JP6577230B2 - Sorting device - Google Patents

Description

  The present invention relates to a switching device for a sorting conveyor, and in particular, when conveying a wide variety of objects to be conveyed, enables a stable conveyance at the same time as reducing the interval between rotating bodies for performing conveyance and direction change sorting. The present invention relates to a sorting apparatus having a structure.

  In the field of physical distribution, there are cases where articles with various shapes and sizes of objects to be transported are mixed and transported and sorted. When transported in the sorting direction by the rotating body of the sorting unit, the number of rotating bodies is generally large. As the interval is smaller and the rotation speed is more uniform, stable and reliable sorting becomes possible.

  Patent Document 1 discloses a sorting device using a rotating disk having a desired inclination angle, and Patent Document 2 discloses a plurality of specific configuration proposals in which a driving rotating body corresponding to the inclination propagates rotational force to the rotating disk. It is disclosed.

  Specifically, as a structure of a rotating body in which a disk rotates in Patent Document 2, a side surface of a cylindrical rotating driving body or a drum-shaped driving rotating body having a small outer diameter at a central portion and a large outer diameter at both ends and a rotating disk There are three main examples: the same structure as in Patent Document 1 in which the outer peripheral flat surface abuts, the structure via a pulley, and the drive rotating body having the same inclination that presses against the inclined surface as in this proposal. .

  Here, in the first structure, the pressure contact surface is perpendicular to the rotation axis and a pressure contact force is applied in the surface direction of the rotating disk, and the second structure can transmit the rotation even if it has a slight angle, and the pulley By selecting the diameter of the rotating part, it is easy to obtain a large torque force, and unlike the former two, the third structure does not use a pulley and propagates the force by pressure contact with the driving rotating body with the same inclination angle Therefore, the force is applied only to a part of the outer periphery of the inclined disk.

Japanese Patent Laid-Open No. 4-115820 Japanese Utility Model Publication No. 5-26921

  However, in the sorting device structure using these rotating disks, it is necessary to increase the number of rotating disks and reduce the interval in order to reliably sort various objects to be conveyed including large and small sizes. Along with this, the number of drive units for driving the rotating disk needs to be increased, and at the same time, it is necessary to reduce the size of the rotary disk. In addition, the burden of initial cost and operation cost increases including the complexity of maintenance and inspection.

  In order to solve these problems, it is possible to increase the density by providing rotating disks on both sides of the drive unit that is driven to rotate, and the structure as described in the cited document is effective. In the conventional structure in that case, it is possible to rotationally drive two annular rotators by one rotational drive body by adopting a symmetrical structure before and after the axial direction of the rotational drive body. Since a force in the reverse direction is applied to the position where the two annular rotators are pressed against the body at a position 180 degrees opposite to the radial direction, a large moment is generated in the shaft fixing portion of the rotary drive body. Furthermore, a moment due to the repulsive force is also generated in the annular rotating body. For these, consideration must be given to dealing with parts wear, metal fatigue, etc., and it is also necessary to consider structural reinforcement.

  Further, in the conventional structure, in order to increase the height position of the maximum outer periphery of the rotating disk, it is desirable that the center of rotation when the rotating disk is tilted is offset from the center rather than being positioned at the center of the disk. However, when the rotary drive has a symmetrical structure with respect to the front and rear in the axial direction, the length of the radius of the press contact position in the rotary disk differs by increasing the deviation of the center position.

  When two rotary bodies are rotationally driven by one rotary drive body, the rotational speed or the rotational speed of the rotary body that is slidably rotated by the rotary drive body varies according to the ratio of the radii of the press contact positions. In general, in the case of rotational propagation due to friction, the combination of friction and slip will stabilize within a certain range, but when the rotational speed increases, the absolute speed and rotational speed depend on the size of the object to be conveyed. A large difference in numerical values. In particular, an unstable movement such as rotation of a small and lightweight conveyance object occurs.

