Curved belt conveyor

Abstract

To conquer the performance-related problem that a curved belt does not have an orbit fixed without employing a belt holding mechanism for tensing the curved belt, nor a belt holding mechanism, such as a pinch roller and a tracking roller, for correcting the orbit of the curved belt.SOLUTION: A curved belt conveyor comprises a belt tension equalizing mechanism which equalizes tension, with which a curved belt 420 is loaded in a circumferential direction of a concentric circle having the center at a vertex 470 where generators of the curved belt 420 cross one another, over the entire region of the curved belt 420, and the belt tension equalizing mechanism controls a length movement of a center line of the curved belt 420 during rotation of the curved belt 420 within a predetermined range, so that the curved belt 420 rotates along a predetermined orbit.SELECTED DRAWING: Figure 5

Description

[Technical Field]

[0001] The present invention relates to a curved belt conveyor that is advantageous in terms of versatility, stability, safety, and quietness of conveyed objects compared to a curved roller conveyor in the case of curved conveyor transport of conveyed objects. In particular, the present invention relates to a curved belt conveyor in which a curved belt is wound around a curved roller conveyor that has a small number of parts and does not require a complex configuration. [Background technology]

[0002] The principles of heavy-duty transport technology using rollers and hemp canvas, which were invented in ancient civilizations to transport heavy objects, have been passed down to the present day, and remarkable improvements have been made to materials and mechanisms, evolving into devices that continuously transport goods, industrial materials, soil and sand, semi-finished products, food ingredients, etc., as defined by the Japanese Industrial Standards (JIS) as "machines for continuously transporting loads." In particular, they have contributed to the development of industry around the world as a fundamental technology for forming trunk lines for transporting goods common to all industries. Today, they are not limited to transporting goods, but also contribute to the transport of people and food, for example, in walking paths and conveyor belt sushi restaurants.

[0003] Even today, typical conveyors are broadly divided into roller conveyors, which use rollers as their base, and belt conveyors, which use hemp canvas as their base, based on the principles of ancient transport technology.However, since both conveyors have various advantages and disadvantages, they are used differently depending on the purpose of use in the industrial field.

[0004] For example, belt conveyors are widely used in the construction industry, which handles materials such as coal and gravel, and in the food and automotive industries, which handle raw materials and semi-finished products of various shapes and properties, due to their low cost and flexibility. Belt conveyors are well-suited to these industries because of their ability to transport a wide variety of materials, including bulk materials (e.g., bulk materials), regardless of weight, volume, or properties, without being consolidated into cardboard boxes or containers, thanks to their strong frictional force. In the logistics industry, belt conveyors are also used for bulk materials for similar reasons. Belt conveyors also have the advantage of low vibration and impact on the materials, making them popular for materials and processes that require stable and safe transport. Furthermore, because conveyors are used indoors, they are quieter and do not produce impact noise due to collisions with products, which is another major factor in their adoption.

[0005] On the other hand, roller conveyors are characterized by their low roller friction, making them suitable for transporting relatively heavy, large-volume items, such as bulk items, which are aggregated into units like cardboard boxes or containers. They are particularly popular in various processes in the logistics industry. This is due to the roller's low friction, which allows for an excellent accumulation function, allowing items to be temporarily stored on the roller conveyor, and the gap between the rollers, which allows various narrow conveyor technologies to be inserted into the gap, allowing the direction of transport of the items to be freely changed. Furthermore, by utilizing an inclination, they can be used as an energy-saving conveyor known as a gravity conveyor, which does not require power. In other words, in the logistics industry, where products must be delivered from producers to consumers and complex transport processes such as sorting and consolidation are required, roller conveyors are indispensable because they can freely control the direction of transport of items and also save energy.

[0006] However, roller conveyors are typically limited to transporting items that can be accommodated by four or more conveying rollers. This makes it difficult to accommodate lighter, thinner, and smaller cardboard boxes and containers, which contain goods, simplify packaging, and handle loose items. They also have difficulty transporting items containing liquids or precision instruments and parts, which require protection from impact damage. While the former is clearly infeasible because items fall through the gaps between the rollers, the latter is difficult to address because items are prone to slippage, resulting in unstable transport direction, resulting in items falling off the roller conveyor or colliding with guards, and damage from collisions with metal rollers. Furthermore, the impact noise generated by collisions between items and metal rollers is loud, creating noise reduction issues. In particular, improvements to working environments, including noise reduction, have recently become a pressing issue in logistics centers and other facilities. However, these drawbacks stem from the very source of the advantages of roller conveyors, which involve transport over gapped rollers and contact with hard metal rollers, resulting in low friction between the rollers. No solution has been found that reconciles these drawbacks.

[0007] Therefore, to improve the disadvantages of roller conveyors, it is easy to think of switching the conveying path from a roller conveyor to a belt conveyor, but this would mean sacrificing the advantages of roller conveyors that are required for logistics systems, such as the ability to easily add functions such as a conveying path length adjustment function, an accumulating function, and a conveying direction change function using the roller gap, and therefore it is not applicable to all conveying paths.

[0008] However, in a curved roller conveyor with an arc-shaped curve in the conveying path, not only when using straight rollers but also when using tapered rollers, the gap between the rollers is larger on the outer periphery of the curve than on the inner periphery of the curve, resulting in an uneven structure. In addition, due to the difference in diameter of the tapered rollers, a speed difference occurs between the outer and inner periphery, so that the conveyed object is likely to fall into the gap between the tapered rollers, and it is more likely to rotate or fall due to slippage of the conveyed object than in a straight roller conveyor. Also, for the same reason, the damage and noise caused by falling of the conveyed object and collision between the conveyed object and the metal rolls are severe in a curved roller conveyor. Therefore, in the case of a curved conveyor, switching from a roller conveyor to a belt conveyor is an unavoidable and inevitable trend.

[0009] For this reason, curved belt conveyors have been developed for a long time, and as a result, they have already been widely put into practical use (e.g., Patent Documents 1 to 17). Such curved belt conveyors are basically configured with two tapered rollers, which function as pulleys in a belt conveyor, arranged at the radius where the rollers intersect with both ends of the fan-shaped arc, and equipped with a drive mechanism to operate them. A curved belt shaped like the side of a truncated cone is placed over the two tapered rollers and wrapped around the outside of the two tapered rollers so as to bridge them and apply tension. Based on this configuration, curved belt conveyors have had problems such as the shifting of the curved belt shaped like the side of a truncated cone, with the central fan-shaped portion of the fan removed in a plan view projected onto a horizontal plane, to the inner periphery due to centripetal force, meandering due to the difference in peripheral speed between the inner and outer peripheries of the curved belt, and deformation and shortened lifespan of the curved belt due to the belt holding mechanism provided to prevent these problems. However, various countermeasures have been implemented to the basic configuration of the curved belt.

[0010] First, there is a method in which the curved belt is held and rotated in a state in which a plurality of protrusions arranged on the outer peripheral edge of the curved belt, i.e., on the base of the truncated cone-shaped curved belt, are sandwiched between rollers, ball bearings, etc., installed on the outer periphery of the curved belt conveyor (for example, Patent Documents 1 to 5). This method has been widely studied, and improvements have been made to absorb the load fluctuations applied in the radial direction of the curved belt, the ease of attaching and detaching the curved belt, and the sliding properties of the protrusions, which are believed to have reduced damage to the curved belt and achieved stable conveyance, and has been put to practical use.

[0011] In the second type, an endless belt is attached to a rotating body such as a plurality of rollers or ball bearings installed on the outer periphery of the curved belt conveyor, and the outer peripheral edge of the curved belt and the endless belt are bridged by a connecting member having spring elasticity, thereby holding and rotating the curved belt (for example, Patent Document 6). The connecting member has elasticity, and the endless belt to which it is hooked is severely damaged, so improvements have been made to the connecting part between the outer peripheral edge of the curved belt and the endless belt (for example, Patent Document 7). For the same purpose, improvements using a chain as the endless belt have also been proposed (for example, Patent Documents 8 and 9).

[0012] Thirdly, a mechanism that reverses the configuration of the belt holding mechanism has been proposed. This is a system in which rotating bodies such as rollers or ball bearings are provided on the outer periphery of the curved belt, and guide rails are provided on the outer periphery of the curved belt conveyor to allow these rotating bodies to run (for example, Patent Documents 10 and 11). Like the system using protrusions, this does not require springs, is thought to reduce damage to the curved belt, and achieves stable conveyance, and has already been put to practical use.

[0013] However, these curved belt conveyors require a belt holding mechanism, which results in a large number of parts and a complex mechanical configuration. In addition, the tension applied to the curved belt by the belt holding mechanism causes deformation of the curved belt and a shortened lifespan of the curved belt. Therefore, a curved belt conveyor has been proposed that prevents the curved belt from shifting or meandering without the need for a belt holding mechanism.

[0014] First, a drive roller for driving a curved belt is disposed between the outward and return surfaces of the outer peripheral edge of the curved belt so that the central axis of rotation of the drive roller coincides with a line connecting the center of the curved belt's arc and the center of the curved belt's outer periphery. A pinch roller is disposed above the drive roller, and the curved belt is sandwiched between the pinch roller and the drive roller (see, for example, Patent Document 12). This system, in which the pinch roller presses the curved belt against the drive roller from above the outward surface of the curved belt, prevents the curved belt from shifting or meandering. Since the curved belt holding mechanism does not impose a load on the curved belt, it also solves the problem of damage to the curved belt. Furthermore, proposals have been made to provide this mechanism for sandwiching the curved belt between the pinch roller and the drive roller on the return side, and even to provide multiple pinch rollers on both the outward and return sides (see, for example, Patent Documents 13 and 14). However, although such pinch rollers and drive rollers do not exert a load on the curved belt by pulling the curved belt, they are also included in the category of belt holding mechanisms.

