is possible to apply a force to return the offset of the sex member in an oblique state. In this way, it is possible to prevent the flexible member from meandering and shifting by a simple structure.

  Moreover, in the shaft member support mechanism, the sliding portion between the supported member on the shaft member side and the support member that supports the shaft member is viewed along the rotation center axis of the rotating body, and the action of the shaft load is applied. Since it is arranged so as to be located in the vicinity of the point, the sliding moment resistance of the sliding portion generated by this axial load can be made extremely small, and the sliding frictional resistance can be reduced. Therefore, even when the axial load is small, the rotating body can be smoothly rotated and displaced relative to the side of the flexible member, and a return force can be applied while the side is small. The meandering and the offset running of the flexible member can be quickly eliminated.

  Therefore, in the belt transmission device and the belt conveyance device using the above rotating device, the belt meandering and the offset running can be quickly eliminated as described above, and the belt transmission capability and the conveyance capability can be sufficiently exhibited. .

In addition, if the rotating device is used in a winding device for yarn or tape, the traveling position of the yarn or tape can be stabilized as described above, so that the winding can be performed more reliably. Will be advantageous.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. It should be noted that the following description of the preferred embodiment is merely illustrative in nature, and is not intended to limit the present invention, its application, or its use.

  1 and 2 show a case where the present invention is applied to, for example, a tape winding device. In both figures, reference numeral 1 is a aligning roller as a rotating device according to the present invention, and reference numerals 2 and 2 are guide rollers for adjusting the winding angle of the tape 3 around the aligning roller 1. In this example, the tape 3 is wound around a winding roller or the like (not shown) and travels from the left side to the right side as a whole (see, for example, FIG. 8). As shown in a cross section in FIG. 2, the guide roller 2 is freely rotatable by a shaft member 22 attached to a base member 21 fixed to the vertical wall portion 4 of the winding device and bearings 23, 23 on the shaft member 22. The roller member 24 is supported by the roller 3 and is rotated counterclockwise as the tape 3 travels.

  On the other hand, the tape 3 is wound around the aligning roller 1 at a contact angle of about 180 °, and the aligning roller 1 rotates clockwise as the tape 3 travels. Yes. When the running position of the tape 3 is shifted in the width direction of the alignment roller 3 (the direction of the rotation center axis C1), the roller body 5 is inclined due to the axial load that is shifted from the center in the width direction. As a result, the offset of the tape 3 is returned.

  Specifically, as shown in FIG. 3, the aligning roller 1 is inserted into the roller main body 5 (rotary body) around which the tape 3 is wound, and is positioned coaxially. A shaft member 7 that rotatably supports both ends of the roller body 5 around the rotation center axis C1 by bearings 6 and 6, respectively, and surrounds the roller body 5 and the shaft member 7 so as to surround the shaft member. 7, and an annular holding member 8 that holds both ends of the holding member 7, and a support plate member 10 that rotatably supports the outer peripheral flange portion 8 b of the holding member 8 by a bearing 9. The portion is attached to the same vertical wall portion 4 as the guide roller 2.

  The holding member 8 has a shape in which a round hole 8a is opened in the entire bottom of the deep dish, and an outer peripheral flange portion 8b is formed so as to extend radially outward from the upper end of the peripheral wall portion, It has an annular shape as a whole. Openings 8c and 8c are formed in two portions of the peripheral wall portion that face each other in the diametrical direction, with the lower ends being arc-shaped and notched from the upper ends. The shaft members 7 are formed in the openings 8c and 8c, respectively. Both end portions of these are fitted and held from above.

  That is, the roller main body 5 and the shaft member 7 are arranged so as to extend in the diameter direction on the inner peripheral side of the annular holding member 8, and both end portions of the roller main body 5 in the width direction (direction of the rotation center axis C 1). Both end portions of the shaft member 7 extending further outward are held by the openings 8c and 8c of the holding member 8, respectively. By holding both end portions of the shaft member 7 in this way, the bending becomes smaller compared to holding only one end portion in a cantilevered state, so that the positioning accuracy of the roller body 5 can be improved, and consequently As will be described later, the positional accuracy when adjusting the running position of the tape 3 is also improved.