  In order to solve the above-described problems, the present invention has a structure in which two rotating bodies are rotated by a set of rotary driving bodies including a power source. In addition, an external force such as an unnecessary moment is not applied to the rotating disk, and at the same time The challenge is to provide a sorting device that can achieve uniform and smooth rotation while at the same time ensuring operating life by reducing the difference in radii, increasing the operating rate, and greatly reducing maintenance and inspection costs and material costs. It was.

  In order to solve problems such as economy and life among such problems, the present invention provides a belt drive mechanism including a power source by simultaneously rotating two annular rotators before and after the axial direction of the drive rotator. The structure reduces the number.

  Furthermore, with respect to the unnecessary moment generated by combining a symmetric drive rotor and two rotors, and the above-described problem relating to different rotational speeds, the rotary driver that is supported rotatably on a shaft, and A rotary drive body is formed by integrating a disk body so as to form a predetermined angle from the axis of the first fixed shaft that is elastically fixed to one side of the rotary drive body with respect to the axial direction of the shaft. (1) An inner diameter side of a first annular rotating body, which is disposed on an inclined portion so as to be freely rotatable via a sliding contact mechanism and whose outer peripheral portion is formed in an annular shape, extends and protrudes at a predetermined angle of the rotational driving body. A disc body is integrated so as to form a predetermined angle from an axis of a second fixed shaft that is in pressure contact with the inclined outer peripheral portion and is elastically fixed to the other side of the rotary drive body with respect to the axial direction of the shaft. In sliding contact with the second inclined portion of the rotary drive body to be formed When the side surface side of the second annular rotator is in contact with the outer peripheral portion having a predetermined angle of the rotary drive body, the rotary drive body performs a predetermined rotation by being arranged so as to be freely rotatable through the structure. The structure has a function of propagating the rotational force to the first annular rotator and the second annular rotator by the frictional force at the press contact location.

  That is, in the present invention, by utilizing the inclination of the annular rotator, one is brought into sliding contact with the inner surface of the annular rotator substantially perpendicular to the inclination of the annular rotator, and the other is brought into sliding contact with the inclined outer portion of the annular rotator. By adopting a structure, the pressing force applied to the two annular rotating bodies can be reduced by pressing one side in the axial direction and pressing the other without pressing as if sandwiched from the front and back surfaces of the rotary driving body. Since the pressure is directed in the same direction with respect to the rotary drive body, the moment as described above does not occur, and the ratio of the radial position where the rotational transfer drive body touches and the radial position where the inclined annular rotary body touches is made substantially constant. Thus, the difference in rotational speed can be eliminated or reduced.

  In order to transmit an efficient and reliable rotational force to the rotary disks provided on both sides of the drive unit, any one of the three components of the rotary drive body and the two annular rotary bodies installed on both sides The component member is fixed in the axial direction of the shaft, and has a pressing method in which a force is always applied to the pressure contact surface that propagates the rotational force by the rotary drive body, and is slid on at least one of the surfaces that are in sliding contact with each other. A reliable and stable rotational propagation force can be obtained by providing means for enhancing the frictional force at the time of contact.

  In addition, by forming one or more slits in the first inclined portion of the rotary drive body that is expanded in the shape of a conical cylinder, a force acts in the direction in which the diameter increases due to the centrifugal force associated with the rotation of the rotary drive body. Therefore, it is possible to obtain a larger force than the rotational propagation force at the time of sliding contact can be obtained only by the frictional force.

  Incidentally, at least one of the sliding contact surfaces of the drive rotating body and the annular rotating body and the area in contact with the object to be conveyed are made of engineering plastics such as polyacetal resin and polyurethane resin, for example, by frictional force and elastic force. It is possible to obtain a reliable rotational force propagation utilizing the effect and a buffering effect on the conveyance object.

  As a result, the structure of the switching device of the sorting conveyor is simplified, the number of annular rotating bodies can be increased, the gap between the rotating bodies can be reduced, and at the same time, smooth rotation can be obtained and the internal stress of the structure can be reduced. By reducing the cost, it is possible to reduce the cost of maintenance and inspection.