[0015] Secondly, for the same purpose, a curved belt conveyor has been proposed in which the shapes of the tapered rollers and curved belt at both ends are optimized without adding any parts to the basic structure of the curved belt conveyor (for example, Patent Documents 15 and 16).

[0016] However, it is considered difficult to prevent the curved belt from shifting or meandering simply by optimizing the shape of the two tapered rollers at both ends of the curved belt conveyor and the shape of the curved belt. Therefore, a third type of curved belt conveyor has been proposed, in which a curved belt with a truncated cone side is placed over a curved roller conveyor in which multiple tapered rollers are arranged in a fan shape, and is wrapped around the outside of the two tapered rollers to bridge them and apply tension (for example, Patent Documents 17 and 18).

[0017] Even with this type of curved belt conveyor, the problems of curved belt deviation and meandering occur. To solve these problems, methods have been proposed for controlling the surface contact state between the curved belt and tapered rollers, such as installing tracking rollers to correct belt trajectory fluctuations (tracking defects) and attaching convex tracking members to tapered rollers (Patent Document 17). Other proposals include uneven tension control by increasing the elongation rate on the outer periphery of the curved belt, i.e., tension on the outer periphery of the curved belt, and modifying the design of the curved belt and attaching a sleeve to the outer periphery of the tapered roller (Patent Document 18). However, the present inventor has experimentally confirmed that these proposals are insufficient to solve the problems of curved belt deviation and meandering that occur in curved belt conveyors that have a curved belt wound around a curved roller conveyor. Furthermore, the installation of tracking rollers is a belt retention mechanism, which complicates the mechanical configuration, making it a solution that should be avoided.

[0018] However, curved belt conveyors that do not use a belt holding mechanism, especially the third type curved belt conveyor in which a curved belt is wound around a curved roller conveyor, have not yet overcome performance problems. However, because they have a small number of parts and a simple mechanical configuration, they have many practical advantages over curved belt conveyors with belt holding mechanisms that are currently in practical use, including the ease of manufacturing, maintenance, and rearrangement of curved belt conveyors, as well as the repurposing of curved roller conveyors, and are therefore expected to be a promising curved belt conveyor in the future. [Prior art documents] [Patent documents]

[0019] [Patent Document 1] Japanese Patent Application Publication No. 05-155413 [Patent Document 2] Japanese Patent Application Laid-Open No. 2002-114343 [Patent Document 3] Japanese Patent Application Laid-Open No. 2006-213487 [Patent Document 4] Japanese Patent Application Laid-Open No. 2011-251779 [Patent Document 5] Japanese Patent Publication No. 2022-143522 [Patent Document 6] Japanese Patent Application Publication No. 9-208023 [Patent Document 7] Japanese Patent Application Laid-Open No. 2009-083946 [Patent Document 8] Japanese Patent Application Laid-Open No. 2004-203504 [Patent Document 9] Japanese Patent Application Laid-Open No. 2006-021899 [Patent Document 10] Special Publication No. 2002-502345 [Patent Document 11] Japanese Patent Application Laid-Open No. 2004-299857 [Patent Document 12] Japanese Patent Application Laid-Open No. 2000-327117 [Patent Document 13] Japanese Patent Application Laid-Open No. 2002-338025 [Patent Document 14] Japanese Patent Application Laid-Open No. 2003-206015 [Patent Document 15] Japanese Patent Application Laid-Open No. 2003-176008 [Patent Document 16] Japanese Patent Application Laid-Open No. 2007-297155 [Patent Document 17] Special Publication No. 2005-525276 [Patent Document 18] Japanese Patent Publication No. 2022-180293 Summary of the Invention [Problem to be solved by the invention]

[0020] As explained in the background art, curved belt conveyors that do not use a curved belt holding mechanism and that have a curved belt wound around a curved roller conveyor have not been able to overcome performance problems. However, because they have a small number of parts and a simple mechanical configuration, they have many practical advantages over curved belt conveyors with belt holding mechanisms that are currently in practical use, including the ease of manufacturing, maintenance, and rearrangement of curved belt conveyors, as well as the repurposing of curved roller conveyors, and are therefore expected to be a promising curved belt conveyor in the future.

[0021] The present invention aims to overcome the performance problem of poor tracking, where the trajectory of the curved belt is unstable in a curved belt conveyor that has a curved belt wound around a curved roller conveyor, without employing a belt holding mechanism for pulling the curved belt or a belt holding mechanism such as a pinch roller or tracking roller for correcting the trajectory of the curved belt. In particular, the present invention aims to prevent poor tracking, where the curved belt is biased to the inner periphery (center of the arc) of the curved belt conveyor, which is considered to be the biggest problem with this type of conveyor.

[0022] Furthermore, in order to clarify the problem that the present invention aims to solve concretely and technically, the causes of the instability of the curved belt of this type of curved roller conveyor, particularly the deviation of the curved belt to the inner circumference of the curved belt conveyor, were analyzed.

[0023] When analyzing the cause, it is necessary to recognize the belt conveyor trajectory correction technology, which is closely related to the cause and is the basis for the basic concept of the analysis. Therefore, Figures 1 and 2 show the trajectory correction technology for a straight belt conveyor.

[0024] FIG. 1 is an outline schematic plan view of a straight conveyor belt 100, in which a conveyor belt 110 is bridged between a head pulley 120 and a tail pulley 130, abstracted for explaining conveyor belt trajectory correction technology for a straight belt conveyor. FIG. 1(a) shows a trajectory correction method when the conveyor belt is deviated downward from the plane of the paper, and FIG. 1(b) shows a trajectory correction method when the conveyor belt is deviated in the opposite direction. The only difference between the two methods is that the trajectory correction direction is reversed, and the principle of this trajectory correction method is that the conveyor belt 110 enters the pulley at a right angle and travels the shortest distance around the pulley. As shown in FIG. 1(a), when the conveyor belt 110 does not meander, the direction of travel of the conveyor belt 110 is perpendicular to the side directions of the head pulley 120 and the tail pulley 130. However, if the conveyor belt 110 deviates downward from the plane of the drawing, for example, by tilting the tail pulley 130 to the right, the conveyor belt 110 will enter the side of the tail pulley 130 at a right angle and attempt to travel the shortest distance between the pulleys. This applies tension T1 to the conveyor belt 110 toward the top of the plane of the drawing along the tail pulley 130, correcting the trajectory of the conveyor belt 110 from deviating downward from the plane of the drawing to the top of the plane of the drawing. The trajectory of the conveyor belt 110 is corrected using a similar principle in FIG. 1(b). A pulley is generally a cylindrical part on which a belt is fastened when driving a rotating machine, and is a term used for a part with a groove like a pulley. However, in the case of belt conveyors and other industrial equipment, the components are not necessarily limited to cylindrical parts with grooves, as shown in FIG. 1, and the term "roller," which is a cylindrical part that rotates around a belt, is also used synonymously with the term "pulley," so in this specification, the two terms will be used interchangeably.

[0025] Such trajectory correction technology for the straight belt conveyor 100 is utilized in the shape of pulleys to prevent meandering of the conveyor belt 110 of the straight belt conveyor 100. As an example, Fig. 2 is a schematic plan view of a crowned pulley (a) and a concave pulley (b) on which a conveyor belt is wound, to explain that a crowned roller and a concave roller are used as bend pulleys, respectively, and exhibit an effective trajectory correction function. As can be seen from the figure, the traveling direction of the conveyor belt 110 is not perpendicular to the side surfaces of the crown pulley 140 and the concave pulley 150 in either case, so the conveyor belt 110 enters the side surfaces of the crown pulley 140 and the concave pulley 150 at right angles and tries to travel the shortest distance between the pulleys. As a result, tensions T1 and T2 are applied to the conveyor belt 110 along the crown pulley 140 and the concave pulley 150 toward both ends of the pulleys, thereby maintaining the conveyor belt's straightness.

[0026] Next, in a curved belt conveyor in which a curved belt is wound around a curved roller conveyor, a schematic cross-sectional view of a curved belt conveyor 200, which abstracts only the essential parts of the curved belt conveyor, cut by a horizontal plane passing through the center line of the curved rollers, is shown in Figure 3 to explain the tension (a) applied to the curved belt based on the conveyor belt trajectory correction technology of such a straight belt conveyor, as well as the centripetal force (b) applied to the curved belt of the curved belt conveyor based on the circular motion of the curved belt that is unique to curved belt conveyors. 3 shows one tapered roller 210 located at one end of a curved roller conveyor in which two or more tapered rollers are arranged radially, and a curved belt 220 having a substantially truncated cone side shape and a uniform thickness is wound around the tapered roller 210, and the state in which the curved belt 220 rotates around the tapered roller 210 is illustrated focusing on the contact surface between the outer side surface of the tapered roller 210 and the inner surface of the curved belt 220, and the outer surface of the curved belt 220. For ease of understanding, the taper angle of the tapered roller 210 and the thickness of the curved belt 220 are made extremely large compared to the width of the curved belt conveyor 200.

[0027] As can be seen from FIG. 3(a), the tension applied to the curved belt 220 is such that the inner surface of the curved belt 220 and the side surface of the tapered roller 210 rotate about a common rotation center 230. At the contact surface between the outer side surface of the tapered roller 210 and the inner surface of the curved belt 220, the curved belt 220 always enters at a right angle with respect to the tapered roller 210. Therefore, no large tension is generated on the inner surface of the curved belt 220. However, when focusing on the outer outer surface of the curved belt 220, at a rotation center 240 different from the rotation center 230 of the inner surface of the curved belt 220, the radius r2 of the inner peripheral end of the outer outer surface of the curved belt 220 is larger than the radius r1 of the inner peripheral end of the inner surface of the curved belt 220. Since the outer outer surface of the curved belt 220 cannot enter at a right angle with respect to the tapered roller 210, it enters at a right angle and generates a large tension in the direction of the rotation center 240 of the outer outer surface of the curved belt 220 so as to travel the shortest distance with respect to the tapered roller 210. Such a phenomenon causes the curved belt in a curved belt conveyor of a method of winding a curved belt around a curved roller conveyor to shift toward the inner peripheral side, and also causes meandering, reduced lifespan, and damage of the curved belt due to deformation.