  Thus, the holding member 8 holding the roller body 5 and the shaft member 7 is assembled to the support plate member 10 from above. That is, the support plate member 10 has an irregular hexagonal shape in plan view and penetrates in the thickness direction so as to be larger in diameter than the peripheral wall portion of the holding member 8 and smaller in diameter than the outer peripheral flange portion 8b. Are formed in a circular shape as a whole. An inner peripheral flange portion 10b is formed so as to extend inwardly from the inner periphery of the lower end portion of the round hole 10a, and the diameter of the circle drawn by the inner peripheral end is substantially the same as the outer periphery of the bottom portion of the holding member 8.

  And the said holding member 8 is arrange | positioned substantially coaxially so that it may be accommodated in the round hole 10a of the said support plate member 10. FIG. At this time, the bottom portion of the holding member 8 is positioned at substantially the same height as the inner peripheral flange portion 10 b of the support plate member 10, and the outer peripheral flange portion 8 b of the holding member 8 is above the upper surface of the support plate member 10. Positioned somewhat apart. Thus, the bearing 9 is disposed between the outer peripheral flange portion 8b of the holding member 8 and the inner peripheral flange portion 10b of the support plate member 10 facing each other in the vertical direction.

  In this embodiment, the bearing 9 is a single-row ball bearing as an example, and a reference numeral is attached only to FIG. 4, but a plurality of balls arranged between the inner and outer rings 91 and 92 at a constant pitch in the circumferential direction. Are held by a retainer (not shown), and the balls 93, 93,... Roll in the circumferential direction in the respective groove portions of the inner and outer rings 91, 92. 92 is relatively rotated. The outer ring 92 of the bearing 9 is press-fitted into the inner periphery of the round hole 10a of the support plate member 10 and is integrally fitted to the rotation. On the inner periphery of the inner ring 91, the peripheral wall portion of the holding member 8 is provided. Thus, the holding member 8 is connected to the support plate member 10 so as to be rotatable around the central axis C <b> 2 of the bearing 9.

  Thus, in this embodiment, the axis C2 serving as the rotation center of the holding member 8 can be tilted within a predetermined angle range with reference to the vertical direction. That is, as described above, the end portion of the support plate member 10 that supports the holding member 8 is fixed so as to be substantially orthogonal to the base plate member 11 superimposed on the surface of the vertical wall portion 4 of the winding device. The base plate member 11 is rounded from the back so as to be coaxial with the axis of the shaft member 7 attached to the support plate member 10 via the holding member 8 as described above, that is, the rotation center axis C1 of the roller body 5. A hole 11 a is perforated, and the tip of the pin 41 embedded in the vertical wall portion 4 is fitted into the round hole 11 a from the inside, whereby the base plate member 11 and the support plate member 10 are fitted together. It can be rotated around the pin 41.

  The base plate member 11 is formed with arc-shaped elongated holes 11b and 11b at two locations on the circumference centered on the round hole 11a, and the two elongated holes 11b and 11b are respectively formed. Bolts 12 and 12 to be inserted are screwed into screw holes 4a and 4a formed in the vertical wall portion 4 on both the upper and lower sides of the pin 41, respectively. Therefore, if these bolts 12 and 12 are loosened and the base plate member 11 is rotated around the pin 41 together with the support plate member 10, the central axis C2 of the bearing 9 orthogonal to the support plate member 10, that is, The rotation center axis of the holding member 8 relative to the support plate member 10 can be tilted from the vertical direction to the left and right sides in FIG.

  In the use state of the aligning roller 1 shown in FIG. 1, as schematically shown in FIG. 4, the axial load L due to the tension of the tape 3 wound around the roller body 5 passes through the roller body 5. The shaft member 7 acts substantially downward in the vertical direction. With reference to the direction of the axial load L, the central axis C2 of the bearing 9 is the front side in the rotation direction of the roller body 5 (the clockwise side in the figure). In other words, the tape 3 is tilted forward by an angle α in the traveling direction of the tape 3 indicated by an arrow R in FIG.

