CONTINUOUS UNLOADER, CONTINUOUS UNLOADER FACILITY, AND CONTINUOUS UNLOADER OPERATION METHOD

A continuous unloader (1) is a bucket elevator-type continuous unloader provided with a bucket elevator (9) that continuously transports bulk cargo (M), wherein the bucket elevator (9) comprises a plurality of buckets (27) that scoop and load the bulk cargo (M), an endless chain (25) to which the plurality of buckets (27) are mounted, a driving roller (31a) for driving and circulating the endless chain (25), and a turning roller (33) to guide the endless chain (25) and to change the direction of travel of the endless chain (25). The maximum speed for the circulating motion of the endless chain (25) during operation is 90 to 150 m/minute.

TECHNICAL FIELD

The present invention relates to a continuous unloader of a bucket elevator type, a continuous unloader facility and a method of operating a continuous unloader.

BACKGROUND ART

Conventionally, a bucket elevator described in the following Patent Document 1 is known as a technique in such a field. This bucket elevator has a chain bucket that moves endlessly within the elevator post (elevator body) and revolves. This chain bucket has two chains circling by a plurality of drive rollers and a large number of buckets attached so as to hang between the two chains. In the lower part of the bucket elevator, a large number of orbiting buckets scrape the bulk and load it, so that the bulk can be conveyed continuously.

Japanese Unexamined Patent Publication No. 2001-253547

This type of bucket elevator type continuous unloader is required to improve cargo handling capacity. In the continuous unloader of the bucket elevator type, its size is related to cargo handling ability, so that it is possible to enlarge the continuous unloader to improve cargo handling capacity. However, since the size of the continuous unloader is closely related to the manufacturing cost, there is a problem that an improvement in cargo handling capacity due to an increase in size leads to an increase in the manufacturing cost of the continuous unloader.

SUMMARY

In view of this problem, it is an object of the present invention to provide a continuous unloader, a continuous unloader facility, and an operation method of a continuous unloader, which can improve cargo handling ability while suppressing an increase in manufacturing cost.

In the continuous unloader of the present invention,

A bucket elevator type continuous unloader having a bucket elevator for continuously conveying an object,

The bucket elevator,

A plurality of buckets for scraping and stacking the objects,

An endless chain to which the plurality of buckets are attached,

A driving roller for driving and circulating the endless chain,

And a deflecting roller that guides the endless chain and converts a traveling direction of the endless chain,

Characterized in that the maximum speed of the circulating movement of the endless chain at the time of operation is 90 to 150 m / min.

According to this continuous unloader, by setting the maximum speed of the circulating movement of the endless chain to 90 to 150 m / min, it is possible to improve the cargo handling ability while suppressing upsizing of the continuous unloader.

Also, the maximum speed may be 95 to 150 m / min.

Also, the maximum speed may be 100 to 150 m / min.

Also, the maximum speed may be 100 to 120 m / min.

The vibration acceleration generated by the bucket elevator at the time of operation may be 6 G or less.

The continuous unloader facility of the present invention is characterized by comprising a quay wall and any one of the continuous unloaders described above provided on the quay wall. Since this continuous unloader facility can improve the cargo handling ability while suppressing the increase in the size of the continuous unloader, the demand strength of the quay supporting the continuous unloader can also be suppressed. Therefore, it is possible to improve the cargo carrying capacity while suppressing the manufacturing cost including the continuous unloader and the quay.

In the operation method of the continuous unloader of the present invention,

A bucket elevator type continuous unloader having a bucket elevator for continuously conveying an object,

The bucket elevator,

A plurality of buckets for scraping and stacking the objects,

An endless chain to which the plurality of buckets are attached,

A driving roller for driving and circulating the endless chain,

And a deflecting roller that guides the endless chain and converts a traveling direction of the endless chain,

And circulating the endless chain at a speed of 90 to 150 m / min.

According to this operation method, by setting the speed of the circulating movement of the endless chain to 90 to 150 m / min, it is possible to improve the cargo handling ability while suppressing the increase in the size of the continuous unloader.

According to the present invention, it is possible to provide a continuous unloader, a continuous unloader facility, and an operation method of a continuous unloader, which can improve cargo handling ability while suppressing an increase in manufacturing cost.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a view showing a continuous unloader and a continuous unloader facility according to an embodiment of the present invention.

FIG. 2 is a plan view showing the continuous unloader facility of FIG. 1.

FIG. 3 is a partially broken perspective view showing the bucket elevator upper portion of the continuous unloader of FIG. 1.

FIG.4(A) is a side view of the diverting roller and (b) is a sectional view showing a supporting structure of the diverting roller.

FIG. 5(A) is a cross-sectional view showing another example of the deflecting roller, (B) is a side view showing still another example of the diverting roller, and (C) is a sectional view thereof.

FIG. 6 is a cross-sectional view showing an example of a support structure for supporting a fixed shaft in a rotation axis direction.

FIG.7(A) to (C) are side views showing another example of the deflecting roller.

FIG. 8 is a cross-sectional view showing an example of a support structure for supporting a fixed shaft in a rotation axis direction.

FIG. 9 is a cross-sectional view showing another example of a support structure for supporting a fixed shaft in a rotation axis direction.