[0028] Furthermore, as can be seen from FIG. 3(b), centripetal forces F1 and F2 based on the circular motion of the curved belt 2 which are peculiar to the curved belt conveyor 200 are generated in the curved belt 220, causing the curved belt 220 to shift toward the inner peripheral side. Moreover, since a larger centripetal force acts on the outer surface of the curved belt than on the inner surface of the curved belt , it causes meandering, reduced lifespan, and damage of the curved belt due to deformation of the curved belt 220. This difference is clear, for example, when looking at the inner peripheral end of the curved belt 220 in FIG. 3(b). The inner peripheral end of the inner surface of the curved belt 220 has a rotation speed v1 with a radius r1 and an angular velocity ω1, while the inner peripheral end of the outer surface of the curved belt 220 has a rotation speed v2 with a radius r2 and an angular velocity ω2(=ω1). Although the angular velocities are equal, the radii are greatly different, so v1 << v2. Therefore, the centripetal forces of the inner peripheral end of the inner surface and the inner peripheral end of the outer surface of the curved belt 220 are F1 = m·v1 2 / r1 and F2 = m·v22 / r2, which is proportional to the square of the rotation speed, so that the centripetal force F2 at the inner circumferential end of the outer surface of the curved belt 220 is larger.

[0029] As described above, a large force acts on the curved belt of a curved belt conveyor, moving toward the center of rotation of the curved belt conveyor, causing problems such as deviation, meandering, shortened lifespan, and damage to the curved belt. Therefore, the studies described in paragraphs 0010 to 0018 were conducted, and these problems could be solved by providing a belt holding mechanism for the curved belt. However, these problems have not yet been solved without providing a belt holding mechanism for the curved belt.

[0030] Therefore, the object of the present invention is to provide a curved belt conveyor in which a curved belt is wound around a curved roller conveyor, which does not have a belt holding mechanism for the curved belt, and which solves the above-mentioned technical causes of problems such as deviation, meandering, shortened lifespan, and damage of the curved belt. In particular, the object of the present invention is to find a means to solve the technical causes of tracking problems, such as deviation and meandering of the curved belt. [Means for solving the problem]

[0031] As described in paragraphs 0022 to 0028, the inventors analyzed the tension and centripetal force acting on a curved belt conveyor, which are directed toward the center of the curved belt's rotation, and considered whether there might be a correlation with the thickness of the curved belt. Therefore, a curved belt whose thickness continuously decreases from the outer periphery to the inner periphery of the curved belt was examined using FIG. 4. Similar to FIG. 3, FIG. 4 illustrates a curved roller conveyor having two or more tapered rollers arranged radially, with one tapered roller 310 positioned at one end. A curved belt 320, which has a substantially truncated cone-like side surface and whose thickness continuously decreases from the outer periphery to the inner periphery, is wound around the tapered roller 310. The curved belt 320 is rotated by the tapered roller 310, with attention focused on the contact surface between the outer side of the tapered roller 310 and the inner surface of the curved belt 320, and the outer surface of the curved belt 320. Here, what is characteristic of the curved belt 320 and tapered roller 310, whose film thickness changes continuously, is that the extension lines of the inner and outer surfaces of the curved belt 320 and the extension lines of the side surface and center line of the tapered roller 310 intersect at a single convergence point 330. As is clear from this diagram, the curved belt 320 enters the tapered roller 310 at a right angle, so it is thought that tension from the outer circumferential side to the inner circumferential side of the curved belt 320 does not occur in principle. In addition, because the radii r1 of the inner peripheral ends of the inner and outer surfaces of the curved belt 320 are equal, it is thought that the centripetal forces acting on the inner and outer surfaces of the curved belt 320 do not generate stress that would deform the curved belt 320, although there is a difference in centripetal force due to the difference in angular velocity.

[0032] Based on this study and various detailed studies, it was found that, as will be explained with reference to Figure 4, the means for solving the problems of the present invention is not simply to have the extension lines of the inner and outer surfaces of curved belt 320 and the extension lines of the side and center line of tapered roller 310 intersect at one convergence point 330, but that the problems of the present invention can also be solved by introducing a belt tension equalization mechanism that equalizes the tension applied to curved belt 320 in the circumferential direction of concentric circles with convergence point 330 as the center of the circles. Furthermore, it was found that introducing a mechanism to prevent sliding between tapered roller 310 and curved belt 320 is more preferable for solving the problems of the present invention, which led to the completion of the present invention.

[0033] That is, the present invention is a curved belt conveyor comprising a curved belt formed into the shape of the side surface of a substantially truncated cone and two or more rotatable tapered rollers arranged radially, the inner surface of the curved belt contacting the outer surface of the tapered rollers and wound around the tapered rollers so as to bridge the curved belt, and the curved belt rotates as the tapered rollers rotate, the curved belt conveyor further comprising a belt tension equalizing mechanism that equalizes the circumferential tension of concentric circles whose center is the vertex where the generatrix of the curved belt intersects, across the entire area of ​​the curved belt, and the belt tension equalizing mechanism controls the longitudinal movement of the center line of the curved belt within a predetermined range as the curved belt rotates, causing the curved belt to rotate along a predetermined orbit.

[0034] The equalization of belt tension in such a curved belt conveyor is a fundamental technical idea for the curved belt to rotate by tapered rollers without causing tracking problems, and any mechanism that can realize the equalization of belt tension can be adopted.

[0035] Therefore, the belt tension equalizing mechanism is not limited, but is preferably composed of: tension equalizing tapered rollers arranged in a radial pattern such that the extensions of all of the center lines of the tapered rollers and the extensions of all of the generatrixes of the tapered rollers that are on the same plane as the cross section passing through the center lines converge to one point; and a tension equalizing curved belt in which, in a cross section obtained by cutting the curved belt conveyor in a horizontal plane, the convergence point of the tapered rollers is the center of a circle, and the curved belt has a shape surrounded by an outer circular arc formed with a predetermined radius shorter than the outer peripheral end of the tapered roller, an inner circular arc formed with a predetermined radius longer than the inner peripheral end of the tapered roller, and the outer generatrixes of the tapered rollers at both ends, and the lengths of all arcs from the outer arc to the inner arc are a predetermined percentage selected from approximately 96 to 99%, and the inner surface of the side surface of an approximately truncated cone has a shape formed by arcs.

[0036] Furthermore, in a curved belt conveyor constructed with the tension-leveling tapered rollers and tension-leveling curved belt designed in this manner, it is preferable that, in a cross section taken along a horizontal plane passing through the centerlines of the tension-leveling tapered rollers, the tension-leveling curved belt is designed so that the angle formed by the extensions of the two generatrix lines at both ends of the outer surface of the tension-leveling curved belt that contact the tension-leveling tapered rollers at both ends and the intersection of these two extensions is equal to or greater than the angle formed by the extensions of the two outer generatrix lines of the tension-leveling tapered rollers at both ends and the convergence point where the centerlines and extensions of the generatrix lines of all the tapered rollers meet. A curved belt conveyor equipped with such a tension-leveling curved belt is significantly more effective in resolving problems such as curved belt deviation, meandering, reduced lifespan, and damage. It is particularly suitable as a means of resolving technical causes of tracking problems, such as curved belt deviation and meandering.

[0037] In particular, it is more preferable for the purpose of solving the problems of the present invention that the tension-leveling curved belt is designed so that the intersection of the extensions of the two generatrix lines at both ends of the outer surface of the tension-leveling curved belt that contact the tension-leveling tapered rollers at both ends coincides with the convergence point of the tension-leveling tapered rollers.

[0038] Such a belt tension equalizing mechanism maintains stable running of the curved belt on the curved belt conveyor and prevents tracking problems. However, it is more preferable to provide a sliding prevention mechanism on the tension equalizing tapered roller in addition to the belt tension equalizing mechanism in order to increase the contact force and friction force between the tension equalizing tapered roller and the tension equalizing curved belt and prevent sliding.

[0039] The anti-slip mechanism is not particularly limited as long as it can increase the contact force and friction force between the tension-leveling tapered roller and the tension-leveling curved belt without impairing the belt tension-leveling mechanism, but it is preferable that the anti-slip mechanism has a grip-enhancing protrusion that has been physically or chemically processed to increase the contact force and friction force with the inner surface of the tension-leveling curved belt, located at a distance of approximately 0 to 50% from the outer peripheral end of the tension-leveling tapered roller. By configuring the grip-reinforcing convex portion, not only is sliding between the tension equalizing tapered roller and the tension equalizing curved belt eliminated, but this elimination of sliding also drastically reduces the loss of tension applied to the tension equalizing curved belt, maintaining a more stable running of the curved belt and improving the effectiveness of preventing tracking defects.

[0040] Physical processing to increase the contact force and friction force includes forming convex portions with heights such as radial or tapered crown shapes or the inverse concave shapes as the overall shape of the grip-enhancing convex portions on the surface of the tension-leveling tapered roller; forming grooves such as longitudinal grooves, lateral grooves, threaded grooves, helical grooves, double helical grooves, and diamond-cut grooves; and forming fine irregularities, such as those formed on the surface of a general conveyor belt, such as the weave of canvas. To increase the contact force, the grip-enhancing convex portions can be made taller, but only to the extent that the height does not cause an imbalance in tension on the tension-leveling curved belt. The friction force can be further increased by using these physical processing methods in combination.