It is a top view of the principal part of the conveying apparatus explaining arrangement | positioning and an effect | action of a sorting apparatus. It is a block diagram which shows the positional relationship of the height direction in the inclination of a conveyance conveyor part and a rotary body. It is a figure which shows the relationship between the external force and moment in the rotary drive body in a conventional structure, and two rotary bodies. It is a figure which shows the magnitude | size of the radius from the rotation center of the press load part between each member in the rotation drive body in a conventional structure, and two rotation bodies. It is a figure showing the locus | trajectory of the axis | shaft of the inclination rotation center of a rotary body, and the maximum height position in case the rotation center of an inclination exists in the center of a rotary body disc thickness direction. It is a figure showing the locus | trajectory of the axis | shaft of the inclination rotation center of a rotary body, and the maximum height position in case the rotation center of an inclination deviates from the center of a rotary body disk thickness direction. It is a structural diagram showing the relationship between the rotary drive and the rotary body according to the embodiment of the present invention. It is a schematic diagram which shows the pressing force and moment in a rotary drive body and rotary body which concern on embodiment of this invention. It is a schematic diagram which shows the positional relationship regarding the radial direction of the rotation drive body which concerns on embodiment of this invention, and the press part of a rotary body. Is a schematic view showing a pressure contact force at the sliding contact portion of the first rotating body and the rotating driving member according to an embodiment of the present invention, the component force of the N ₂₁ in the structure shown in FIG. 7 according to the directly to the frictional force . Is a schematic view showing a pressure contact force at the sliding contact portion of the second rotary member and the rotary driving member according to an embodiment of the present invention, the component force of the N ₂₂ in the structure shown in FIG. 7 according to the directly to the frictional force . It is a block diagram which shows an example of the installation position of the spring elastic structure of the axial direction which concerns on embodiment of this invention. It is a block diagram which shows the other example of the installation position of the spring elastic structure body of the axial direction which concerns on embodiment of this invention. It is a block diagram which shows the other example of the installation position of the spring elastic structure body of the axial direction which concerns on embodiment of this invention. It is a combination chart which shows the combination of the position and direction which fixes or presses a component. It is the perspective view and side view which show the basic structure of the rotary drive body which concerns on embodiment of this invention. In the rotary drive body which concerns on embodiment of this invention, it is the perspective view and side view which show the shape which provided the slit in the area | region press-contacted to a cyclic | annular rotary body.

  Hereinafter, a sorting device according to an embodiment of the present invention will be described with reference to the drawings. In the following, the range necessary for the description for achieving the object of the present invention is schematically shown, and the range necessary for the description of the relevant part of the present invention will be mainly described. According to a known technique.

  FIG. 1 is a diagram schematically showing a state in which a conveyance object 82 is sorted in the vertical direction (A) and the sorting direction (B or C) in the transport device 8 to which the sorting device 81 according to the present invention is applied. .

FIG. 2 is a diagram illustrating a conveyor belt 6 and a sorting device according to an embodiment of the present invention, in which the contact sliding position between the rotating body 1 and the rotation driving body 4 changes between two conveyor belts 6. This shows the situation where the height position at () is shown (only the right side is shown here). The maximum height at which the height position of the maximum outer peripheral portion of the rotating body 1 changes in accordance with the rotation of the rotary drive body 4 fixed to the shaft 2 and the fixed portion 3 having the inclined portion is indicated by broken line arrows. Its height is the effective area of the height protruding to have regions D2 is the height direction from the position of the conveyor 6 for transport, two positions of W1 region which is located inside the gap W between the conveyor width It becomes the effective area of the direction.