FIG. 10 is a cross-sectional view showing still another example of the support structure for supporting the fixed shaft in the rotation axis direction.

FIG. 11 is a cross-sectional view showing still another example of the support structure for supporting the fixed shaft in the rotation axis direction.

FIG.12(A) is a side view of a deflecting roller used in the simulation, (Bb) is a supporting structure of a deflecting roller in a model M1, and (C) is a supporting structure of a deflecting roller in a model M2.

FIG.13 is a graph showing the acceleration of the deflection roller of the simulation result.

FIG.14 is a graph showing the displacement of the deflection roller of the simulation result.

FIG.15 is a graph showing the acceleration of the deflection roller of the simulation result.

FIG.16 is a graph showing the displacement of the deflection roller of the simulation result.

DETAILED DESCRIPTION

Hereinafter, embodiments of the continuous unloader, the continuous unloader facility, and the continuous unloader operating method according to the present invention will be described in detail with reference to the drawings.

The continuous unloader facility 200 shown in FIG. 1 and FIG. 2 includes a quay wall 101 and a continuous unloader 1 provided on the quay wall 101. The quay wall 101 is constructed of, for example, reinforced concrete, and the quay wall 101 has a predetermined strength for supporting the continuous unloader 1. As will be described later, the continuous unloader 1 is movable on the rail 3 a, and here, a portion constructed to have a predetermined strength corresponding to the movement range of the continuous unloader 1 is referred to as a quay wall 101. In this unloader facility 200, the ship 102 is brought into parallel with the shore wall 101, and unloading from the ship 102 is executed by the continuous unloader 1.

A bucket elevator type continuous ship unloader (CSU) 1 shown in FIGS. 1 to 3 is a device for continuously discharging a bulk M (for example, coal, coke, ore, etc.) from a hold 103 of a ship. The continuous unloader 1 is provided with a traveling frame 2 which is movable along the quay wall 101 by two rails 3 a laid in parallel on the quay wall 101. A swivel frame 5 is supported so as to be swingable on the traveling frame 3, and a bucket elevator 9 is supported at a tip portion of a boom 7 protruding in a transverse direction from the revolving frame 5. The bucket elevator 9 is held vertically regardless of the up-and-down angle of the boom 7 by the parallel link 8, the balancing lever 12 and the counterweight 13.

The continuous unloader 1 is equipped with a cylinder 15 for regulating the angle of rise of the boom 7. When the cylinder 15 is extended, the distal end side of the boom 7 is raised so that the bucket elevator 9 is raised. When the cylinder 15 is contracted, the distal end side of the boom 7 faces downward and the bucket elevator 9 is lowered.

The bucket elevator 9 continuously digs and scrapes the bulk M in the hold 103 by the scraping portion 11 of the side excavation type provided in the lower portion of the bucket elevator 9 and conveys the scraped bulk M upward .

The bucket elevator 9 includes a tubular elevator main body 23 extending in the vertical direction and a chain bucket 29 rotating around the elevator main body 23. The chain bucket 29 includes a pair of roller chains (endless chain) 25 connected in an endless manner and a plurality of buckets 27 supported at both ends by the pair of chains 25. Specifically, the two chains 25 are juxtaposed in a direction orthogonal to the paper surface of FIG. 1, and each bucket 27 is suspended between two chains 25 as shown in FIG. 3 So as to be attached to the chain 25, 25 via a predetermined attachment tool.

Further, the bucket elevator 9 includes a drive roller 31 a on which the chain 25 is laid, driven rollers 31 b, 31 c for guiding the chain 25, and a deflection roller 33 for guiding the chain 25. The driven roller 31 a is provided at the uppermost part 9 a of the bucket elevator 9, the driven roller 31 b is provided at the front portion of the scraping portion 11, and the driven roller 31 c is provided at the rear portion of the scraping portion 11. The deflecting roller 33 is a driven roller located slightly below the driving roller 31 a, and guides the chain 25 and changes the traveling direction of the chain 25. A cylinder 35 is interposed between the driven roller 31 b and the driven roller 31 c. By expanding and contracting this cylinder 35, the distance between the disposing axes of the driven rollers 31 b, 31 c is changed, so that the chain bucket 29 So that it is possible to change the moving orbit locus. Incidentally, in correspondence to the presence of the two chains 25, there are also two drive rollers 31a, followers 31b, 31c and two deflection rollers 33, respectively, and are arranged side by side in a direction orthogonal to the page of FIG. 1 .

As the driving roller 31a drives the chain 25, the chain 25 circulates in the direction of the arrow W with a predetermined trajectory with respect to the elevator main body 23, and the chain bucket 29 moves round the uppermost portion 9a of the bucket elevator 9 and the scraping portion 11 And circulates while traveling around.

The bucket 27 of the chain bucket 29 ascends in a posture in which its opening 27 a faces upward. Then, at the uppermost part 9a of the bucket elevator 9, when passing through the driving roller 31a, the chain 25 changes its direction from upward to downward, and the opening 27a of the bucket 27 turns downward. The discharge chute 36 is formed below the opening 27 a of the bucket 27 which is thus directed downward. The lower end of the discharge chute 36 is connected to a rotary feeder 37 disposed on the outer periphery of the bucket elevator 9.