[0041] Chemical processing increases the coefficient of friction by lining the surface of the tension-leveling tapered roller or the grip-enhancing convex surfaces molded onto the tension-leveling tapered roller. Rubber-based resins with high coefficients of friction are preferred for the lining. Examples of such rubber-based resins include silicone rubber (VMQ, FVMQ), urethane rubber (AU, EU), isoprene rubber (IR), butadiene rubber (BR), styrene-butadiene rubber (SBR), chloroprene rubber (CR), nitrile rubber (NBR), isobutylene-isoprene rubber (IIR), ethylene propylene rubber (EPDM), chlorosulfonated polyethylene rubber (CSM), acrylic rubber (ACM), fluororubber (FKM), and epichlorohydrin rubber (ECO).

[0042] Furthermore, tapered rollers include tapered pipe-type tapered rollers (pulleys) in which a tapered pipe is inserted into the shaft, and tapered adapt-type tapered rollers (pulleys) in which a tapered adapt is inserted into the shaft, and the grip-enhancing protrusions can be provided on the tapered pipe and tapered adapt. In both physical and chemical processing, the protrusions can be provided during the molding process of the tapered pipe and tapered adapt, but they can also be provided in the form of a sleeve used as a coating material for the roller. Furthermore, chemical processing can be applied to tapered pipes and tapered adaptors that have been subjected to physical processing, as well as to sleeves that are coated on these.

[0043] In particular, sleeves are thin, cylindrical components that can be easily physically and / or chemically processed, and grip-enhancing projections can be easily attached, making them suitable for incorporating grip-enhancing projections. As described below, the shape of the sleeve depends on the relationship between the angle formed by the extensions of the two generatrix lines at both ends of the outer surface of the tension-equalizing curved belt that contact the tension-equalizing tapered rollers at both ends and the intersection of these two extensions, and the angle formed by the extensions of the two generatrix lines on the outside of the tension-equalizing tapered rollers at both ends and the convergence point of these tapered rollers. This also depends on the width of the curved belt conveyor, and is not particularly limited. However, for cylindrical sleeves, the width is preferably about 20 to 80 mm and the thickness is preferably about 1.0 to 3.0 mm, and the width is preferably about 30 to 70 mm and the thickness is preferably about 1.2 to 2.5 mm. Furthermore, the sleeve can be made of a variety of materials, including general-purpose resins such as nylon, polyvinyl chloride, and polyester, as well as rubber-based resins with high friction coefficients, making it easy to mold and form grooves. Furthermore, the ability to select from a variety of materials means that lining processing is not required. For these reasons, sleeves are suitable and preferably used as a method for providing grip-enhancing protrusions to tension-leveling tapered rollers.

[0044] Furthermore, in order to effectively exhibit the anti-slip function in a curved belt conveyor equipped with a belt tension equalizing mechanism, in addition to the specific position of the anti-slip mechanism arranged in the tension equalizing tapered roller as explained in paragraph 0040, it is preferable to select from the radially arranged tension equalizing tapered rollers that make up the curved belt conveyor, and both ends of the tension equalizing tapered rollers wound around the tension equalizing curved belt are suitable. This also applies when grip-enhancing protrusions are used as the anti-slip mechanism.

[0045] In addition, in a curved belt conveyor equipped with a belt tension equalizing mechanism as described in paragraph 0036, it is preferable that, in a cross section of the curved belt conveyor taken along a horizontal plane, the angle formed by the extensions of the two generatrix lines at both ends of the outer surface of the tension equalizing curved belt that contacts the tension equalizing tapered rollers at both ends and the intersection of these two extensions is equal to or greater than the angle formed by the extensions of the two outer generatrix lines of the tension equalizing tapered rollers at both ends and the convergence point where the extensions of the generatrix lines meet and the center lines of all the tapered rollers. Such a relationship in magnitude of the angle also exists when grip-enhancing protrusions are provided on the tension equalizing tapered rollers as an anti-slip mechanism in addition to the belt tension equalizing mechanism. In other words, in a cross section taken along a horizontal plane passing through the center lines of the tension-leveling tapered rollers of a curved belt conveyor equipped with a belt tension equalizing mechanism and grip-reinforcing protrusions as a sliding prevention mechanism, the angle formed by the intersection of two tangents to the maximum and minimum protrusions on the outer surface of the tension-leveling curved belt that contacts the tension-leveling tapered rollers at both ends and the two tangents is preferably equal to or greater than the angle formed by the extensions of the two outer generatrix lines of the tension-leveling tapered rollers at both ends and the convergence point where the extensions of the generatrix lines meet with the center lines of all the tapered rollers. A curved belt conveyor designed in this way completely eliminates problems such as curved belt deviation, meandering, shortened lifespan, and damage, particularly tracking defects such as curved belt deviation and meandering, due to the synergistic effect of the tension equalizing mechanism and the sliding prevention mechanism of the grip-reinforcing protrusions.

[0046] Furthermore, in accordance with paragraph 0038, it is even more preferable that the tension-leveling curved belt and tension-leveling tapered rollers are designed so that the intersection of two tangents to the maximum and minimum protrusions at both ends of the outer surface of the tension-leveling curved belt, which contacts the tension-leveling tapered rollers at both ends, coincides with the convergence point of the tension-leveling tapered rollers, and that the tension-leveling curved belt and tension-leveling tapered rollers are provided with grip-enhancing convex portions.

[0047] The belt tension equalizing mechanism exerts different effects depending on the material and structure of the curved belt. The tension equalizing curved belt of the present invention has a film thickness of about 0.7 to 2.6 mm and a mass of about 1.0 to 3.0 kg / m. 2 As for the material, a tension-equalizing curved belt that does not have a core made of the above-mentioned rubber-based resin or thermoplastic polyurethane has excellent elasticity, equalizes the tension of the belt, and is effective in preventing tracking defects. To more effectively prevent tracking defects, a thickness of about 1.0 to 2.0 mm and a mass of about 1.2 to 1.6 kg / m 2 The material is preferably a tension-equalizing curved belt that does not have a core made of thermoplastic polyurethane. Thermoplastic polyurethane has the advantage that its composition can be changed to control its physical properties, making it possible to produce curved belts suited to various applications.

[0048] Conventional conveyor belts are typically constructed with a canvas core made from polyester fibers, polyamide fibers including nylon, and various types of rubber laminated together. While these conveyor belts offer advantages in terms of strength and lifespan, they lack elasticity and have anisotropic physical properties, making them unsuitable for achieving the fundamental technical solution of the present invention, i.e., tension uniformity. Therefore, a curved belt without a core is a suitable configuration for a tension-uniforming curved belt. However, in a tension-uniforming curved belt that is subjected to circumferential tension around the convergence point of the extension of the center line of the tension-uniforming tapered roller and the extension of the generatrix, resin filaments arranged in the circumferential direction of the curved belt conveyor can be used as the core to ensure long-term durability. Such filaments eliminate the drawbacks of conventional canvas and do not impair the tension uniformity of the curved belt. In particular, the filaments are preferably made of fibers or threads made of polyurethane or nylon, which have excellent elasticity.

[0049] The curved belt conveyor of the present invention described above is a curved belt conveyor in which a tension-leveling curved belt is wound around multiple radially arranged tension-leveling tapered rollers. While this can be used alone, multiple curved belt conveyors can be installed as curved belt conveyor units, with the convergence points of the center lines and generatrix extensions of the tension-leveling tapered rollers aligned and the spacing between the tension-leveling tapered rollers approximately equal to the spacing between adjacent curved belt conveyor units. This method allows for the creation of curved conveyor paths with excellent tracking performance by connecting curved belt conveyor units that can fully utilize the effects of the tension-leveling mechanism. Furthermore, by combining multiple curved belt conveyor units as basic units and with straight conveyors, core conveyor routes in logistics centers, various factories, etc. can be freely configured. [Effects of the Invention]

[0050] According to the present invention, in a curved belt conveyor in which a curved belt is wound around a curved roller conveyor, problems such as deviation, meandering, shortened lifespan, and damage of the curved belt can be solved without providing a belt holding mechanism for the curved belt. In particular, it is effective in preventing tracking problems such as deviation and meandering of the curved belt. Furthermore, it is also effective in constructing a flexible conveying route by combining the curved belt conveyors of the present invention as basic units.

[0051] Furthermore, the curved belt conveyor of the present invention, which has a simple structure without a belt holding mechanism, has the same mechanism and economy as a roller curved conveyor, and can achieve stable and safe transport of items such as carbonated beverages, which was difficult with a roller curved conveyor, with less impact, no falling, and no risk of explosion. Furthermore, it can transport items of a size that could not be transported with conventional roller conveyors, without bundling the items in cardboard boxes or containers, thereby greatly easing restrictions on the items to be transported. Furthermore, it produces extremely little transport noise and impact noise, making the entire transport line at a logistics center quieter and significantly improving the working environment of logistics center workers. [Brief explanation of the drawings]