FIG. 3 is a specific example in which the rotary body 1 is duplicated with the rotary drive body 4 based on the conventional structure. When the axial pressing forces (F ₁ , F ₂ ) are applied to the fixed portion 3, the rotations are respectively rotated. contact pressure at a portion where the body 1 comes into sliding contact _{(N 11, N 22)} by the rotary drive member 4 occurs moment _{(M 3),} each _{M 1} is the first and second rotary bodies (11, 12) And M ₂ moments are generated. Since this moment is always applied as a load while rotating, metal fatigue or the like due to repetitive load can be considered in long-time operation. Incidentally, N ₂₁ and N ₁₂ shown in the figure are expressed as reaction forces of the pressure contact forces (N ₁₁ , N ₂₂ ).

FIG. 4 is a specific example in the state of FIG. 3, and the radius (r ₁ , r ₂ ) from the center of the shaft 2 at the portion where the rotary drive body 4 and the rotary body 1 are in sliding contact with each other, The radii (s ₁ , s ₂ ) from the center of rotation to the point of sliding contact are shown. Here, the position of the sliding contact portion in the rotary drive body is r ₁ = r ₂ , but the position of the rotation center O where the rotary body 1 is inclined with respect to the fixed portion 3 is the thickness t ₁ of the rotary body. On the other hand, when the relationship is t ₂ > t ₃ , the radius to the sliding contact portion of the first and second rotating bodies 1 is s ₁ > s ₂ . That is, the number of rotations or the rotation speed of the first and second annular rotators causes a difference corresponding to the ratio of s ₁ and s ₂ .

FIG. 5 a shows a case where the position of the inclined rotation center O in the rotating body 1 according to the embodiment of the present invention has a relationship of t2 = t3 with respect to the thickness t1 of the rotating body 1. Incidentally, the state in which the rotating body 1 is in sliding contact with the rotational drive body 4 is indicated by three positions x, y, and z with which the rotating body 1 comes into contact. The rotating body 1 is a horizontal sectional view passing through the rotation center O. For y , the contact state with the rotary drive 4 is not shown. Here, the distance from the position of the shaft 2 is increased and the distance from the position of the shaft 2 is increased from the position X at which the conveyance object is in contact at the inclined position x of the rotating body 1 indicated by the solid line in FIG. A trajectory XYZ from a point Y to a point Z at a height at which the conveyance object comes into contact at a position z indicated by a one-dot chain line in the drawing is indicated by a thick broken line.

Here, regarding the position of the rotation center O in the rotating body 1, when t ₂ = t ₃ , the position of the rotating body in contact with the object to be conveyed is the diagonal radial position L ₁ at the inclined position x indicated by the solid line in the figure. The position of the contact point X in the height direction gradually increases, reaches the maximum value (position Y) in the state of the position y in the vertical direction in the figure, and further rotates, thereby the inclination indicated by the alternate long and short dash line in the figure The position moves to the contact point at the radial position L ₂ at the position z. Since L ₁ = L ₂ , the height difference is the difference between the Y point and the X and Z points, which is a value indicated by H ₁ .

On the other hand, FIG. 5b shows a case where t ₂ > t ₃ in relation to the position of the rotation center O in the rotator 1 unlike the case (a). In this case as well, from the point X where the conveyance object is in contact at the inclined position x of the rotating body 1 indicated by the solid line in the figure, through the maximum height Y point at the inclined position y, at the inclined position z indicated by the one-dot chain line in the figure. The locus XYZ up to the contact point Z is indicated by a thick broken line.

Here, when t2 ≠ t3, the relationship is different from the above. For example, when t2> t3, relationships r1> r2 and L3> L4 occur. As shown in FIG. 4, in the case of the structure in which the rotary body 1 is duplicated with the rotary drive body 4, the rotational speeds or rotational speeds of the two rotary bodies are different. However, the height difference H2 with respect to the conveyance object here is larger than the above-mentioned H1. The figure here, the height difference conveyor while it becomes possible to have stable and changing the conveying direction of the conveying object by a large rotational speed indicates a conflict with a different.

