• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    A furnace charging device with a fixed feed channel is positioned in the center of the furnace head. A distribution spout is pivotably supported under the fixed feed channel and has a control rod attached to the spout. A driving means is provided so that the control rod which consist of two telescopic elements may be lengthened or shortened and at the same time may be rotated along with the spout as one assembly around the vertical axis of the furnace.
    公开号:SU833168A3
    申请号:SU792800889
    申请日:1979-08-15
    公开日:1981-05-23
    发明作者:Лежиль Эдуард；Мейе Пьер
    申请人:Поль Вюрт С.А. (Фирма)；
    IPC主号:
    专利说明:

    54) LOADING DEVICE OF THE MINE FURNACE
    FIELD OF THE INVENTION The invention relates to ferrous metallurgy and relates to a charging device for shaft furnaces. The closest in technical essence and the achieved result to the proposed is the loading device of the shaft furnace, which contains a vertical cylindrical chamber and a stationary loading channel located in it, rotating coaxial with the channel with a ring disk and a tray suspended on it, mechanisms of rotation of the sleeve and tray swing mechanism with a movable barbell vertically. The gutter rearrangement takes place in this device with the help of two autonomous engines, the rotational movement of which appropriately transforms into independent movements of rotation and rotation of the gutter, for this purpose they resort to using gears and transmission mechanisms, in particular, differential gears and planetary gears. These drive mechanisms must operate in such a way that the chute can be directed to any point of the smelting bed, and the feed material can be stowed along a very specific pattern and to those females to promote optimal use of the LlJ furnace. The disadvantage of the device is that due to both the channel of the gear box radial over the annular chamber in which they rotate. must be quite large, and the same applies to the radial extension of the annular disk, which shields the chamber relative to the interior of the furnace. This leads to the fact that the heat-affected surface of the furnace is relatively large, as a result, additional cooling of the chamber and the drive bodies in it with the help of the cooled inert gas cooling circuit is necessary. In this case, the cost and technical costs of manufacturing the device are large and mean a certain disadvantage when used in blast furnaces of medium and low power. The purpose of the invention is to reduce the cost of manufacture and increase reliability.
    The goal is achieved by the fact that in the device containing a vertical cylindrical chamber and stationary loading channel accommodated therein, a coaxial with a rotating channel with an annular disk and a tray suspended on it, the mechanism of rotation of the sleeve and the rolling mechanism of the tray with a movable vertical barbell are last of the two telescopic elements, the upper of which, in the form of a lead screw, is pivotally suspended on the sleeve, and the lower one in the form of a sleeve, is pivotally connected to the tray. The rotation mechanism of the pumping is made in the form of gears, suspended on coaxial drive vertical shafts and interlocking with two toothed rims, one of which is connected with the drive sleeve and the other with the driving screw of the rod. The device is equipped with a support, on which are suspended gear teeth, made in the form of a rotating ring J supported on the inner bearing fixed on the wall of the cylindrical chamber and the outer bearing supported on the drive sleeve. The lower telescopic element is connected in the upper part with a bronze nut, the internal thread of which corresponds to the external thread of the lead screw.
    The hinge suspension of the vertical bar is made in the form of a universal universal joint and is attached to a six suspended on a vertical shaft fixed in a bearing rigidly connected to the sleeve.
    The stationary loading channel and the annular disk are made with cavities connected to the coolant supply and removal systems. The inner wall cylindrical at the level of the annular disk is provided with a hollow ring; connected to the system of supply and removal of refrigerant. The lrizod node is located outside the cylindrical chamber, the gear shaft connected to the sleeve is connected to the horizontally placed worm gear drive motor, and the gear shaft of the rod spindle drive is connected to the vertical motor through a gearbox.
    FIG. 1 schematically shows the upper part of a blast furnace with the proposed charging device; in fig. 2 installation with one hopper, top view; in fig. 3 - installation with two hoppers, top view; Fig. 4 is a schematic example of a drive chute drive mechanism; in fig. 5 suspension of the control rod in the first embodiment, partial sectional view; in fig. b - control rod suspension; in fig. 7 is a cross section of a control rod suspension.
    according to the second embodiment; in fig. 8 is a device with the possibility of cooling various parts of the cooling sewer system, a sectional view; in fig. 9 is a view of the drive section of the drive unit outside the annular chamber.
    The furnace is loaded through the transfer device 1 with a vertical loading channel 2, which is adjacent to the loading chute 3. This trench can perform rotational movement around the vertical axis of the furnace, as well as rotational movement between the presented continuous lines and strokes with the help of an appropriate mechanism, which is located in the annular chamber 4 and is driven by the provided drive motor unit 5. The feed material is taken from one or more feed bins and flows depending on the position of the metering valve b at the outlet of these feed bins 7 through the connecting pipe of the valve b and the loading channel 2 to the loading chute 3.