The rotary feeder 37 conveys the bulk M carried out from the discharge chute 36 to the boom 7 side. A boom conveyor 39 is arranged on the boom 7, and this boom conveyor 39 is adapted to supply the hopper 41 with the bulk M transferred from the rotary feeder 37. Below the hopper 41, a belt conveyor 43 and an on-ground conveyor 45 in the machine are arranged.

The unloading of the bulk load (object) M using this continuous unloader 1 is carried out as follows. The scraping portion 11 at the lower end portion of the bucket elevator 9 is inserted into the hold 103 and the chain 25 is made to circle in the direction of the arrow in FIG. Then, the bucket 27 located in the scraping portion 11 continuously excavates and scrapes off the bulk load M such as coal, coke, ore and the like. The bulk material M scraped and stacked by these buckets 27 is conveyed vertically upward to the uppermost part 9 a of the bucket elevator 9 as the chain 25 rises.

Thereafter, the bucket 27 passes through the position of the drive roller 31 a, and the bucket 27 turns, whereby the bulk M drops from the bucket 27. The bulk M dropped from the bucket 27 falls into the discharge chute 36 and is carried out to the side of the rotary feeder 37 and further transferred to the hopper 41 by being transferred to the boom conveyor 39. Further, the bulk M is carried out to the ground side facility 49 via the belt conveyor 43 and the ground conveyor 45. The above operation is repeatedly performed using a plurality of buckets 27, whereby the bulk M in the hold 103 is continuously landed.

Subsequently, the configuration of the vicinity of the deflecting roller 33 of the bucket elevator 9 will be described in more detail.

As shown in FIG. 3, the deflecting roller 33 is brought into contact with the chain 25 which moves downward after being folded by the driving roller 31 a, and bends the chain 25 toward the inside of the circulation path. Then, the deflecting roller 33 converts the traveling direction of the chain 25 after turning back by the driving roller 31 a from the obliquely downward direction to the vertically downward direction. According to this configuration, since the bucket 27 that has discharged the bulk M after folding moves diagonally downward so as to avoid the discharge chute 36 between the drive roller 31 a and the deflecting roller 33, the bucket 27 on the upper side It is hard to interfere with the bulk load M falling down from 27. Therefore, the bulk M continuously dropped from each bucket 27 is smoothly introduced into the discharge chute 36. In this manner, the bending of the circulation path of the chain 25 by the deflecting roller 33 contributes to the smooth movement of the bulk M to the discharge chute 36.

Here, the present inventors have found that the deflection roller 33 is involved as a relatively large vibration source due to collision with the chain 25 in the vibration generated in the bucket elevator 9. Therefore, in order to reduce vibration caused by the deflecting roller 33, the following structure is adopted for the bucket elevator 9.

(1) As shown in FIG. 4, the two deflection rollers are arranged in parallel so that the rotation axis A is common. The bucket elevator 9 includes a fixed shaft 51 extending through the center of the two deflection rollers 33 in the direction of the rotation axis A and rotatably supporting both deflection rollers 33. The fixed shaft 51 is a cylindrical bar member fixed to the elevator main body 23 so as not to rotate, and the fixed shaft 51 is supported at both ends thereof by the elevator main body 23 at both ends thereof. The two deflection rollers 33 are supported by one common fixed shaft 51 and are rotatable around the fixed shaft 51. In this case, the size of the bucket 27 is set so that the bucket 27 passing between the deflecting rollers 33, 33 does not interfere with the fixed shaft 51.

(2) Each deflecting roller 33 is composed of three portions of a bearing (rotating shaft portion) 61, a wheel portion 62, and a ring portion 63 concentrically provided from the rotation center side. The bearing 61 is a portion to be joined to the fixed shaft 51, and is composed of, for example, a ball bearing. The ring portion 63 is located at the circumferential outer edge portion of the deflecting roller 33 and is a portion that contacts the chain 25. The wheel portion 62 is a portion connecting the bearing 61 and the ring portion 63. The deflecting roller 33 is supported by the fixed shaft 51 and rotates around the fixed shaft 51 via the bearing 61.

The wheel portion 62 of the deflecting roller 33 is formed of a single plate member 62 a having a thickness in the direction of the rotation axis A (see FIG. 5). When viewed in the direction of the rotation axis A, the plate member 62 a has a shape that fills the entire region between the bearing 61 and the ring portion 63. That is, the plate member 62 a has a ring shape sandwiched by two concentric circles, which is a boundary line between the bearing 61 and the ring portion 63 as seen in the direction of the rotation axis A. In addition, the wheel portion 62 does not have straight spokes extending straightly along the radius of the deflecting roller 33, but is formed of only the plate-like member 62 a. In the following description as well, spokes composed of straight members extending along the radius of the diverting roller are referred to as “straight spokes”. In general, the wheel portion 62 having such a structure is sometimes referred to as a “disk wheel”, a “disk wheel” or the like.

In this way, as another example of the deflecting roller having the disk wheel type wheel portion 62, as shown in FIG. 5 (a), the wheel portion 62 has a plurality of (see FIG. 5 (a)) arranged in parallel in the direction of the rotation axis A In the example of FIG. 1) two plate-like members 62 a may be used. As shown in FIGS. 5 (b) and 5 (c), as a reinforcing material for reinforcing the plate member 62 a, a straight spoke portion 62 b extending straight along the radius of the diverting roller is formed as a plate-like member 62 a On one side or on both sides.