  In other words, in this embodiment, as described above, the shaft member 7 is fixed to the roller body by the holding member 8 that holds both ends of the shaft member 7, the bearing 9, the support plate member 10, and the base plate member 11. 5 and a support mechanism that swingably supports a pivot C2 tilted by a predetermined angle α to the front side in the rotation direction when viewed along the rotation center axis C1 of the roller body 5.

  In this support mechanism, between the holding member 8 which is a supported member and the support plate member 10 which supports the support member 8, both the members 8 and 10 are slidable parts that slide around the pivot axis C <b> 2. , The bearing 9 is disposed, and when viewed along the rotation center axis C1 of the roller body 5 as shown in FIG. 4, the bearing 9 has a portion indicated by a virtual line in FIG. It arrange | positions so that the intersection with C2 may be included.

  As described above, the pivot C2 that is the center of oscillation of the shaft member 7 is tilted to the front side in the rotational direction of the roller body 5 with respect to the direction of the axial load L, and thus is wound around the roller body 5 and travels. When the position of the axial load L is shifted due to the offset of the tape 3 to be rotated, the roller body 5 is inclined in the direction of the axial load L due to the rotational moment generated thereby, and the tape 3 is inclined with respect to the tape 3. As a result, a force to return the offset of the belt is generated.

  More specifically, when the tape 3 is applied in the vicinity of the center of the width of the roller body 5 as indicated by a solid line in FIG. 5, the axial load vector L intersects the pivot C2, and the component L0 is along the pivot C2. The component force L1 acts at right angles to the pivot axis C2. At this time, the component force L1 does not generate a rotational moment around the pivot C2.

  On the other hand, as indicated by the phantom line in the figure, when the tape 3 is offset in the width direction of the roller body 5, the axial load L is applied to the offset side, so that the component force L1 of the axial load L is It acts around the pivot C2 to generate a rotational moment in the shaft member 7. That is, if the direction of the axial load L is parallel to the pivot C2, L = L0 and L1 = 0 at this time, and no rotational moment is generated around the pivot C2, but the axial load L is not increased as in this embodiment. If the pivot C2 is tilted, a rotational moment around the pivot C2 is generated by the component L1 of the axial load. Here, the angle α corresponds to the tilt angle of the pivot C2 with respect to the direction of the axial load L.

  In this embodiment, as shown in FIG. 4 and the like, the pivot C2 is tilted forward in the rotational direction of the roller body 5, so that the roller body 5 and the shaft member 7 rotate around the pivot C2 as described above. Then, as shown in FIG. 6 (viewed in the direction of the arrow VI in FIG. 4), the roller body 5 has a lower side on which the tape 3 is offset in the direction of the axial load L as seen in the direction orthogonal to the axial load L. As shown in FIG. 7 (indicated by arrow VII in FIG. 4) when viewed in the direction of the axial load L, the side on which the tape 3 is offset is the front side in the belt running direction. As shown, the tape 3 is obliquely crossed. 5-7, the state which the roller main body 5 rotationally displaced is shown with the virtual line (two-dot chain line).

  Due to the rotational displacement of the roller body 5, the tape 3 has a return force (force to return the offset) due to the inclination of the roller body 5 and a return force due to the roller body 5 being obliquely crossed. Thus, the running position of the tape 3 is corrected. That is, the offset force acting mainly on the characteristics of the winding device and the return force from the roller body 5 act on the tape 3, and the tape 3 travels at a position where both balance. Even if the tape 3 is largely displaced due to disturbance, the tape 3 is returned to a position where the return force and the offset force are balanced.

