Patent Application
20110168352
This disclosure relates to an air supply apparatus for supplying air to a carriage which moves in a carriage path, and a cooling facility having the air supply apparatus for hot grain/lump material. The cooling facility loads hot sintered ore, pelletized ore and the like into the carriage and cools the same.
A sintered ore cooling facility is one of cooling facilities for hot grain/lump material. The sintered ore cooling facility is formed so that sintered ore, which is a hot grain/lump material, is loaded into a carriage and the carriage is moved along a generally circular carriage path while cooling air is blown from a lower part of the carriage to an upper part to cool the sintered ore (refer to JP-A-4-139380, JP-A-6-257955 and JP-A-2000-310489, for example).
In the sintered ore cooling facility, a carriage formed of plural connected pan carriages for loading the sintered ore thereinto is arranged between an inner circumferential sidewall and an outer circumferential sidewall, which extend along a circular path, to be freely movable. In a bottom part of the pan carriage, provided is a cool-air box which the cooling air is supplied into. The cool-air box of each pan carriage is connected to a stationary circular duct through a connecting duct. The stationary circular duct is connected to a movable circular duct so that the movable circular duct is fitted into the stationary circular duct through a water sealing device to be freely movable. Further, a cooling air supply apparatus is arranged through the connecting air duct to supply cooling air.
The water sealing device has an inner circumferential circular water seal chamber and an outer circumferential circular water seal chamber, which are formed in the movable circular duct. The water sealing device comprises water sealing plates whose lower ends are sunk in sealing water in the inner circular water seal chamber and the outer circular water seal chamber, the water sealing plates being formed in the stationary circular duct.
Now, an example of the above-mentioned sintered ore cooling facility is described on the basis of
In
The carriage 1 comprises plural pan carriages 7, an inner circular sidewall 3 and an outer circular sidewall 4, as shown in
Each of the pan carriages 7 comprises, as shown in
A stationary circular duct 31 is provided to cover the upper part of the movable circular duct 21 all over and form a circular stationary air path 37 communicating with the movable air path 25. In the stationary circular duct 31, a top cover plate 40 and both sidewall parts 32 and 33 are formed into the shape of “C” having an opening on its bottom side in cross section. The top cover plate 40 in the cooling zone C is connected to plural middle air ducts 38 from an arc-shaped air header 39 shown in
The stationary circular duct 31 is connected to the movable circular duct 21 through a water sealing device 28, as shown in
A dead plate 42 is mounted to the stationary circular duct 31 at a part other than the middle air duct 38 through an expansion joint 41. To the upper end parts of the inner plate 22a and the outer plate 23a, mounted are labyrinth sealing plates 43a and 43b whose top ends are close to the dead plate 42 to provide the labyrinth seal.
In an upper part of the carriage path A, provided is a stationary hood 51 formed from the inner and outer circumferential stationary plates 51a and 51b, which are provided at the upper end parts of the inner and outer circular sidewalls 23 and 24 through sealing devices, and a stationary top plate 51c for connecting the upper end parts of the inner and outer circumferential stationary plates 51a and 51b. An exhaust duct 52 is connected to a predetermined place of the stationary hood 51.
Furthermore, a partition plate 47 is provided for every connection air duct 26 (every pan carriage 7) in the movable air path 25 of the movable circular duct 21, as shown in
The sintered ore cooling facility having the above-mentioned structure has the following problems.
The pressure of the movable air path 25 and the cool-air box 12 is the atmospheric pressure in the feed and discharge zone B. On the other hand, the pressure of the movable air path 25 in the cooling zone C is 300 to 500 mmAq (referred to as “differential pressure in cooling,” hereinafter). The latter pressure is kept also in the upper space of the water seal chamber 24i by the dead plate 42 and the labyrinth sealing plates 43a, 43b and 43c due to the structure. The length of the dead plate 42, however, is 10 m or more and, therefore, it is difficult in view of technology of manufacture to completely seal the dead plate 42 having such long length. Moreover, combined with aging due to long-term use, generated is a gap between the labyrinth sealing plates 43a, 43b and 43c and the dead plate 42, so that the cooling air in the spaces of the water seal chambers 24i and 24i is leaked. This causes a lowering of cooling efficiency.