(3) Among the turning rollers 33, the ring portion 63 is a portion where the chain 25 actually contacts, and an impact force in the rotational radial direction acts on the ring portion 63 due to the collision of the chain 25. Therefore, the ring portion 63 is supported by the elevator main body 23 via a radial damping member for suppressing vibration in the radial direction (radial direction) of the ring portion 63. As a concrete example of this configuration, as shown in FIG. 4 (b), the vibration damping member 53 as the radial vibration damping member is disposed so as to concentrically surround the fixed shaft 51, The fixed shaft 51 is fixed to the elevator main body 23 via the damping member 53. In the elevator main body 23, a ring-shaped steel material 55 is disposed in a portion surrounding the vibration damping member 53. The material of the vibration damping member 53 may be, for example, an elastic member such as damping rubber or a spring, or a damping steel plate or the like. With this structure, the fixed shaft 51 is supported by the elevator main body 23 via the vibration damping member 53, and eventually, the ring portion 63 is supported by the elevator main body 23 via the vibration damping member 53. As another example of the configuration in which the ring portion 63 is supported by the elevator body 23 via the radial damping member, the material of the wheel portion 62 may be a vibration damping steel plate. In this case, the entire wheel portion 62 made of a vibration damping steel plate functions as a radial damping member.

Due to the weight of the deflecting roller 33 and the fixed shaft 51, the lower part of the vibration damping member 53 is most deteriorated. Therefore, periodically, by rotating the vibration damping member 53 around the rotation axis A and installing it again, deterioration of the vibration damping member 53 biased to a part is avoided, and the life of the vibration damping member 53 is prolonged be able to.

FIG. 6 is an enlarged view showing the vicinity of one end face 51 a of the fixed shaft 51, and is a view showing an example of a support structure for supporting the fixed shaft 51 in the direction of the rotation axis A. As shown in FIG. In this structure, the end surface 51 a of the fixed shaft 51 and the steel material 55 are connected by a U-shaped fixing jig 71. It should be noted that the fixing jig 71 is not shown in FIG. The fixing jig 71 is composed of three link members connected by hinge joints at the joint portions 71 a, 71 b, and the joint portions 71 a, 71 b are positioned substantially on the rotation axis A. According to such a fixing jig 71, it is possible to restrict the movement in the direction of the rotation axis A while allowing movement of the fixed shaft 51 in the radial direction of rotation. Therefore, according to this support structure, it is possible to support the fixed shaft 51 in the direction of the rotation axis A without impairing the vibration damping function in the radial direction of the fixed shaft 51 by the vibration damping member 53. A similar support structure is also formed on the other end face of the fixed shaft 51.

As another concrete example of the configuration in which the ring portion 63 is supported by the elevator main body 23 via the radial damping member, as shown in FIG. 7, the radial damping member is included in the wheel portion of the diverting roller It may be configured. That is, as shown in FIG. 7 (a), the wheel portion 262 is composed of two parts: an outer peripheral portion 262 a having straight spokes and an inner peripheral portion 262 b formed by the vibration damping member 54 a on the inner side thereof May be used. Further, as shown in FIG. 7 (b), the wheel portion 362 is composed of two parts, an outer peripheral portion 362 a formed by the vibration damping member 54 b and an inner peripheral portion 362 b having straight spokes on the inner side thereof May be used.

Further, as shown in FIG. 7 (c), the wheel portion 462 is composed of two parts, an outer peripheral portion 462 a formed by the vibration damping member 54 c and an inner peripheral portion 462 b having a disc shape inside the outer portion 462 a May be used. The inner peripheral portion 462 b is provided with a punch hole 462 c penetrating in the rotation axis direction. The wheel portion 462 is a plate-like member extending in the region between the bearing 61 (rotating shaft portion) and the ring portion 63 when viewed in the thickness direction with the thickness in the direction of the rotation axis A being the thickness. A punch hole (through hole) 462 c penetrating in the direction of the rotation axis A is provided in the wheel portion 462. According to this structure, it is easier to reduce the weight by the weight of the punch hole 462 c than the above-described deflection roller 33 (see FIG. 4).

(4) The deflection roller 33 shown in FIG. 4 is supported in the direction of the rotation axis A with respect to the elevator main body 23 via an axial vibration damping member for suppressing vibration in the direction of the rotation axis A (thrust direction). A concrete example of such a support structure will be described below with reference to FIGS. 8 to 11. A part of the members shown in FIGS. 8 to 11 are not shown in FIG. 4 for convenience of illustration. 8 to 11 show the structure in the vicinity of one end face 51 a of the fixed shaft 51, a similar support structure is also constructed on the other end face of the fixed shaft 51. In addition, in the support structure shown in FIGS. 6 to 11, the same or equivalent constituent elements are denoted by the same reference numerals, and redundant explanations are omitted.

As an example of the support structure, as shown in FIG. 8, a circular structure as an axial vibration damping member is provided around the hinge shaft 71 c fixed to the link member 71 j side in the joint portion 71 a of the fixing jig 71 described above The vibration member 73a is inserted and the vibration damping member 73a is interposed between the hinge shaft 71c and the bearing portion of the hinge shaft of the link member 71k. That is, in this structure, the link members 71 h and 71 k fixed to the steel material 55 side, the link member 71 j fixed to the end face 51 a of the fixed shaft 51, and the joint portion 71 a hinge-connected between the link members 71 k and 71 j , The vibration damping member 73a as an axial vibration damping member is interposed between the hinge shaft 71c and the link member 71k.