  Here, since the return force due to the skew has a higher effect of returning the position of the tape 3 than the return force due to the tilt, in order to effectively use the return force due to the skew, the tilt of the pivot C2 is inclined. The angle α is preferably set in the range of more than 0 degree and 45 degrees or less, and more preferably 30 degrees or less. In this embodiment, as shown in FIG. 4 as an example, the tilt angle α is set to about 10 to 20 °.

  However, if the tilt angle α of the pivot C2 is set to be small, the axial load L acts geometrically in the direction of the pivot C2, so that the axial load component L0 in the pivot C2 direction is increased. Since the axial load component L1 around the pivot C2 that generates a rotational moment in the roller body 5 and the shaft member 7 is small, particularly in the tape winding device having a relatively small tension as in this embodiment, the roller body 5 There is a possibility that the rotational displacement may be delayed or may not be smoothly rotated.

  In this regard, in this embodiment, the sliding portion between the holding member 8 (supported member) that holds the shaft member 7 and the like and the support plate member 10 that supports the shaft member 7 is configured by the ball bearing 9, The friction coefficient is reduced, and the bearing 9 is moved as close as possible to the point of application of the axial load L, so that the twisting moment acting on the bearing is suppressed.

  That is, as described above, when the pivot C2 is tilted with respect to the direction of the axial load L when viewed along the rotation center axis C1 of the roller body 5, the axial load L acts obliquely with respect to the pivot C2. Therefore, if the bearing 9 that pivotally supports the holding member 8 around the pivot C2 is away from the point of action of the axial load L in the direction of the pivot C2, the bearing 9 is driven by the axial load L. There is a possibility that a sliding moment acts and the sliding frictional resistance increases.

  However, in this embodiment, as described above, the bearing 9 includes the intersection of the rotation center axis C1 and the pivot axis C2 (= the point of action of the axial load L) when viewed along the rotation center axis C1 of the roller body 5. In other words, since it is arranged in the direction of the pivot C2 at substantially the same position as the point of action of the axial load L (see FIG. 4), the bearing 9 has little torsional moment due to the axial load L. There is no fear of increasing the dynamic frictional resistance.

  Therefore, according to the alignment roller 1 according to this embodiment, the tape 3 that runs while being wound around the roller body 5 is displaced in the width direction of the roller body 5 (direction of the rotation center axis C1) for some reason. When the axial load L acts to deviate from the position corresponding to the pivot C2, a rotational moment around the pivot C2 is generated by the axial load L, and the roller body 5 and the shaft member 7 are rotationally displaced. As a result, the running position of the tape 3 is returned toward the center.

  Moreover, in such a support mechanism that rotatably supports the roller body 5 and the shaft member 7 around the pivot C2, the ball bearing 9 is interposed between the holding member 8 on the supported side and the support plate member 10 on the support side. The sliding friction between the two is reduced, and the bearing 9 is further arranged so as to include the point of action of the axial load L on the inner peripheral side, so that almost no twisting moment acts on the bearing 9. Therefore, the sliding frictional resistance against the rotational displacement of the roller body 5 or the like can be made extremely small.

  Therefore, even when the tension is low like the winding of the tape 3 and the axial load L acting on the aligning roller 1 is small, the roller body 5 is not delayed with respect to the offset of the tape 3. A necessary and sufficient return force can be immediately applied by smoothly rotating (swinging). That is, since the running position of the tape 3 can be corrected by applying a return force while the deviation is small, the meandering and deviation running can be quickly eliminated.

  Thus, if the tape 3 does not meander or shift, the running position of the tape 3 on the roller body 5 can be accurately and stably controlled. 3 can be more reliably taken up. With respect to this point, as described above, it is also advantageous that both end portions of the shaft member 7 are held so that the bending thereof is reduced, thereby improving the positioning accuracy of the roller body 5.

-Example of tape processing device-
FIG. 8 shows a configuration example of a tape processing apparatus A including the above-described tape winding apparatus. The tape processing apparatus A unwinds an unprocessed tape 3 wound around a core material in a laminated state. It comprises a drawer A1 that is drawn out from the roll R1, a processing unit A2 that performs a predetermined process on the tape 3, and a winding unit A3 that winds up the tape 3 thus processed. This winding part A3 is the tape winding device described above.