[0052] [Figure 1] FIG. 1 is a schematic plan view of an abstracted straight conveyor belt in which the conveyor belt is bridged between a head pulley and a tail pulley, for explaining a conveyor belt trajectory correction technique for a straight belt conveyor. [Figure 2] As an example of utilizing conveyor belt trajectory correction technology to prevent meandering of a straight belt conveyor, a crown-shaped pulley (a) and a concave-shaped pulley (b) on which a conveyor belt is wound are shown. [Figure 3] This is a schematic cross-sectional view of a curved belt conveyor cut through a horizontal plane, with only the essential parts abstracted to explain the tension (a) acting on the curved belt based on the conveyor belt trajectory correction technology of a straight belt conveyor, and the centripetal force (b) acting on the curved belt of a curved belt conveyor based on the circular motion of the curved belt that is unique to curved belt conveyors, in a curved belt conveyor in which a curved belt is wound around a curved roller conveyor. [Figure 4]This is a schematic cross-sectional view of a curved belt conveyor cut by a horizontal plane, with only the essential parts abstracted, illustrating the state of the curved belt rotating by tapered rollers, focusing on the contact surface between the outer side of the tapered roller and the inner surface of the curved belt, and the outer outer surface of the curved belt, in a curved belt conveyor that is a type in which a curved belt is wound around a curved roller conveyor, where the curved belt is a curved belt that becomes continuously thinner from the outer periphery to the inner periphery of the curved belt. [Figure 5] According to one embodiment of the present invention, the tension equalizing mechanism includes tension equalizing tapered rollers arranged radially so as to have a convergence point where the center lines of the tapered rollers and the extension lines of the generatrix converge to one point, and a curved belt, in a cross section of the curved belt conveyor cut by a horizontal plane, the convergence point of the tapered rollers is the center of a circle, and the curved belt has an outer circumferential arc formed with a predetermined radius shorter than the outer circumferential end of the tapered rollers, an inner circumferential arc formed with a predetermined radius longer than the inner circumferential end of the tapered rollers, and tapered rollers at both ends. and a tension equalizing curved belt having a shape surrounded by the outer generatrix of the tension equalizing tapered roller, with the inner surface of the side of the approximately truncated cone being formed by arcs that account for approximately 98% of the length of all arcs from the outer arc to the inner arc, and the tension equalizing curved belt wound around the tension equalizing tapered roller. (a) is a schematic plan view of a curved belt conveyor, and (b) is a schematic cross-sectional view taken perpendicular to the paper and passing through the center line of the tapered roller that constitutes the tension equalizing tapered roller of the plan view (a). [Figure 6] (a) is the same schematic cross-sectional view as Figure 5(b), (b) is a schematic cross-sectional view passing through the center line of a tapered roller with a roller width of 600 mm, a small diameter of 40 mm, and a large diameter of 65 mm, and (c) is a schematic cross-sectional view taken vertically through the center line of a tension-equalizing tapered roller that is not at either end of a curved belt conveyor equipped with a tension-equalizing mechanism consisting of a tension-equalizing tapered roller arranged in the same manner as in Figure 5 and a tension-equalizing curved belt designed in the same manner as in Figure 5, using the tapered roller of (b). [Figure 7](a) is a schematic cross-sectional view of a curved belt conveyor cut in a horizontal plane, with the main parts abstracted, based on Figure 3(a), and (b) is a schematic cross-sectional view of a curved belt conveyor cut in a horizontal plane, with the main parts abstracted, based on Figure 4. These figures are shown side by side to compare the effect of the film thickness of the curved belt. [Figure 8] This is a schematic cross-sectional view of a curved belt conveyor cut by a horizontal plane, with only the essential parts abstracted, showing the state of the curved belt rotating by the tapered roller, focusing on the contact surface between the outer side of the tapered roller and the inner surface of the curved belt, and the outer outer surface of the curved belt, in order to compare the effect of the thickness of the curved belt on the tension of the curved belt in a curved belt conveyor that is wound around a curved roller conveyor. [Figure 9] This is a schematic cross-sectional view of a curved belt conveyor cut by a horizontal plane, with only the essential parts abstracted, showing the state of the curved belt rotating by the tapered roller, focusing on the contact surface between the outer side of the tapered roller and the inner surface of the curved belt, and the outer outer surface of the curved belt, in order to compare the effect of the thickness of the curved belt on the centripetal force of the curved belt in a curved belt conveyor that is a type in which a curved belt is wound around a curved roller conveyor. [Figure 10] This is a cross-sectional schematic diagram using the same method as Figure 6 to analyze the tracking prevention effect of the tension-equalizing curved belt in a curved belt conveyor that has a type in which a curved belt is wound around a curved roller conveyor equipped with a belt tension equalizing mechanism, and in which the protrusions arranged as sleeves on the tension-equalizing tapered rollers have a tracking prevention effect of the tension-equalizing curved belt. [Figure 11] This is a cross-sectional schematic diagram using the same method as Figure 6 to explain that in a curved belt conveyor equipped with a belt tension equalizing mechanism and in which a curved belt is wound around a curved roller conveyor, an inclined tension equalizing curved belt whose film thickness changes continuously has a tracking prevention effect. [Figure 12] 1 is a schematic diagram showing a cross-sectional structure of a conveyor belt that can be used in a curved belt conveyor equipped with a belt tension equalizing mechanism of the present invention. [Figure 13]1A and 1B are schematic diagrams showing the shape of a sleeve with longitudinal grooves that can be used as a grip-reinforcing protrusion as an anti-slip mechanism in a curved belt conveyor equipped with a belt tension equalizing mechanism of the present invention, where (a) is a perspective view and (b) is a cross-sectional view taken along the center line of the sleeve. [Figure 14] 1A to 1C are cross-sectional schematic diagrams illustrating a method for arranging grip-reinforcing protrusions of the present invention for a tapered pipe type tapered roller and a tapered adapt type tapered roller. [Figure 15] FIG. 1 is a schematic plan view showing an outline of a combined curved belt conveyor in which a curved roller conveyor equipped with a belt tension uniforming mechanism of the present invention is combined as a unit. DETAILED DESCRIPTION OF THE INVENTION

[0053] The present invention will be described in more detail below using the embodiments shown in the drawings, but the present invention is not limited to these and can be implemented in various modifications within the scope that does not deviate from the gist of the present invention, and is limited only by the technical ideas described in the claims.

[0054] FIG. 5 shows a belt tension equalizing mechanism according to one embodiment of the present invention, in which seven tapered rollers 410 are radially arranged to have a convergence point 460 where the center lines of the seven tapered rollers and the extensions of the generatrix converge, and in a cross section cut by a horizontal plane passing through the center line of the tension equalizing tapered roller 410, the convergence point where the center line of the tension equalizing tapered roller 410 and the extensions of the generatrix converge is the center of a circle, and the tension equalizing tapered roller 410 has an outer circumferential arc formed with a predetermined radius shorter than the outer circumferential end of the tension equalizing tapered roller 410, an inner circumferential arc formed with a predetermined radius longer than the inner circumferential end of the tension equalizing tapered roller 410, and a circle at both ends. 1A is a schematic plan view of a curved belt conveyor 400 in which the tension-leveling curved belt 420 is wound around the tension-leveling tapered roller 410. The tension-leveling curved belt 420 has a shape surrounded by the outer generatrix of a tension-leveling tapered roller 410 and the outer generatrix of the tapered roller 410, and the inner surface of the side of the approximately truncated cone has a shape formed by arcs with a length of approximately 98% of the total length from the outer circular arc to the inner circular arc. The tension-leveling curved belt 420 is wound around the tension-leveling tapered roller 410. The tension-leveling curved belt 420 is a stretch curved belt without a core made of thermoplastic polyurethane, has a film thickness of approximately 1.2 mm, and a mass of approximately 1.4 kg / m. 2 The stretch curve belt has uniform physical properties over the entire surface.

[0055] Although it cannot be seen from this figure that the tension-leveling curved belt 420 is wound around the tension-leveling tapered roller 410 with a substantially constant tension in the circumferential direction of a concentric circle with the convergence point 460 as the center of the circle, this is clear from the design concept of the tension-leveling curved belt 420 described above.

[0056] Furthermore, as is clear from FIG. 5( a), the generatrix of the tension leveling tapered rollers 410 located on the outside of both ends and the generatrix of the tension leveling curved belt 420 that comes into contact with those generatrix are in a parallel positional relationship, and the film thickness of the tension leveling curved belt is approximately uniform. Therefore, the angle formed by the extensions of the two generatrixes at both ends of the outer surface of the tension leveling curved belt 420 that comes into contact with the tapered rollers 410 at both ends of the tension leveling tapered roller 410 and the intersection 470 of these two extensions is equal to the angle formed by the extensions of the two generatrixes on the outside of the tapered rollers 410 at both ends of the tension leveling tapered rollers 410 at both ends and the convergence point 460 where the center lines and extensions of the generatrix of all the tapered rollers 410 converge. Considering this, it can be understood that the tension leveling curved belt 420 is wound around the tension leveling tapered roller 410 with approximately constant tension in the circumferential direction of a concentric circle with the convergence point 460 as the center of the circle.

[0057] In a curved belt conveyor 400 equipped with a belt tension equalization mechanism, this angle condition is a necessary condition for achieving belt tension equalization; simply satisfying this condition does not necessarily mean that the belt tension will be equalized. However, the conditions for the tension equalization curved belt 410, which constitutes one of the belt tension equalization mechanisms described in paragraph 0053, specify its inner surface, not its outer surface. Therefore, for the belt tension equalization mechanism to function more effectively, the outer surface of the tension equalization curved belt 420 must be specified. Without this specification, there are no restrictions on the cross-sectional shape of the curved belt, and it cannot be denied that tension equalization of the curved belt cannot be achieved. However, this does not apply if the film thickness is uniform. Therefore, the fact that the angle formed by the extensions of the two generatrix lines at both ends of the outer surface of the tension leveling curved belt 420 that contact the tapered rollers 410 at both ends and the intersection 470 of these two extensions is equal to the angle formed by the extensions of the two generatrix lines on the outside of the tapered rollers 410 at both ends of the tension leveling tapered rollers 410 at both ends and the convergence point 460 where the extensions of the center lines and generatrix lines of all the tapered rollers 410 meet specifies the tension leveling curved belt 420 and presents the conditions for the belt tension leveling mechanism to function effectively. However, this is not to deny that the belt tension leveling mechanism is effective as a higher-level concept that takes this point into consideration.