FIG. 6 is a structural diagram showing the relationship between the rotary drive body 4 and the rotary bodies 11 and 12 according to the embodiment of the present invention, and the inner diameter side of the annular portion of the first rotary body 11 and the second rotary body 12. The rotary drive body 41 which is in sliding contact with the outer side surface portion at the same time is shown. The first annular rotating body 111, via a sliding contact mechanism 7 in a first predetermined relative to the fixed shaft 311 of the tilt angle (theta) inclined disc 312 which is fixed with a integrally fixed to the shaft 2 Te freely rotatable, the second annular rotating body sliding on the inclined disc 322 relative to the second fixed shaft 321 is integrally fixed to the shaft 2 which is fixed with a predetermined angle (theta) The rotary drive body 42 is configured to be freely rotatable via the contact mechanism 7, and one of the rotational drive bodies 42 is in sliding contact with the inner diameter portion of the first annular rotary body 111, and the other is on the outer peripheral side surface portion of the second annular rotary body 121. A structure having a function of propagating rotational force in sliding contact is shown.

FIG. 7 shows the pressing force in the rotary drive body 4 and the rotary bodies 11 and 12 according to the embodiment of the present invention, and the first and second rotary bodies 11 and 12 having a predetermined inclination angle (θ) and the drive. The force with which the rotating body 4 is in sliding contact is the force F1 that directs the first rotating body 11 in the right direction in the figure and the force F2 that directs the second rotating body 12 in the right direction in the figure with respect to the rotational drive body 4. In other words , it indicates that it faces the same direction as the press contact forces N21 and N22. As a result, a large moment (M3 in FIG. 3) as in FIG. 3 does not occur. Incidentally, the moment generated here is only the moment generated by the difference between the two slidable radii (r3-r4).

For example, assuming the moment M in FIG. 3, F ₁ × r ₁ and F ₂ × r ₂ are combined, and F ₁ = F ₂ , so that M = F (r ₁ + r ₂ ). . On the other hand, in FIG. 7, since M = F (r ₃ −r ₄ ), ideally, if r ₃ = r ₄ , no moment is generated, but even if there is a difference between the two, the conventional structure is obtained. In comparison, a significant reduction is achieved.

FIG. 8 shows the positional relationship in the radial direction of the pressing portions of the rotary drive body 4 and the rotary bodies 11 and 12 according to the embodiment of the present invention, and in the first rotary body 11 having a predetermined inclination angle (θ). The first inclined portion 41 of the rotary drive body 4 is in sliding contact with the position of the rotation radius r _{3 at} the position of the radius s ₃ corresponding to the inner diameter portion of the rotation body 11. The outer peripheral side surface is in sliding contact with the second inclined portion 42 of the rotary drive body 4 at the position of the rotation radius s ₄ of the rotary body 12. Here, when the position of the rotation center in the rotating body 1 is in the positional relationship shown in FIG. 5B, r ₃ > r ₄ in the rotation driving body 4 and s ₃ > in the rotating bodies 11 and 12. s ₄ relationship. Further, the rotational speed or the rotational speed is the same if the ratio of the radius (r) of the rotary drive body 4 and the radius (s) of the rotary bodies 11 and 12 is constant. Realistically, the effect increases if the ratio is made as close as possible.

FIG. 9 is a diagram in which a pressure contact force N ₂₁ is applied at a location where the first rotating body 11 and the rotational driving body 4 are in sliding contact, and the actual rotational force depends on the friction coefficient (μ) depending on the material and shape of the contact, μ It rotates by receiving the force of × N ₂₁ sinθ.

FIG. 10 is a diagram in which a pressure contact force N ₂₂ is applied at a location where the second rotary body 12 and the rotary drive body 4 are in sliding contact, and the actual rotational force depends on the effect of the friction coefficient (μ) depending on the material and shape of contact. It rotates by receiving the force of × N ₂₂ cos θ.