  A guide roller R2, a centering roller R3, a guide roller R4, and a driving roller R5 are arranged in the drawing portion A1 in the order in which the tape 3 travels. The driving roller R5 is rotated counterclockwise in the figure by a prime mover (not shown). By rotating, the tape is pulled out from the unwinding roll R1. Further, the processing section A2 processes the tape 3 running around the tension roller R6 and the guide rollers R7, R8, R9 by the processing device S disposed between the guide rollers R7, R8. It is configured as follows.

  The tape 3 that has been subjected to the predetermined processing proceeds to the winding portion A3, and is wound around the winding roller R10 that is rotated clockwise in the drawing by a motor (not shown), so that the guide roller 2 and the aligning roller described above are aligned. The roller 1 and the guide roller 2 run in this order. At this time, the running position of the tape 3 is always corrected toward the center by the operation of the aligning roller 1, and the meandering and the offset running are prevented.

  In this example, in addition to the aligning pulley 1 that prevents the tape 3 from meandering and shifting in the winding portion A3 as described above, the tape 3 is prevented from meandering and shifting in the drawing portion A1. The aligning roller R3 is arranged as much as possible. The aligning roller R3 has a structure as shown in FIG. 9, for example. Like the aligning roller 1, the roller body 30 is supported by a shaft member 31 so as to be rotatable around its central axis. The shaft member 31 and the shaft member 31 are configured to swing around the pivot shaft.

  More specifically, as shown in the figure, the aligning roller R3 includes a cylindrical shaft member 31 that supports the roller body 30 by a bearing 32, a support rod 33 having a distal end side 33a inserted in the shaft member 31, and a pivot shaft. And a pin 34 constituting the. Although not shown, the other end 33b of the support rod 33 is attached to the vertical wall portion of the drawer portion A1, and the axial center of the pin 34 coincides with the axial load direction. Is arranged.

  That is, the aligning roller R3 does not oscillate by itself according to the positional deviation of the belt 3 unlike the aligning roller 1, and the rotational displacement of the roller body 5 of the aligning roller 1 ( The touch angle is mechanically fed back via, for example, a wire, a shaft, a gear or the like. In this way, by feeding back the touch angle from the aligning roller 1 and synchronously rotating the roller main body 30 of the aligning roller R3, the tape 3 can be prevented from meandering and offset running in the drawer A1. Can do.

(Other embodiments)
The configuration of the present invention is not limited to the above-described embodiment, and includes other various configurations. That is, in the above embodiment, the ball bearing 9 which is a sliding portion between the holding member 8 and the support plate member 10 is viewed along the rotation center axis C1 of the roller body 5 as shown in FIG. However, from the viewpoint of bringing the bearing 9 close to the point of action of the axial load L, it may be arranged so as to overlap the shaft member 7.

  In addition, the sliding portion may be constituted by other rolling bearings such as a roller bearing instead of the ball bearing 9, or a sliding material may be used. In that case, the sliding portion does not need to be an annular shape surrounding the roller body 5 and the shaft member 7. For example, arc-shaped convex portions formed at both ends of the shaft member 7 are respectively arranged around the pivot C 2. You may comprise by the circular-arc-shaped recessed part hold | maintained slidably so that it may rotate.

  Further, in the above embodiment, the base plate member 11 for attaching the support plate member 10 to the vertical wall portion 4 of the winding device is rotatable around the pin 41, and the roller body 5 and the shaft member 7 are swung. Although the angle of the pivot C2 that is the center of movement can be adjusted, the angle may be fixed to a preset value.

  Furthermore, in the above-described embodiment, the aligning roller 1 which is the rotating device of the present invention is applied to the winding device for the tape 3. However, the winding device is not limited to the tape 3, and other windings such as yarn, string, rope, etc. Needless to say, the rotating device of the present invention can be applied to, for example, a pulley, and can also be applied to a belt driving device for belt conveyance, belt transmission, and the like. If it is applied to a belt transmission device, it will be advantageous for fully exhibiting the transmission capability of the belt, and if it is applied to a conveyance device such as a belt conveyor, it will be advantageous for ensuring the conveyance capability of articles stably. .