[0058] Now, the angle formed by the extensions of the two generatrix lines of the tension leveling tapered rollers 410 at both ends and the convergence point 460 was compared with the angle formed by the extensions of the two outer generatrix lines of the tension leveling curved belt that contacts the tension leveling tapered rollers 410 at both ends and their intersection point 470. It can be seen that this is the same as the comparison of angles when the tension leveling curved belt 420 is wound around a single tension leveling tapered roller. In other words, this is equivalent to comparing the angle formed by the extensions of the two generatrix lines of a single tension leveling tapered roller 410 and the convergence point 460 with the angle formed by the extensions of the two outer generatrix lines of the tension leveling curved belt 420 that is wound around this tension leveling tapered roller 410 and contacts the generatrix lines of this tension leveling tapered roller and their intersection point 470. Therefore, as shown in Figure 5(b), in the cross-sectional view of a certain tension leveling tapered roller 410 in Figure 5(a), the angle formed by the extensions of the two upper and lower generatrix lines of the tension leveling tapered roller 410 and the convergence point 360 is equivalent to the angle formed by the extensions of the two outer generatrix lines of the tension leveling curved belt 420 that contact the generatrix lines of the tension leveling tapered roller 410 and the intersection point 470 of these lines. Hereinafter, when specifically describing the curved belt conveyor of the present invention using its embodiments, the cross-sectional view of Figure 5(b) will be used. This is for the purpose of making the description easier to understand.

[0059] Therefore, first, the angular relationship shown in paragraph 0055 will be explained in more detail, and in order to demonstrate the validity of the angular relationship explained in paragraph 0056, it will be shown in Figure 6 using the schematic cross-sectional view of Figure 5(b).

[0060] 6(a) shows the same schematic cross-sectional view as FIG. 5(b), FIG. 6(b) shows a schematic cross-sectional view passing through the center line of a tapered roller 411 used in the calculation, which has a roller width of 600 mm, a small diameter of 40 mm, and a large diameter of 65 mm, and FIG. 6(c) shows a schematic cross-sectional view passing through the center line of a tension-equalizing tapered roller 411 not at both ends when a curved belt conveyor is fabricated using the tapered roller 411 of FIG. 5 and equipped with a tension-equalizing mechanism consisting of a tension-equalizing tapered roller 411 arranged in the same manner as in FIG. 5 and a tension-equalizing curved belt 420L with a film thickness of 1.2 mm designed in the same manner as in FIG. 5. For ease of understanding, in FIG. 6(b) and FIG. 6(c), the tapered roller drive belt 440 and the frame 450 supporting the tapered roller shown in FIG. 6(a) are omitted, and the tapered roller 410, which was tilted in the curved belt conveyor 400, is made horizontal. In addition, to simplify the calculations, the widths of the curved belt and the tapered roller are made to be the same, but this does not affect the angle under consideration.

[0061] From the schematic diagram of FIG. 6(c), it can be seen that the angle θ2 formed by the extensions of the two generatrix lines at both ends of the outer surface of the tension-leveling curved belt 420L that contact the top and bottom of the tension-leveling tapered roller 411 (but not both ends) and the intersection 470L of these two generatrix lines is 0.0208 rad, and this angle is the same as the angle θ1 (0.0208 rad) formed by the extensions of the two upper and lower generatrix lines with the center line of the tension-leveling tapered roller 411 as the center of symmetry, and the convergence point 460L where the extensions of the generatrix lines and the center line of the tension-leveling tapered roller meet. Therefore, as explained in paragraph 0055, in the curved belt conveyor 400 shown in FIG. 5, the angle formed by the extensions of the two generatrix lines at both ends of the outer surface of the tension-leveling curved belt 420 that contact the tension-leveling tapered rollers 410 at both ends and the intersection 470 of these two extensions is consistent with the angle formed by the extensions of the two generatrix lines on the outside of the tension-leveling tapered rollers 410 at both ends of the tension-leveling tapered rollers 410 at both ends and the convergence point 460 where the extensions of the center lines and generatrix lines of all the tapered rollers converge.

[0062] A study of a curved belt conveyor that does not have a belt holding mechanism and that winds the curved belt suggests that the thickness of the curved belt is an important factor. In this regard, the influence of the thickness of the curved belt on the tension and centripetal force acting on the curved belt is explained using Figures 7 and 8.

[0063] First, let's consider tension. As shown in Figure 4, in a curved belt conveyor 300 in which a curved belt 320, which is approximately frustum-shaped and whose thickness gradually decreases from the outer periphery to the inner periphery, is wound around a tapered roller 310, the curved belt 320, whose thickness is inclined, enters the tapered roller 310 at a right angle, so it is thought that tension from the outer periphery to the inner periphery of the curved belt 320, whose thickness is inclined, does not occur in principle. To compare this situation with a curved belt with a uniform thickness, Figure 7(a) cites Figure 3(a) and Figure 7(b) cites Figure 4. As can be seen from FIG. 7(a), the outer surface of curved belt 220 with a uniform thickness tends to enter tapered roller 210 at a right angle, and a strong tension T5 acts toward intersection 240 of the extensions of the generatrix at both ends of curved belt 220, whereas the inner and outer surfaces of curved belt 320 with an inclined thickness as shown in FIG. 7(b) enter tapered roller 310 at a right angle, and therefore the tension T6 acting toward intersection 330 of the extensions of the generatrix at both ends of curved belt 320 is considered to be extremely small. Here, this intersection 330 is also the convergence point 330 where the extensions of the center line and generatrix of the tapered roller 310 converge, and a noteworthy feature is that the angle formed by this convergence point and the extensions of the two generatrix at both ends of the curved belt 320, whose film thickness is inclined, is larger than the angle formed by the two outer generatrix at both ends of the tapered rollers 210 and 310 and the convergence points 230 and 330 where the center lines and generatrix of the tapered rollers 210 and 310 converge, and the angle formed by the extensions of the two generatrix at both ends of the curved belt 220 and the intersection point 240 of these extensions.

[0064] Next, let's consider centripetal force. In this case, too, Figure 4 shows a curved belt conveyor 300 in which a curved belt 320, roughly shaped like a truncated cone and whose thickness gradually decreases from the outer periphery to the inner periphery, is wound around a tapered roller 310. When viewed from the inner and outer peripheries of the curved belt 320, the radius r1 of the inner periphery, with the convergence point 330 as the center of rotation, is equal. Therefore, although there is a difference in centripetal force due to the difference in angular velocity, the centripetal force acting on the inner and outer surfaces of the curved belt 320 is unlikely to generate stress that would deform the curved belt 320. To compare this situation with a curved belt with a uniform thickness, Figures 8 and 9, which are superimposed views of Figures 3(a) and 4 cited in Figure 7, are used. Figure 8 shows the superimposed view as is to provide an overall view, while Figure 9 shows an enlarged view to clearly illustrate the key points for comparing centripetal forces.

[0065] As can be seen from the figure, the radius r2 of the inner peripheral edge of the outer surface of the curved belt 220 with a uniform thickness is larger than the radius r1 common to the inner peripheral edge of the inner surface of the curved belt 220 with a uniform thickness and the inner peripheral edges of the outer and inner surfaces of the curved belt 320 with an inclined thickness, and the angular velocity ω2 of the outer surface of the curved belt 220 with a uniform thickness is equal to the angular velocity ω1 of the inner surfaces of both curved belts 220, 320. Therefore, the peripheral velocity v2 of the outer surface of the curved belt 220 with a uniform thickness is large, and the centripetal force F2, which is proportional to the power of the peripheral velocity, is much larger than the centripetal force F1 of the inner surfaces of both curved belts 220, 320. Therefore, it is thought that the curved belt 220 with a uniform thickness is likely to shift toward the inner circumference, which may also lead to deformation of the curved belt 220. The radius r1 of the outer surface and the inner surface of the curved belt 320 with a gradient film thickness is equal, but the angular velocity ω3 of the outer surface is greater than the angular velocity ω1 of the inner surface, so the peripheral velocity v3 of the outer surface is greater than the peripheral velocity v1 of the inner surface, and the centripetal force F3 of the outer surface is greater than the centripetal force F1 of the inner surface. However, compared to the curved belt 220 with a uniform film thickness, it is considered that the curved belt 320 with a gradient film thickness is extremely unlikely to shift toward the inner circumference side or to deform.

[0066] As explained in paragraph 0062, in Figures 8 and 9, a notable feature of the curved belt 320 having a gradient film thickness is that the intersection 330 of the extension lines of the two generatrix lines at both ends of the curved belt 320 having a gradient film thickness coincides with the convergence points 230, 330 where the two outer generatrix lines at both ends of the tapered rollers 210, 310 and the center lines and generatrix lines of the tapered rollers 210, 310 converge, and the angle formed by the extension lines of the two generatrix lines at both ends of the curved belt 320 having a gradient film thickness and these intersection points 330 is larger than the angle formed by the two outer generatrix lines at both ends of the tapered rollers 210, 310 and the convergence points 230, 330 where the center lines and generatrix lines of the tapered rollers 210, 310 converge, and the angle formed by the extension lines of the two generatrix lines at both ends of the curved belt 220 having a uniform film thickness and these intersection points 240, which is equal to the angle formed by the angle formed by the two outer generatrix lines at both ends of the tapered rollers 210, 310 and the center lines and generatrix lines of the tapered rollers 210, 310 converge, and

[0067] Based on these theoretical calculations, we assumed that thickening the outer periphery of the curved belt would lead to a reduction in the tension and centripetal force of the curved belt, and so we prototyped and tested a curved belt conveyor that employed a tension equalizing tapered roller 410, which had a sleeve-like projection on the outer periphery of the tension equalizing tapered roller. The curved belt here was a tension equalizing curved belt 420, designed in the same way as in Figure 5, a stretch curved belt without a core made of thermoplastic polyurethane, with a film thickness of approximately 1.2 mm and a mass of approximately 1.4 kg / m. 2 The stretch curved belt has uniform physical properties across its entire surface. The sleeve 430-1 is made of the same thermoplastic polyurethane material as the tension-leveling curved belt, has a width of approximately 50 mm, a thickness of approximately 1.2 mm, and is positioned approximately 50 mm from the outer edge of the tension-leveling tapered roller 410. As a result, tracking problems, such as meandering, which is thought to be due to the curved belt's deviation toward the inner periphery or deformation of the curved belt, did not occur. Because of the first-to-file principle, a long-term running test has not yet been conducted, making it difficult to compare with the curved belt conveyor 400 equipped with only the belt tension-leveling mechanism shown in Figure 5. However, the running conditions were more stable, and the effect of providing the convex portions was confirmed.