FIG. 11 is a diagram showing an example of the installation position of the axial pressing elastic structure according to the embodiment of the present invention. In this example, the rotational driving body 4 is fixed to the shaft 2 by the fixing mechanism 5 in the axial direction. is there. At the same time as fixing the rotary drive body 4 in the axial direction, an elastic structure such as a compression spring is mounted on both the first fixed shaft 31 and the rotary drive body 4 so as to be repelled by the force of F ′. The pressing force N ₂₁ and N ₂₂ shown in FIGS. 9 and 10 can be stably obtained by attaching a pressing structure that applies the pressing force F to the rotary drive body 4 to the shaft 32.

FIG. 12 is a view showing an example of the installation position of the axial pressing elastic structure according to the embodiment of the present invention. When the first rotating body 11 is fixed to the shaft 2 in the axial direction by the fixing mechanism 5. It is an example. At the same time that the first fixed shaft 31 is fixed in the axial direction, an elastic structure such as a compression spring is attached to both the first fixed shaft 31 and the rotary drive body 4 so as to repel each other by the force of F ′. The pressing force N ₂₁ and N ₂₂ shown in FIGS. 9 and 10 can be stably obtained by attaching a pressing structure for applying the pressing force F to the rotary drive body 4 to the fixed shaft 32.

FIG. 13 is a view showing an example of the installation position of the axial pressing elastic structure according to the embodiment of the present invention, and the second fixing shaft 32 is fixed to the shaft 2 by the fixing mechanism 5 in the axial direction. It is an example. At the same time as fixing the second fixed shaft 32 in the axial direction, both the first fixed shaft 31 and the rotary driving body 4 are mounted with an elastic structure such as a compression spring so as to repel each other by the force F ′. The pressure contact forces N ₂₁ and N ₂₂ shown in FIGS. 9 and 10 are stably obtained by attaching a pressing structure that applies a pressure contact force F in the direction in which the rotary drive body 4 is positioned to one fixed shaft 31. It is done.

  FIG. 14 is a table showing the form including the contents shown in FIGS. 11 to 13, and the rotary drive body 4 and the first rotary body 11 and the second rotary body 12 that are in contact at both ends thereof are arranged on the horizontal axis. A portion to be fixed in the axial direction with respect to 2 is drawn on the vertical axis, and the fixing portion and the pressing direction of the elastic structure are indicated by arrows including one direction or both directions.

  FIG. 15 shows the basic structure of the rotary drive body 4 according to the embodiment of the present invention. One rotary body has a protruding inclined portion 41 for contacting the inner diameter portion of the inclined annular rotary body. For the other rotating body, a structure having an inclined portion 42 for contacting the outer shape portion of the inclined annular rotating body is shown.

  FIG. 16 shows a structure in which one or a plurality of slits 43 in the axial direction are provided in the region of the inclined portion 41 protruding from the rotary drive body 4 in FIG. By having this slit, a centrifugal force generated by the rotation of the rotary drive body 4, that is, a force in the outer diameter direction acts on the inclined portion, so that sliding friction is increased, so that a reliable rotational force is transmitted. Will be. In particular, in the case of sliding between inclined surfaces by a rigid structure, complete contact with the entire outer peripheral surface is difficult if the inclination angles do not match slightly, and there is a possibility of linear contact in a narrow area on the outer periphery. Since the inclined portion 41 is easily elastically deformed by the centrifugal force, the contact on a wide surface is possible.

  The transport device according to the present invention is used in many different forms of usage in various places in physical distribution. In particular, in order to reliably transport a large to small transport object, For this reason, it is necessary to make the rotation interval of the rotary plates as small as possible and at the same time make the rotation speeds of the plurality of rotary plates as uniform as possible. Further, by adopting a structure in which an excessive force is not applied to the rotating structure, it is possible to reduce the frequency of failure and to reduce the operation cost associated with maintenance and inspection. In various industries to which the transfer device is applied, it is possible to increase the utility value by improving the transfer efficiency and reducing the device cost.