Further, the air as much as the air leakage leaked in the feed and discharge zone B flows into the upper spaces of the water seal chambers 24i and 24i from the movable air path 25 in the cooling zone C, and violently flows toward the feed and discharge zone B within the upper spaces of the water seal chambers 24i and 24i, due to the differential pressure of the cooling air. This causes, in the circular water seal chambers 24a and 24b in the feed and discharge zone B, wave in the sealing water, or the air leakage from the labyrinth sealing part to the movable air path 25, which causes water splash over the movable air path 25 together with sealing water in the circular water seal chambers 24a and 24b. The sealing water splashed and accumulated in the movable air path 25 will further splash about the pan carriage 7 to adhere to a wall surface in the feed and discharge zone B or in the pan carriage 7. The dust of the sintered ore adheres to the adhered drops of water and solidifies and grows to become the wet dust, which causes troubles such as corrosion or a clogging of the pan carriage 7, so that normal operation is disturbed. Furthermore, wave or splash of the sealing water deteriorates water-sealing performance. This lowers cooling efficiency.
To overcome the problems, levels of an upper end of the partition plate 47 and upper ends of the labyrinth sealing plates 43a, 43b and 43c should be adjusted in all over the zone to be controlled so that gaps between the dead plate 42 and the partition plate 47 become almost closed. It is difficult, however, to control the large number of labyrinth sealing plates 43a, 43b and 43c provided in the extremely long length of movable circular duct 21. The operations and aging of the facility further widen the gap and deteriorate the sealing performance, but it is impossible to rectify during the operation of the facility.
JP-A-2000-310489 has proposed that the upper spaces of the water seal chambers 24i and 24i on a movable air path 25 side are supplemented with compressed air (auxiliary air) in the feed and discharge zone B, as shown in
However, in the method proposed in JP-A-2000-310489, a large quantity of auxiliary air should be supplied as back pressure in the case where the air leakage is increased, resulting in an increase not only in air leakage quantity of the cooling air but also in troubles by loss of the balance caused by the air leakage.
It could therefore be helpful to provide an air supply apparatus used in cooling hot grain/lump material such as sintered ore and pelletized ore and a cooling facility for hot grain/lump material provided with the air supply apparatus, which are superior in efficiency of use and excellent in maintenance performance.
We thus provide the following air supply apparatus and cooling facility for hot grain/lump material:
[1]. An air supply apparatus comprising:
characterized in that:
characterized in that:
characterized in that:
characterized in that:
characterized by:
characterized by:
characterized in that:
characterized in that:
We provide an air supply apparatus and a cooling facility for hot grain/lump material provided with the air supply apparatus, which are superior in efficiency of use and excellent in maintenance performance.
Examples of our apparatus and cooling facilities are described as the structures of a cooling facility of sintered ore, hot grain/lump material. In the description and the drawings, components having substantially the same function and structure are marked with the same reference numbers and signs for omitting redundancy.
A basic structure of a cooling facility of sintered ore in accordance with Example 1 is the same as the structures shown in
The cooling facility of the sintered ore of Example 1 includes the carriage 1 provided along the circular carriage path A shown in
The carriage 1 comprises the plural pan carriages 7, the inner circular sidewall 3 and the outer circular sidewall 4, as shown in
In the material discharge zone 9, the guide rails 6a are bent downwardly to incline the pan carriage 7 downward through the guide wheels 5a so that the loaded sintered ore can be discharged downward.
Each of the pan carriages 7 comprises, as shown in
The stationary circular duct 31 is provided to cover an upper part of the movable circular duct 21 all over and form a circular stationary air path 37 communicating with the movable air path 25. In the stationary circular duct 31, the top cover plate 40 and the both sidewall parts 32 and 33 are formed into the shape of “C” having an opening on its bottom side in cross section. The top cover plate 40 in the cooling zone C is connected to the plural middle air ducts 38 from the arc-shaped air header 39 to supply the stationary air path 37 with cooling air. In the feed and discharge zone B (the material feed zone 8 and the material discharge zone 9), no middle air duct 38 is connected.