[0068] The results were analyzed using the same method as in FIG. 6, using a tapered roller 411 with a roller width of 600 mm, a small diameter of 40 mm, and a large diameter of 65 mm. The results are shown in FIG. 10. For comparison, FIGS. 10(a) and 10(b) are the same schematic cross-sectional views as FIGS. 6(a) and 6(c), respectively. FIG. 10(c) is a schematic cross-sectional view equivalent to FIGS. 10(a) and 10(b) when a sleeve 430-1 is attached to the tension-leveling tapered roller 411. Note that, as in the prototype, the sleeve 430-1 is attached so that its left end is located 50 mm from the outer peripheral end of the tension-leveling tapered roller 411.

[0069] 10(b) and (c), the angle θ3 (=0.023 rad) formed by two tangents to the maximum protrusion (left end of the sleeve 430-1) and the minimum protrusion (right end of the tension leveling tapered roller 411) on the outer surface of the tension leveling curved belt 420L that contacts the top and bottom of the tension leveling tapered roller 411 and the intersection 480L of these two tangents is symmetrical with respect to the center line of the tension leveling tapered roller 411. This is larger than the angle θ1 (=0.0208 rad) formed by the extensions of the two upper and lower generatrix lines at the center and the convergence point 460L where the extensions of the center line and generatrix lines of the tension-leveling tapered roller meet, and the angle θ2 (=0.0208 rad) formed by the extensions of the two generatrix lines at both ends of the outer surface of tension-leveling curved belt 420L that contacts tension-leveling tapered roller 411 and the intersection point 470L of these two extensions. Therefore, it is considered that the convex portions of the sleeve provided on tension-leveling tapered roller 410 not only have the effect of an inclined curved belt with a continuously changing film thickness as described in paragraphs 0062 to 0065, but also have the effect of preventing the curved belt from sliding toward the inner circumference by increasing the frictional force of the convex portions, thereby effectively preventing tracking problems of tension-leveling curved belt 410. Although it is not certain at this point, we have determined that the latter effect is greater, and as explained in the means for solving the problem, this convex portion is one means of an anti-slip mechanism that increases the contact force and friction force between the outer surface of the tension-equalizing tapered roller and the inner surface of the tension-equalizing curved belt, and also functions as a grip-enhancing convex portion in the embodiment of the present invention.

[0070] Furthermore, as an embodiment of a curved belt conveyor having the characteristics of the inclined curved belt conveyor described in paragraph 0065 using Figures 8 and 9, a curved belt conveyor was designed in which a tapered roller 411 having a roller width of 600 mm, a small diameter of 40 mm, and a large diameter of 65 mm is wound around the tapered roller 411, i.e., the center lines and extensions of the generatrix of all the tapered rollers converge to one convergent point, and a curved belt 421L having an inclined tension uniformity whose film thickness continuously changes from 2.0 mm to 1.25 mm, i.e., the length of the arc connecting the inner surfaces of both ends of the generatrix of the curved belt shaped like a side of a truncated cone shown in paragraph 0053 is reduced to about 98% of the length of the arc connecting the both ends of the generatrix of the radially arranged tapered rollers, and a schematic cross-sectional view similar to Figures 6 and 10 is shown in Figure 11.

[0071] In this case too, the intersection 490L of the extension lines of the two generatrix lines on the upper and lower outer surfaces of the tension-leveling curved belt 421L, whose film thickness is inclined, naturally coincides with the center line of the tension-leveling tapered roller 411 and the convergence point 460L where the generatrix lines meet, and the angle θ4 (=0.0221 rad) formed by the extension lines of the two generatrix lines on the upper and lower outer surfaces of the tension-leveling curved belt 421L, whose film thickness is inclined, and these intersection points 490L is larger than the angle θ1 (=0.0208 rad) formed by the two generatrix lines on the upper and lower outer surfaces of the tension-leveling tapered roller 411 and the center line of the tension-leveling tapered roller 411 and the convergence point 460L where the generatrix lines meet. Therefore, in this case, as with the case where sleeve 430-1 is provided, in addition to the effect of the inclined curved belt whose thickness changes continuously as described in paragraphs 0062 to 0065, since the outer periphery of inclined tension-leveling curved belt 421L is thick, the contraction force acting in the circumferential direction of concentric circles whose center is the intersection 490L of the extensions of the two generatrix lines of the upper and lower outer surfaces of tension-leveling curved belt 421L whose thickness is inclined increases. This increase in frictional force also prevents sliding of inclined tension-leveling curved belt 421L toward the inner periphery, thereby enhancing the tracking failure prevention effect of tension-leveling curved belt 421L. Although it is not clear at this point, we believe that the former effect is greater. As described in the Summary of the Invention, the inclined curved belt constitutes part of a belt tension-leveling mechanism and functions as a tension-leveling curved belt in the embodiment of the present invention.

[0072] From the above, when the film thickness of the curved belt is uniform, the belt tension equalization mechanism can be determined by the size and film thickness of the inner surface of the curved belt. However, when taking into consideration the tension and centripetal force of the curved belt, as well as the difference in contraction force due to the difference in film thickness of the curved belt, an inclined curved belt that becomes thinner from the outer periphery to the inner periphery of the curved belt is preferable.

[0073] The structure of the curved belt that can be applied to such a belt tension equalization mechanism is not particularly limited. As shown in Figure 12(a), a one-ply canvas core conveyor belt 420-1, a typical example of a commonly used resin conveyor belt, can be used. This conveyor belt has a structure in which a surface cover resin layer 421-1 and a back cover resin layer are laminated on a canvas core 422-1 made of polyester fiber or the like. The canvas core 422-1 is used to improve the strength and durability of the conveyor belt. However, the mechanical strength and anisotropy of the canvas core 422-1 can sometimes hinder the tension equalization of the curved belt. For this reason, a stretch conveyor belt, as shown in Figure 12(b), is more suitable as a curved belt. In particular, a coreless conveyor belt 420-2 made of thermoplastic polyurethane without a core is preferred. However, when durability is taken into consideration, a linear core conveyor belt 420-3 can be adopted in which linear cores 422-3 are arranged in the matrix resin 421-3 in the approximate rotation direction of the curved belt or in the tangential direction of the rotation circle. In this case, the matrix resin 421-3 is preferably thermoplastic polyurethane, and the linear cores 422-3 are preferably made of elastic urethane or nylon fibers or threads.

[0074] The anti-slip mechanism can be any mechanism, provided that the outer periphery of the tension-leveling tapered roller is provided with a convex portion. However, a sleeve is the simplest mechanism, and its overall shape, surface shape, and placement can be freely modified depending on the specifications of the curved belt conveyor, making it easy to handle. A smooth-surfaced sleeve, as shown in Figure 10(c), can be used as the smooth-surfaced grip-enhancing convex member 430-1. However, to further improve grip strength, i.e., anti-slip function, it is preferable to apply physical or chemical processing, such as grooves or lining, to the sleeve surface that comes into contact with the inner surface of the curved belt. Figure 13 shows an example of a grooved grip-enhancing member 430-2, which is a sleeve with longitudinal grooves 431-2.

[0075] The method for forming the protrusions as a sliding prevention mechanism and forming them into a grip-enhancing member varies depending on the type of tapered roller. As shown in Figure 14(a), in the case of a smooth-surface grip-enhancing protrusion member 430-1 such as that shown in Figure 10(c), it can be easily attached to a tapered pipe-type tapered roller 410-1 in which a tapered pipe 411-1 is attached to a shaft 412-1. Furthermore, such a sleeve-shaped smooth-surface grip 430-1 can also be similarly attached to a tapered adapter-type tapered roller 410-2 in which first to fourth tapered adapters 411-2 to 411-4 are attached to a roller 415-2 fixed to a shaft 416-2 as shown in Figure 14(b).

[0076] In the case of the tapered adapter type tapered roller 410-2, it is preferable that the grip-enhancing protrusions can be molded during the tapered adapter molding process. Figures 14(c) and 14(d) show examples of tapered rollers equipped with a grip-enhancing member to prevent slippage, using a third tapered adapter 418-2 with smooth-surface grip-enhancing protrusions and a third tape adapter 419-2 with diamond-cut grooved grip-enhancing protrusions, respectively.

[0077] The belt tension equalizing mechanism and the curved belt conveyor of the present invention equipped with the belt tension equalizing mechanism and anti-slip mechanism described above can be used as a single curved belt conveyor. However, by combining these as a unit, the range of possible uses for the conveying path is expanded. Figure 15 shows an example of a combined curved belt conveyor 500, which is a first curved belt conveyor 500-1 consisting of a first tension equalizing tapered roller 510-1 and a first tension equalizing curved belt 520-1 of the present invention, and a second curved belt conveyor 500-2 consisting of a second tension equalizing tapered roller 510-2 and a second tension equalizing curved belt 520-2 of the present invention. This combination not only allows for the construction of a highly flexible conveying path, but also reduces the number of tapered rollers per unit, thereby suppressing tracking problems in the curved belt. Furthermore, it is possible to install a curved belt conveyor in reverse or in conjunction with a straight conveyor, allowing the creation of a core transport route for logistics centers and various factories. [Industrial Applicability]

[0078] The curved belt conveyor of the present invention is a curved belt conveyor of simple configuration that does not have a belt holding mechanism, and can solve problems such as curved belt deviation, meandering, shortened lifespan, and damage. In addition, it has the effect of being able to use one curved belt conveyor of the present invention as a basic unit and to combine it with other conveyors, including straight conveyors, to create flexible transport routes. This makes it possible to create core transport routes in logistics centers and various factories, and therefore has extremely high industrial applicability.