According to this structure, the vibration of the link member 71 j in the direction of the rotation axis A with respect to the link members 71 h, 71 k of the fixing jig 71 is suppressed, and further the vibration in the direction of the rotation axis A of the fixed shaft 51 and the deflecting roller 33 is suppressed . In addition, according to this configuration, even if vertical displacement of the fixed shaft 51 occurs due to aged deterioration of the vibration damping member 53, the vibration damping member 73 a deforms following it and can absorb vertical displacement.

As another example of the support structure, as shown in FIG. 9, a vibration damping member 73 b as an axial vibration damping member is inserted between the link member 71 j of the fixing jig 71 and the end face 51 a of the fixed shaft 51 . That is, in this structure, the steel member 55 and the end face 51 a of the fixed shaft 51 are coupled to each other by the restricting tool 70 b including the fixing jig (regulating device main body) 71 and the damping member 73 b, and fixed to the steel material 55 The movement of the shaft 51 in the direction of the rotation axis A is restricted.

According to this structure, the vibration of the fixed shaft 51 in the direction of the rotation axis A with respect to the fixing jig 71 is suppressed, and further the vibration in the direction of the rotation axis A of the deflecting roller 33 is suppressed. According to this configuration, even if vertical displacement of the fixed shaft 51 occurs due to aged deterioration of the vibration damping member 53, the vibration damping member 73 b follows and deforms to absorb vertical displacement.

As still another example of the support structure, the flange 75 is attached to the end face 51 a of the fixed shaft 51 as shown in FIG. 10. The flange 75 protrudes from the fixed shaft 51 in the rotational radial direction up to a position facing the steel material 55. A damping member 73 c as an axial vibration damping member is inserted between the flange 75 and the steel member 55 and the damping member 53. That is, in this structure, the steel member 55 and the end face 51 a of the fixed shaft 51 are coupled by the restricting tool 70 c including the flange (regulating device main body) 75 and the damping member 73 c, and the fixed shaft 51 The movement in the direction of the rotation axis A is restricted. According to this structure, the vibration of the fixed shaft 51 in the direction of the rotation axis A with respect to the steel material 55 (the elevator main body 23) is suppressed, and further the vibration of the deflecting roller 33 in the direction of the rotation axis A is suppressed.

As still another example of the support structure, as shown in FIG. 11, a lid portion 77 for pressing the end face 51 a of the fixed shaft 51 is attached to the steel material 55. A damping member 73 d as an axial vibration damping member is inserted between the lid portion 77 and the end face 51 a of the fixed shaft 51. That is, in this structure, the steel member 55 and the end face 51 a of the fixed shaft 51 are connected to each other by the restricting tool 70 d including the lid portion (regulating device main body) 77 and the damping member 73 d, and the fixed shaft 51 in the direction of the rotation axis A is restricted. According to this structure, the vibration of the fixed shaft 51 in the direction of the rotation axis A with respect to the steel material 55 (the elevator main body 23) is suppressed, and further the vibration of the deflecting roller 33 in the direction of the rotation axis A is suppressed.

8 to 11 can support the fixed shaft 51 in the direction of the rotation axis A without impairing the vibration damping function in the radial direction of the fixed shaft 51 by the vibration damping member 53. The material of the vibration damping members 73a to 73d may be, for example, an elastic member such as a damping rubber or a spring, or a vibration damping steel plate or the like.

Next, the action and effect of the above-described bucket elevator 9 will be described. The bucket elevator 9 is characterized in particular by the following four points (first to fourth feature points).

(First feature point)

As a first characteristic point, the bucket elevator 9 includes a fixed shaft 51 extending on a common axis of rotation A of the pair of deflecting rollers 33, 33 and rotatably supporting both deflecting rollers 33, 33 There. According to this configuration, the acceleration response of the elevator main body 23 due to the impact force of the collision of the chain 25 and the deflecting roller 33 becomes small as shown in the simulation described later, and the vibration of the bucket elevator 9 is reduced.

(Second Feature Point)

As a second characteristic point, in the deflection roller 33 of the bucket elevator 9, the wheel portion 62 has a shape in which the direction of the rotation axis A is the thickness direction and a shape that fills the entire region between the bearing 61 and the ring portion 63 when viewed in the thickness direction Shaped member. According to this configuration, the acceleration response of the elevator main body 23 due to the impact force of the collision of the chain 25 and the deflecting roller 33 becomes small as shown in the simulation described later, and the vibration of the bucket elevator 9 is reduced.

(Third Feature Point)

As a third characteristic point, in the diverting roller 33 of the bucket elevator 9, the ring portion 63 is provided with a radial vibration damping member (for example, vibration damping members 53, 54 a to 54 c, etc.) for suppressing vibration in the radial direction of rotation , And is supported by the elevator main body 23. Among the turning rollers 33, the ring portion 63 is a portion where the chain 25 actually contacts, and an impact force in the rotational radial direction acts on the ring portion 63 due to the collision of the chain 25. On the other hand, according to the above-described configuration, since the vibration in the radial direction of the ring portion 63 due to the impact force is hardly transmitted to the elevator main body 23 through the radial damping member, the vibration of the bucket elevator 9 Is suppressed.