The stationary circular duct 31 is connected to the movable circular duct 21 through the water sealing device 28, as shown in
In an upper part of the carriage path A, provided is a stationary hood 51 formed from the inner and outer circumferential stationary plates 51a and 51b, which are provided at the upper end parts of the inner and outer circular sidewalls 23 and 24 through sealing devices, and a stationary top plate 51c for connecting the upper end parts of the inner and outer circumferential stationary plates 51a and 51b. An exhaust duct 52 is connected to a predetermined place of the stationary hood 51.
A waste heat recovery zone D may be provided in a part of the cooling zone C in Example 1, as shown in
Example 1 has the following structure additionally to the above:
The air damper 81 is in a closed state in the material feed zone B to close the connection air duct 26, as shown in
Such a structure causes the movable air path 25 and the upper spaces of the water seal chambers 24i and 24i to form an entirely communicated circular duct having no partition in the circumferential direction and an operation of the air damper 81 to properly prevent air leakage in the feed and discharge zone B. Accordingly, no difference in pressure between the feed and discharge zone B and the cooling zone C is made, so that no air flows in the movable air path 25 from the cooling zone C toward the feed and discharge zone B.
Further, the movable air path 25 and the upper spaces of the water seal chambers 24i and 24i are formed into an entirely communicated circular duct having no partition in the circumferential direction while the pressure in the movable air path 25 and the upper spaces of the water seal chambers 24i and 24i is the same in the circumferential direction.
Furthermore, no difference in pressure between the movable air path 25 and the upper spaces of the water seal chambers 24i and 24i in the circumferential direction causes no air flow to the circumferential direction in the movable air path 25 and the upper spaces of the water seal chambers 24i and 24i. Accordingly, no air flow occurs in the feed and discharge zone B from the upper spaces of the water seal chambers 24i and 24i toward the movable air path 25.
This results in prevention of a trouble such as corrosion of the pan carriage 7 and the like and decrease in cooling efficiency due to scatter of sealing water from the circular water seal chambers 24a and 24b. Moreover, the air damper 81 provided in the connection air duct 26 is easy to be maintained and controlled more than the conventional labyrinth sealing part (the dead plate 42 and the labyrinth sealing plates 43a, 43b and 43c), so that performance in maintenance is excellent. In addition, the middle air duct 38 can be provided also on an entrance side and an exit side of the feed and discharge zone B and on an exit side of the waste heat recovery zone D although it cannot be provided in the above places conventionally due to the dead plate 42. This allows the cooling performance to be improved while the scale of the system is kept as it is.
In the waste heat recovery zone D, the heat recovery is performed for the air having high temperature due to cooling of sintered ore, and then, the air is fed again as the cooling air. This often causes a foreign matter such as dust of the sintered ore to be intruded into the cooling air. Intrusion and accumulation of such a foreign matter in the circular water seal chambers 24a and 24b causes deterioration of the water sealing performance due to damage of the water sealing plates 34a and 34b and the like. Accordingly, it is preferable to provide a foreign matter intrusion prevention plate (an obstacle plate) 85, which is for preventing the foreign matter intruded into the cooling air from intruding into the circular water seal chambers 24a and 24b from a space between upper ends of the inner plates 22a and 23a of the circular water seal chambers 24a and 24b and the fitting flange 35 through the upper spaces of the water seal chambers 24i and 24i, in upper parts of the upper spaces of the water seal chambers 24i and 24i, as shown in
Further, in the case where a foreign matter such as dust is intruded into the circular water seal chambers 24a and 24b, and thereby, piled therein, preferably provided is a sucking device (not shown) for sucking and collecting the foreign matter from the circular water seal chambers 24a and 24b. The sucking device may be provided in the feed and discharge zone B where a room is left.
Further, in the case of an improper positional relation between the side rail 6b and the side wheel 5b, which are provided for guiding and holding the running pan carriage 7 from the side, the pan carriage 7 runs off the circle. This causes the movable circular duct 21 connected to the pan carriage 7 through the connection air duct 26 to also run off in rotation. As a result, a great difference in relative relation occurs between the circular water seal chambers 24a and 24b provided on the movable circular duct 21 side and the water sealing plates 34a and 34b provided on the stationary circular duct 31 side so that the water sealing performance is lowered. To prevent the lowering, a gap between the side rail 6b and the side wheel 5b, which causes running off, should be adjusted. The gap, however, can be only adjusted in a standstill state because of a conventional stationary type for liner adjustment. Accordingly, adjustment simultaneous with confirmation of a rotational state cannot be carried out during running, so that accurate adjustment has been difficult.