[0079] Furthermore, the curved belt tension equalization technology of the present invention is believed to be effective in improving various rotary drive devices that use belts, and is believed to have extremely wide industrial applicability. [Explanation of symbols]

[0080] 100 Belt Conveyor 110 Conveyor Belt 120 head pulley 130 Tail pulley 140 Crown bend pulley 150 Concave bend pulley 200 Abstract curved belt conveyor to illustrate features 210 Tapered Roller 220 Curve Belt 230 Convergence point of center line and side of tapered roller 240 Convergence point of the curved belt side 300 Inclined Curved Belt Mounted Abstract Curved Belt Conveyor 310 Tapered roller (210) 320 Inclined Curve Belt 330 Inclined curve belt side convergence point (230) 400 curved belt conveyor 410 Tension equalizing tapered roller 410L Tension-equalizing tapered roller of specified dimensions 410-1 Tapered pipe type tapered roller 411-1 Tapered pipe 412-1 Shaft 413-1 Bearing 410-2 Tapered Adapter Type Tapered Roller 411-2 First Taper Adapter 412-2 Second taper adapter 413-2 3rd Taper Adapter 414-2 4th Taper Adapter 415-2 Laura 416-2 Shaft 417-2 Bearing 418-2 Third Taper Adapter with Smooth Surface and Grip-Enhancing Convex Section 419-2 Diamond-cut grooved third tape adapter with grip-enhancing protrusion 420 Tension-equalizing curved belt 420L Tension-equalizing curved belt of specified dimensions 421L Tension-equalizing Inclined Curve Belt of Predetermined Dimensions 420-1 1-ply canvas core conveyor belt 421-1 Surface cover resin layer 422-1 Canvas core 423-1 Back cover resin layer 420-2 Coreless conveyor belt 420-3 Linear core conveyor belt 421-3 Matrix resin 422-3 Linear core 430 Grip-strengthening convex member (sleeve) 430-1 Smooth surface, grip-strengthening convex part (sleeve) 430-2 Grooved grip-strengthening convex part (sleeve) 431-2 Vertical groove 440 Drive Belt 450 frames 460 Convergence point of center line and side of tension equalizing tapered roller 460L The center line and side convergence point of a tapered roller of a specified size 470 Tension equalization curve belt side convergence point 470L Tension-equalizing curved belt with specified dimensions, side convergence point 480L Tension-equalizing curved belt with specified dimensions equipped with grip-enhancing convex parts. Convergence point of tangents of the convex parts on the side. 490L Tension-equalizing inclined curve belt side convergence point 500 Combined Curved Belt Conveyor 500-1 First curved belt conveyor 510-1 First tension equalizing tapered roller 520-1 First tension equalizing curved belt 540-1 First drive belt 560-1 Convergence point of center line and side of first tapered roller 570-1 Convergence point of the first curved belt side 500-2 Second curved belt conveyor 510-2 Second tension equalizing tapered roller 520-2 Second tension equalizing curved belt 540-2 Second drive belt 550 frames 560 Convergence point of center line and side of tension equalizing tapered roller 570 Tension equalizing curved belt side convergence point Tension applied to T, T1 to T6 curved belt F, Centripetal force acting on curved belt F1~F3 r1~r3: Radius of rotation of the inner edge of the curved belt ω1, ω2 Angular velocity of curved belt v1~v3 Speed ​​of the inner edge of the curved belt t Curve belt film thickness θ1 is the angle formed by the convergence point of the center line of the tapered roller and the extension of the generatrix, and the generatrix with the center line of the tapered roller as the center of symmetry. θ2 to θ4: The angle formed by the convergence point of the extensions of the generatrix of the curved belt, with the center line of the tapered roller as the center of line symmetry, and these generatrix

Claims

1. A curved belt conveyor comprising a curved belt formed into the shape of a side surface of a substantially truncated cone and two or more rotatable tapered rollers arranged radially, wherein the inner surface of the curved belt contacts the outer surface of the tapered rollers, the curved belt is wound around the tapered rollers so as to bridge the tapered rollers, and the curved belt rotates as the tapered rollers rotate, a belt tension equalizing mechanism that applies a circumferential tension of a concentric circle having a center at the vertex where the generatrix of the curved belt intersects with the curved belt to the curved belt uniformly over the entire area of ​​the curved belt; A curved belt conveyor characterized in that the belt tension equalization mechanism controls the longitudinal movement of the center line of the curved belt within a predetermined range when the curved belt rotates, causing the curved belt to rotate along a predetermined trajectory.

2. The belt tension equalizing mechanism includes: a tension-leveling tapered roller, the tapered roller being arranged so that an extension line of all center lines of the tapered roller and an extension line of all generatrix lines of the tapered roller, which are in the same plane as a cutting surface passing through the center lines, converge to one point; a tension-equalizing curved belt in which the curved belt has a shape surrounded by an outer circumferential arc formed with a predetermined radius shorter than the outer circumferential end of the tapered roller, an inner circumferential arc formed with a predetermined radius longer than the inner circumferential end of the tapered roller, and outer generatrixes of the tapered rollers at both ends, with the convergence point as the center of the circle in a cross section of the curved belt conveyor cut on a horizontal plane, and in which the lengths of all arcs from the outer circumferential arc to the inner circumferential arc are a predetermined percentage selected from approximately 96 to 99%, and the inner surface of the side of an approximately truncated cone has a shape formed by arcs of lengths 2. The curved belt conveyor according to claim 1, wherein the curved belt conveyor comprises:

3. The belt tension equalizing mechanism further comprises:

3. The curved belt conveyor according to claim 2, wherein the tension-leveling curved belt is designed so that, in a cross section taken along a horizontal plane passing through the centerline of the curved belt conveyor, the angle formed by the extensions of two generatrix lines at both ends of the outer surface of the tension-leveling curved belt that contact the tension-leveling tapered rollers at both ends and the intersection of the two extensions is equal to or greater than the angle formed by the extensions of the two generatrix lines on the outside of the tension-leveling tapered rollers at both ends and the convergence point.

4. The belt tension equalizing mechanism further comprises:

3. The curved belt conveyor according to claim 2, wherein the tension-leveling curved belt is designed so that, in a cross section cut by a horizontal plane passing through the center line of the curved belt conveyor, the intersection of extensions of two generatrices at both ends of the outer surface of the tension-leveling curved belt that contact the tension-leveling tapered rollers at both ends coincides with the convergence point.

5. The tension-leveling tapered roller further includes a sliding prevention mechanism that increases the contact force and friction force with the inner surface of the tension-leveling curved belt, 3. The curved belt conveyor according to claim 2, wherein the anti-slip mechanism controls the longitudinal movement of the center line of the tension equalizing curved belt within a predetermined range when the tension equalizing curved belt rotates, so that the tension equalizing curved belt rotates along a predetermined orbit.

6. The curved belt conveyor according to claim 5, wherein the anti-slip mechanism is provided with grip-enhancing protrusions, which are physically or chemically treated to increase the contact force and friction force with the inner surface of the tension-equalizing curved belt, at a distance of approximately 0 to 50% from the end of the outer circumferential side of the tension-equalizing tapered roller.

7. 6. The curved belt conveyor according to claim 5, wherein the anti-slip mechanisms are provided on both ends of the radially arranged tension equalizing tapered rollers.

8. 7. The curved belt conveyor according to claim 6, wherein the anti-slip mechanisms are provided on both ends of the radially arranged tension equalizing tapered rollers.

9. 8. The curved belt conveyor according to claim 7, The tension-leveling curved belt of the belt tension-leveling mechanism is designed so that, in a cross section taken along a horizontal plane passing through the center line of the curved belt conveyor, the angle formed by two tangents to the maximum and minimum protrusions at both ends of the outer surface of the tension-leveling curved belt that contact the tension-leveling tapered rollers at both ends and the intersection of the two tangents is equal to or greater than the angle formed by extensions of the two outer generatrix lines of the tension-leveling tapered rollers at both ends and the convergence point.

10. 9. The curved belt conveyor according to claim 8, The tension equalizing curved belt of the belt tension equalizing mechanism is designed so that, in a cross section taken along a horizontal plane passing through the center line of the curved belt conveyor, two tangents to the maximum and minimum protrusions on both ends of the outer surface of the tension equalizing curved belt that contact the tension equalizing tapered rollers at both ends, and the intersection of the two tangents, coincide with the convergence point.

11. The tension-leveling curved belt has a thickness of about 0.7 to 2.6 mm and a mass of about 1.0 to 3.0 kg / m ２ 11. The curved belt conveyor according to claim 2, wherein the belt is made of thermoplastic polyurethane and does not have a core.

12. The tension-leveling curved belt has a thickness of about 0.7 to 2.6 mm and a mass of about 1.0 to 3.0 kg / m ２ The curved belt conveyor according to any one of claims 2 to 10, characterized in that the belt is made of thermoplastic polyurethane and the core body is a linear body made of resin arranged in the circumferential direction of the curved belt conveyor.

13. A curved belt conveyor comprising a plurality of curved belt conveyors according to any one of claims 1 to 10, radially arranged in succession so that the converging points coincide with each other and the intervals between the tapered roller conveyors are approximately equal to each other.

14. 12. A curved belt conveyor comprising a plurality of curved belt conveyors according to claim 11, radially connected together so that the converging points coincide with each other and the intervals between the tapered roller conveyors are approximately equal to the intervals between the tapered roller conveyors.

15. 13. A curved belt conveyor comprising a plurality of curved belt conveyors according to claim 12, radially connected together so that the converging points coincide with each other and the intervals between the tapered roller conveyors are substantially equal to the intervals between the tapered roller conveyors.

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