(Fourth Feature Point)

As a fourth characteristic point, the deflection roller 33 of the bucket elevator 9 rotates relative to the elevator main body 23 via an axial vibration damping member (for example, vibration damping members 73a to 73d) that suppresses vibration in the direction of the rotational axis A And is supported in the direction of the axis A direction. The inventors of the present invention found that relatively large vibration occurs in the direction of the rotation axis A in the deflection roller 33 at the time of collision of the chain 25 in the bucket elevator 9. On the other hand, according to the above configuration, the vibration in the direction of the rotation axis A of the deflecting roller 33 becomes difficult to be transmitted to the elevator main body 23 through the axial vibration damping member, so that the vibration of the bucket elevator 9 is suppressed.

In FIG. 4, the configuration of the bucket elevator 9 including all of the above-described first to fourth feature points has been described. However, by providing at least one of the first to fourth feature points, the bucket elevator 9 Vibration can be suppressed. Also, two or three of the first to fourth feature points may be used in combination for the bucket elevator. Further, the respective structures of the bucket elevator 9 shown in the description of the above embodiment may be appropriately combined and employed.

Subsequently, a simulation performed by the present inventors to confirm the vibration reduction effect according to the first feature point will be described.

In this simulation, as shown in FIG. 12 (a), a model of the deflecting roller s 1 in which the wheel portion is a straight spoke is used. The structure of this turning roller s 1 is commonly found in turning rollers in a conventional continuous unloader. Here, the radius of the deflecting roller s 1 is 700 mm and the radius of the fixed axis s 51 and s 52 is 55 mm. Further, the Young’s modulus of the material of the diverting roller s 1 was 21000 kgf / mm 2, the Poisson’s ratio was 0.3, and the density was 7.85 ton / m 3.

In the model M 1 shown in FIG. 12 (b), the two deflecting rollers s 1 are supported so as to be cantilevered by different fixed axes s 52. It is assumed that the fixed axis s 52 is directly fixed to the steel material 55 of the elevator main body 23. The support structure of the model M1 is commonly seen as a support structure of the deflecting roller in the conventional continuous unloader. On the other hand, the model M 2 shown in FIG. 12 (c) has the first feature point, and the two deflection rollers s 1 are supported at both ends by a common fixed axis s 51. It is assumed that the fixed axis s 51 is directly fixed to the steel material 55 of the elevator main body 23.

For each of the above models M 1 and M 2, the respective accelerations (longitudinal acceleration, vertical acceleration, lateral acceleration, lateral acceleration, lateral acceleration) of the elevator main body 23 in three directions (the front-rear direction, the up-down direction, and the left-right direction) when the chain 25 collides with the deflection roller s 1 ) Was calculated. In this case, the vertical direction is defined as “vertical direction”, the rotational axis direction of the deflecting roller s 1 is defined as “horizontal direction”, and the direction orthogonal to both the vertical direction and the lateral direction is defined as “longitudinal direction”.

The value of the lateral acceleration in the model M1 is set to 1.0 and each of the obtained accelerations is expressed as a relative value and is shown as a graph in FIG. For each of the models M 1 and M 2, the displacement (longitudinal displacement, vertical displacement, lateral displacement) of the elevator body 23 in three directions (the front-rear direction, the up-down direction, and the left-right direction) when the chain 25 collides with the deflection roller s 1 ) Was calculated. Each obtained displacement is expressed as a relative value with the value of the lateral displacement in the model M1 taken as 1.0 and is shown as a graph in FIG.

According to FIG. 13, it can be seen that the acceleration response of the elevator main body 23 in the model M 2 is lower in both of the three directions than in the model M 1. Further, in the model M 2, as the acceleration response decreased, there was concern that the displacement of the elevator main body 23 would be increased. As shown in FIG. 14, the model M 2 has an elevator body 23 As shown in Fig.

As described above, the structure of the bucket elevator 9 having the above-described first feature reduces the vibration of the elevator main body 23 caused by the collision between the chain 25 and the deflecting roller 33, and reduces the vibration of the bucket elevator 9 and the continuous unloader 1 It was confirmed that it was attempted.

Subsequently, a simulation performed by the present inventors to confirm the vibration reduction effect of the deflecting roller 33 according to the second characteristic point will be described.

In this simulation, a model M 11 using a deflecting roller composed of straight spokes for the wheel portion was prepared for comparison. The structure of the deflecting roller is the same as that of the diverting roller s 1 shown in FIG. 12 (a), so its illustration is omitted. Further, models M12, M13, and M14 using turning rollers having a wheel portion of a plate member were prepared as a model having the second feature point. In each of the models M 11 to M 14, similarly to the support structure shown in FIG. 12 (b), each of the two deflection rollers was supported in a cantilever manner.