  Furthermore, the use state of the aligning roller 1 shown in FIG. 1 and FIG. 8 is merely an example, and when applied to a winding device such as a thread or string as described above, or when applied to a belt driving device. Various layouts can be adopted as necessary. For example, as shown in FIG. 1, the wrapping angle (contact angle) of the tape 3 around the aligning roller 1 is preferably about 180 °, but is not limited thereto.

  As described above, when the rotating device according to the present invention is used, the meandering and the deviation of the belt and the tape are reliably prevented without causing a decrease in durability and transmission capability or an increase in manufacturing cost. be able to. As a result, transmission efficiency and conveyance efficiency can be increased in the belt driving device, and more reliable winding can be performed in a winding device such as a tape, so that the utility value is extremely high.

It is a schematic block diagram which shows the use condition in the tape winding apparatus of the aligning roller which concerns on this invention. It is the II-II sectional view taken on the line of FIG.1 (b) which shows the structure of the roller. It is a disassembled perspective view which shows the structure of the roller. It is explanatory drawing which shows a mode that an axial load acts seeing along the rotation center axis | shaft of the roller. It is explanatory drawing that a rotational moment generate | occur | produces in a shaft member by the axial load in the roller. FIG. 5 is an explanatory diagram schematically showing the rotational displacement of the roller body when the tape running position is offset in a direction perpendicular to the axial load L (in the direction of arrow VI in FIG. 4). FIG. 7 is a view corresponding to FIG. 6 viewed in the direction of the axial load L (the direction of the arrow VII in FIG. 4). It is a layout figure which shows the structural example of the tape processing apparatus containing the winding apparatus which concerns on this invention. It is a perspective view which shows the structure of another aligning roller arrange | positioned at a tape drawer part. FIG. 10 is a view corresponding to FIG.

Explanation of symbols

A Tape processing device A3 Winding unit (tape winding device)
1 Self-aligning roller (rotating equipment)
3 Tape (flexible member)
5 Roller body (rotating body)
7 Shaft member 8 Holding member (supported member)
9 Ball bearing (sliding part)
10 Support plate member (support member)
C1 Rotation center axis C2 Axis L Axis load

Claims (6)

A cylindrical rotating body around which the flexible member is wound;
A shaft member inserted into the rotating body and rotatably supporting the shaft member;
A support mechanism for supporting the shaft member in a swingable manner around a pivot shaft tilted by a predetermined angle to the front side in the rotational direction of the rotating body with respect to the axial load direction when viewed along the rotation center axis of the rotating body; With
The support mechanism includes a sliding portion in which the supported member on the shaft member side and the supporting member that supports the shaft slide relative to each other around the pivot shaft, and the sliding portion rotates the rotating body. A rotating device, wherein the rotating device is disposed so as to overlap the shaft member as viewed along a central axis.   The rotating member characterized in that the supported member and the sliding portion of the supporting member are arranged so as to include an intersection of the rotation center axis and the pivot axis when viewed along the rotation center axis of the rotating body. machine. In the rotating device according to claim 1 or 2,
A rotating device characterized in that both end portions of the shaft member are held by the supported member outside the both end portions in the rotation center axis direction of the rotating body. The rotating device according to claim 3,
The supported member and the supporting member are each annular, and a shaft member is disposed so as to extend in the diameter direction on the inner peripheral side thereof,
A rotating device, wherein a sliding part is constituted by a rolling bearing disposed between the supported member and the supporting member.   A belt drive device, wherein the rotating device according to any one of claims 1 to 4 is provided so as to run around a belt that is a flexible member.   The rotating device according to any one of claims 1 to 4, wherein the rotating device is provided so as to run around one of a thread, a string, a rope, and a tape that are flexible members. A flexible member winding device.

Images