In view of the above, the side wheel 5b is arranged so that it can be adjusted by a screw jack in Example 1. This allows a position of the side wheel 5b to be adjusted even during running and, thereby, rotation of the circular water seal chambers 24a and 24b to be kept at a high degree of circle. The water sealing performance is thus prevented from being lowered.
Example 2 is basically similar in structure to Example 1. In Example 1, however, the movable air path 25 is made to communicate in the circumferential direction and the partition plate having been conventionally provided in the movable air path 25 is removed. On the other hand, a part of the conventional partition plate 47 is notched so that a function of guiding the cooling air would be left while the movable air path 25 would be made to communicate in the circumferential direction in Example 2.
That is to say, in Example 2, a partition plate 47a formed by notching an upper part of the conventional partition plate 47 is provided so that the movable air path 25 would communicate in the circumferential direction, as shown in
The upper part of the conventional partition plate 47 is notched in
Example 3 basically has a structure similar to that of Example 1 mentioned above. The air damper 81, however, is provided in the connection air duct 26 as a means for closing the connection air duct 26 in the feed and discharge zone B in Example 1 while a connection air duct closing plate is mounted to the stationary circular duct 31 in the feed and discharge zone B to close an inlet of the connection air duct 26 by the connection air duct closing plate in Example 3.
That is to say, in Example 3, a connection air duct closing plate (a dead plate) 91 is mounted to the lower end of a rod and dead plate height indicator 92a, which is fixed to the top cover plate 40 of the stationary circular duct 31 by a rock nut 92b, in the feed and discharge zone B to close the inlet of the connection air duct 26 by the dead plate 91, as shown in
Ref. No. 92c in
A position in height of the dead plate 91 can be adjusted to a proper position by the rod 92a and the lock nut 92b. A position in height of the sealing ring 93a can be adjusted to a proper position by the rod 94a and the lock nut 94b.
Moreover, an inlet guide roll 95 is provided at a forward top end of the dead plate 91 toward the feed and discharge zone B, as shown in
As a result, forming a complete communication circular duct with no partition plate in the movable air chamber 25 allows an effect similar to that of Example 1 to be achieved even in Example 3.
In Examples 1 to 3, provided is the waste heat recovery zone D. It goes without saying, however, that our apparatus is also applicable in the case where no waste heat recovery zone D is provided.
Further, the stationary circular duct 31 is arranged to cover the movable circular duct 21 from the upper side in Examples 1 to 3. Our apparatus, however, is also applicable in the case where the movable circular duct 21 covers the stationary circular duct 31 from the upper side as described in JP-A-4-139380.
Furthermore, preventing deterioration of the water sealing function by a bracket structure in which a position of the side wheel 5b can be adjusted by a screw jack is extremely effective in Examples 1 to 3 in which there is no sealing function of the labyrinth sealing part. The bracket structure in which a position of the side wheel 5b can be adjusted can be applied to a sintered ore cooling facility comprising a similar water sealing mechanism (JP-A-4-139380, JP-A-6-257955 and JP-A-2000-310489, for example) other than Examples 1 to 3.
In the above description, exemplified is a cooling facility for sintered ore. Our apparatus, however, may be also applicable to a cooling facility for another hot grain/lump material such as a pellet and a hot clinker.
Preferred examples have been described above with reference to the attached drawings. This disclosure, however, is not limited to the examples. It is clear that those skilled in the art can conceive a variety of modifications and revisions within a range of the technical idea described in the appended Claims. Naturally, modifications and revisions are also included in the technical range of this disclosure.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2008-150005 | Jun 2008 | JP | national |
This is a §371 of International Application No. PCT/JP2009/060816, with an international filing date of Jun. 9, 2009 (WO 2009/151131 A1, published Dec. 17, 2009), which is based on Japanese Patent Application No. 2008-150005, filed Jun. 9, 2008, the subject matter of which is incorporated by reference.
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/JP2009/060816 | 6/9/2009 | WO | 00 | 2/8/2011 |