The deflecting roller of the model M 12 has a wheel portion having a structure in which two plate-like members having a thickness of 6 mm are stacked. The deflecting roller of the model M13 has a wheel portion having a structure in which two plate-shaped members with a plate thickness of 4 mm are stacked. The structure of the deflecting roller of the model M 12, 13 is the same as that shown in FIG. 5 (a), so its illustration is omitted. The deflecting roller of the model M 14 has a wheel portion having a structure composed of one plate member having a plate thickness of 8 mm. Since the structure of the deflecting roller of the model M 14 is the same as that shown in FIGS. 4 (a) and 4 (b), illustration is omitted.

Here, the radius of the deflecting roller of each model M 11 to M 14 was 700 mm, and the radius of the fixed axis was 55 mm. In addition, the material Young’s modulus of each turning roller was 21000 kgf / mm 2, the Poisson’s ratio was 0.3, and the density was 7.85 ton / m 3.

For each of the models M 11 to M 14, the acceleration (longitudinal acceleration, vertical acceleration, and lateral acceleration) in three directions (the front-rear direction, the up-down direction, and the left-right direction) of the elevator main body 23 when the chain 25 collides with the deflecting roller, Was calculated. In this case, the vertical direction is defined as “vertical direction”, the rotational axis direction of the deflecting roller is defined as “horizontal direction”, and the direction orthogonal to both the vertical direction and the horizontal direction is defined as “longitudinal direction”. The value of the lateral acceleration in the model M 11 is set to 1.0, and each of the obtained accelerations is expressed as a relative value and is shown as a graph in FIG. 15. For each of the models M 11 to M 14, the displacement (longitudinal displacement, vertical displacement, and lateral displacement) of the elevator body 23 in three directions (the front-rear direction, the up-down direction, and the left-right direction) when the chain 25 collides with the deflecting roller, Was calculated. Each of the obtained displacements is expressed as a relative value with the value of the lateral displacement in the model M 11 taken as 1.0 and is shown as a graph in FIG. 16.

According to FIG. 15, it is understood that the acceleration responses of the elevator main body 23 in the three models are lower in the models M 12 to M 14 than in the model M 11. Also, in the models M 12 to M 14, there was concern that the displacement of the elevator main body 23 increased due to the decrease in the acceleration response. As shown in FIG. 16, the models M 12 to M 14 were compared with the model M 11 It was confirmed that the displacement of the elevator main body 23 did not increase extremely.

As described above, the structure of the bucket elevator 9 having the above-described second feature reduces the vibration of the elevator main body 23 due to the collision between the chain 25 and the deflecting roller 33, and reduces the vibration of the bucket elevator 9 and the continuous unloader 1 It was confirmed that it was attempted.

Further, according to FIG. 15, it can be seen that the acceleration response of the elevator main body 23 decreases in the order of the models M 12, M 13, M 14. Therefore, when comparing the models M 12 and M 13, when constructing the wheel portion with two plate-like members, it is preferable to use a plate-shaped member having a small thickness as the vibration reducing effect of the bucket elevator 9 and the continuous unloader 1 is It turned out to be big. Further, when the models M13 and M14 are compared, a configuration in which one plate member having the total thickness of the two sheets is adopted as the wheel portion is adopted as compared with the two plate members with thin plate thickness, The vibration reduction effect of the bucket elevator 9 and the continuous unloader 1 is large.

Subsequently, improvement of cargo handling capacity of the continuous unloader 1 and the continuous unloader facility 200 will be described.

In the conventional general bucket elevator type continuous unloader, the speed of circulating movement of the chain at the time of operation is at most about 80 m / min. On the other hand, the maximum speed of the circular movement of the chain 25 during the operation of the continuous unloader 1 is 90 to 150 m / min. In the operation method of the continuous unloader 1 in the present embodiment, the revolution speed of the chain 25 is operated at 90 to 150 m / min.

As described above, in the continuous unloader 1, by making the circulation speed of the chain 25 faster than the conventional speed, cargo handling ability can be improved while avoiding enlargement of the airframe. In this case, by setting the circulation speed of the chain 25 to 90 m / min or more, it is possible to improve the cargo handling ability while sufficiently suppressing the increase in the manufacturing cost of the continuous unloader and the like due to the suppression of the larger size of the airframe. Further, when the circulating speed of the chain 25 exceeds 150 m / min, the conveyed bulk M does not smoothly fall from the bucket 27 to the discharge chute 36, and furthermore, the bucket elevator 9 Vibration is generated, which is not preferable. In addition, if the circulating speed of the chain 25 exceeds 150 m / min, the scraping speed of the bulk M by the bucket 27 is too fast, so that the moving speed of the continuous unloader 1 on the rail 3 a is insufficient, Unloading can not be performed smoothly. On the contrary, in the continuous unloader 1, by setting the circumferential moving speed of the chain 25 to 150 m / min or less, the above-mentioned problem can be reduced.

From the above viewpoint, it is more preferable that the maximum speed of the circling movement of the chain 25 is 95 to 150 m / min. Further, it is more preferably 100 to 150 m / min, and even more preferably 100 to 120 m / min.

In addition, the bucket elevator 9 has at least one of the first to fourth feature points described above. This makes it possible to suppress vibration occurring in the bucket elevator 9 even when the revolution speed of the chain 25 is set to 150 m / min. Specifically, in the continuous unloader 1, when the circulating movement speed of the chain 25 is set to 150 m / min, the acceleration of vibration of the deflection roller 33 is 6 G or less, and the noise at the distal end portion of the bucket elevator 9 is 100 dB or less. This means that vibration and noise generated in the driver’s seat of the continuous unloader 1 can be suppressed within an allowable range.