DESCRIPTION OF SYMBOLS 1 Rotating body 11, 12 1st and 2nd rotating body 111, 121 1st and 2nd cyclic | annular rotating body 1a, 1b, 1c The inclination of a rotating body is one maximum state, when there is no inclination, and an inclination is the other 2 Shaft 3 Fixed portion 31, 32 First and second fixed portions 311, 321 Fixed shafts of first and second rotating bodies fixed to the shaft 312, 322 First and second rotating bodies fixed Inclined disks 331, 332 that hold the first and second fixing parts 4 Rotation drive body 41 First inclination part of rotation drive body 42 Second inclination part of rotation drive body 43 Slit 5 Fixing mechanism for holding the fixed part of the rotating disk in the axial direction 6 Conveying part 7 Conveying mechanism 8 Conveying device 81 Direction changing part 82 Object to be conveyed A, B, C Conveying direction D ₁ Conveyor thickness D ₂ Conveyor Area where the rotating body protrudes from the surface of the part (effective area)
F Force applied by fixing or external force F ₁ , F ₂ Force applied to fixed shafts of first and second rotating bodies H ₁ , H ₂ Difference between highest position and lowest position L ₁ , L ₂ , L ₃ , L ₄ Distance which becomes maximum height at P position and R position M ₁ , M ₂ , M ₃ , M ₄ , M ₅ Moment applied to each part N ₁₁ , N ₂₁ , N ₂₁ , N ₂₂ External force applied to each rotating body Reaction (external force on the rotating drive)
O Rotation center where the rotator is inclined with respect to the fixed part r ₁ , r ₂ , r ₃ , r ₄ Magnitude of contact radius when the rotary drive body contacts the rotator s ₁ , s ₂ , s ₃ , s ₄ The size of the contact radius when the inclined body that is inclined is rotated by the rotary drive body The thicknesses of the t ₁ , t ₂ , and t ₃ rotating bodies and the thickness to the center of the inclined rotation W ₁ The gap between the two conveyors W ₂ region rotator from the conveyor surface is projected (effective area)
X, Y, Z Each position (height) in the state of x, y, z in the locus of the maximum height position from the conveyor surface when the rotating body is inclined
Angle of fixed inclined plate and annular rotating body with respect to θ shaft

Claims (4)

A shaft installed at a position substantially orthogonal to a transport direction in which a transport target is placed and transported on a transport path surface;
A rotary driving body that is pivotally supported by the shaft so as to be freely rotatable, and has a first outer peripheral portion that is extended to have a predetermined angle on one side and a predetermined angle on the other side. A rotary drive body having a formed second outer peripheral portion ;
First a first disk body which is fixed prior to SL to form a first fixed shaft or al a predetermined angle which is elastically fixed with respect to the axial direction of the shaft Ru is freely rotatably arranged via a sliding mechanism 1 annular rotor ,
The Ru is freely rotatably arranged via a sliding contact mechanism in a second disk body which is fixed prior to SL to form a second fixed shaft or al a predetermined angle which is elastically fixed with respect to the axial direction of the shaft Two annular rotators;
Wherein the first outer peripheral portion of the rotary drive member is pressed against the inner diameter of the first annular rotating body, the second outer peripheral portion of the rotary drive member is pressed against the outer peripheral side surface of the second annular rotating body it is, by the rotational drive member performs a predetermined rotation, the rotation force and a function to be propagated the the first annular rotating body and the second annular rotating member by frictional force in the pressure contact portion Sorting device characterized by that. Wherein the rotary drive member, any one place of the components of said first annular rotating body and the second annular rotating body is fixed with respect to the axial direction of the shaft, rotation by the rotational drive member always sorting apparatus according to claim 1, further comprising a force is applied pressurized圧手stage pressing surface to propagate the force. 2. The sorting apparatus according to claim 1, further comprising means for strengthening a frictional force during pressure contact on at least one of the pressure contact surface of the first annular rotator and the pressure contact surface of the second annular rotator. Wherein the first outer peripheral portion of the rotary drive member is extended in a conical tubular shape, wherein the first outer peripheral portion one place or a plurality of slits are provided, sorting apparatus according to claim 1.

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