As described above, according to the continuous unloader 1, by improving the circulation speed of the chain 25, it is possible to improve the cargo carrying capacity while avoiding enlargement of the airframe. By suppressing upsizing of the continuous unloader 1, the manufacturing cost of the continuous unloader 1 can be suppressed. Furthermore, since the weight increase of the continuous unloader 1 is suppressed, the required strength of the quay 101 is suppressed, and as a result, the construction cost of the quay 101 can be suppressed. Therefore, the manufacturing cost of the continuous unloader facility 200 as a whole including the construction cost of the quay 101 can also be suppressed.

The loading capacity and manufacturing cost of a continuous unloader facility will be described below, taking concrete examples.

In the following, a continuous unloader that has been improved in loading capacity by making the bucket elevator faster than the conventional one is called “unloader for high speed”, and the continuous unloader, which has been increased in size and improved in cargo handling capacity as compared with the past, is referred to as “large unloader”. Also, we compare the speeding unloader and the large unloader as having the same loading capacity. The calculation formulas used in the following description are empirically known calculation formulas, and the left side and the right side of these calculation formulas do not necessarily coincide strictly (that is, “=”), In actuality, some errors may occur (that is, “≈”).

In order to achieve the same loading capacity, the weight Wb of the bucket elevator is a function of the bucket elevator speed (speed of the bucket) V,

Wb = f (V) (1)

It can be expressed as.

If the bucket elevator speed of the large sized unloader is V1, the weight of the bucket elevator of the large sized unloader is Wb1, the bucket elevator speed of the high speed unloader is V2, and the weight of the bucket elevator of the high speed unloader is Wb2,

Wb 2 = Wb 1 × (V 1 / V 2) (2)

. Also, when the weight of the entire unloader is Wa 1, the weight Wa 2 of the unloader as a whole is increased by

Wa 2 = (1 – (1 – Wb 2 / Wb 1) / k 1) × Wa 1 (3)

It can be expressed as. Note that k 1 is a predetermined coefficient.

Also, if the weight of the quay that supports the large unloader is Wp 1, the weight Wp 2 of the quay supporting the high speed unloader,

Wp 2 = Wp 1 × k 2 × (Wa 2 / Wa 1) (4)

(Reference 1: Shibasaki Ryuichi et al., “Establishment of Economic Evaluation Method in Seismic Design of Port Facilities Considering Freight Transport Cost”, Kokon Research Data N 0.125). Incidentally, k 2 is a predetermined constant. And if the production cost of the large unloader is Cu 1, the manufacturing cost Cu 2 of the high speed unloader is

Cu 2 = Cu 1 × (Wa 2 / Wa 1) 0.7 (5)

It is empirically known that it is expressed as.

Similarly, the difference between the construction cost Cp 1 per unit length of the quay that supports the large unloader and the construction cost per unit length of the quay supporting the high speed unloader is Cp 2,

Cp 2 – Cp 1 = (Wa 1 – Wa 2) /Wa 1 × 0.2 / 0.05 × 3 [million yen / m] (6)

It is empirically known that it is expressed as.

When the bucket elevator speed of the large unloader is set to 75 m / min and the bucket elevator speed of the high speed unloader is set to 90 m / min using the above equations (1) to (6)

Cu 2 = Cu 1 × 0.94

Cp 2 -Cp 1 = 1. 02 [million yen / m]

. The coefficient k 1 was set to 2. If the manufacturing cost of the large size unloader is 1500 million yen and the length of the quay wall is 300 m, the reduction cost C in the case of adopting the high speed unloader compared with the case of adopting the large unloader is,

C = 1500 × 0.06 + 1 × 300 = 390 [Million yen]

, which is 26% (390/1500) reduction in airframe conversion ratio.

Likewise, if the bucket elevator speed of the large size unloader is set to 75 m / min and the bucket elevator speed of the high speed unloader is compared with 95 m / min, the cost is reduced by 491 [million yen], a reduction of 33% .

Likewise, if the bucket elevator speed of the large unloader is set to 75 m / min and the bucket elevator speed of the high speed unloader is compared with 120 m / min, the cost is reduced by 878 [million yen], a reduction of 59% .

Likewise, if the bucket elevator speed of the large unloader is set to 75 m / min and the bucket elevator speed of the high speed unloader is compared with 150 m / min, the cost is reduced by 3632 [million], and 240% reduction in the airframe conversion ratio .

According to the continuous unloader 1 and the continuous unloader facility 200 in which the maximum speed of the circular movement of the chain 25 is thus set to 90 to 150 m / min, the manufacturing cost of the continuous unloader body and the quay wall is adjusted to about 30 to 240% Can be expected to be reduced.

In the continuous unloader of the bucket elevator type, the present invention improves the cargo handling ability while suppressing an increase in the manufacturing cost by improving the maximum speed of the circulating movement of the chain.

1: continuous unloader,

9: bucket elevator,

25: chain (endless chain),

27: bucket,

31 a, 31 b, 31 c: drive roller,

33 turning roller,

101 quay,

200 continuous unloader facility,

M bulk (cargo).

 

 

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