    If two loading hoppers are provided (FIG. 3), then their respective intermediate pipes 8 are O-shaped relative to each other.
    The device with two loading bunkers is particularly suitable for large capacity furnaces. With this device, the feed hoppers work alternately, and while one of them is filled, the other is emptied.
    As in the device according to FIG. 2 and in the device according to FIG. 3, it is possible to access the drive mechanism of the loading chute 3, in particular with regard to the dismantling of the chute. With the help of a suitable lifting mechanism above the furnace, it is possible to remove all of the charging device by simply lifting it from its landing, and the loading hoppers do not interfere with this operation.
    The feed chute can also be dismantled in the usual way through a hole in the upper conical part of the blast furnace (on the hell, not shown),
    The installation of both loading hoppers 7 directly next to each other, in addition to good access to the charging device 10, is also provided. It makes good access to the load hoppers themselves with regard to backfilling them with a belt conveyor or skips.
    The loading chute 3 (Fig. 4-7) is suspended by means of two hinges 9 on two brackets x 10, which are located symmetrically relative to each other on the loading channel 2 installed around the vertical
    cylindrical rotary sleeve 11. When turning the sleeve 11 also turns the boot chute 3 around the longitudinal axis O of the furnace. In order to be able to rotate around the loading channel 2, the rotary sleeve 11 with its upper part (Fig. 7) is fixed on the annular rotary node 6, which in turn with the help of bearings
    12 is mounted on the formed by the wall 13 of the charging device stationary chassis. The swivel unit 14, and with it the slewing sleeve I, can therefore freely rotate around the loading channel 2, which is fixed to the chassis
    13 A gear ring 15 is provided for producing the rotary motion of the rotary unit 14, which together with the first drive gear 16 forms a gear train. Leading gear 16 is located on vshu 17, which is installed in the support 18 of the wall 13 of the charging device 1.
    The second movement of the loading chute 3, namely the movement of rotation around the hinge 9 between the vertical position (shown in Fig. 4 by continuous lines) and the angled position of the charge (in Fig. 4 indicated by a dotted line) is performed using a control rod 18 which is pivotally connected to the eyelet 19 on the rear of the groove 3. The control rod 18 rotates with the sleeving around the loading channel. For this purpose, it enters the annular drive chamber 4, namely, through the opening 20 in the annular disk 21, which, together with the rotary sleeve 11, forms a mechanical assembly and serves as a heat shield to shield the inner space of the annular chamber 4 ol high top of the blast furnace temperature. To make this thermal protection as efficient as possible, the gap between the rotary disk 17 and the fixed parts, in particular, the wall 13 of the charging device, is kept small without interference for the rotational movement of the disk 21.
    The control rod 18 consists of two telescopic elements, namely an element 22 in the form of a lead screw, which extends into the lower element 23 in the form of a sleeve. This sleeve has a bronze nut 24, the internal thread of which corresponds to the thread of the lead screw 22, therefore rotation of the latter, depending on the direction of rotation, causes the sleeve 23 to move up or down, and thus the corresponding rotation of the loading chute 13. Bronze nut 24 with an annular
    flange 25 (Fig. 5 and 7), which is screwed on top) the extreme part of the sleeve 23, is connected to this sleeve 23 of heat-resistant steel. This composite structure of the control rod 18 has more advantages than the simple structure with internal threads on the sleeve 23, since the need to make this sleeve of heat-resistant steel eliminates the positive properties of the bronze nut 26.
    This also facilitates the disassembly of the control rod 18, in particular the separation of the lead screw 22 from the sleeve 23, since in order to separate these
    5 elements enough to unscrew the annular flange 25 from the sleeve 23.
    To produce a rotational movement of the lead screw 22 around its axis, it is rigidly connected to gear 27, which forms a gear
    0 gear with one row of 26 teeth of a ring gear 28 with a double row of teeth, the other row of 29 teeth of which forms a gear with the second gear 30 directly
    5 next to the gear 16. The ring gear 28 is mounted with the help of rolling bearings 31 in the swivel unit 14, which, together with both the supports 12 and 31, forms a similar to the differential support 32.
    This support 32, which is very compact and has a differential effect, is one of the features of the proposed
    5 devices. In the known devices, the two are always located near each other and have separate supports in order to carry independent and superimposed movements. In contrast, the proposed dual support 32 allows
    0 significantly reduce not only the local view, but also the cost and place, in particular in height.
    Gear 30, like gear 16 ,. rigidly connected to the drive shaft 33,
    5 which is mounted coaxially inside the hollow shaft 17. The independence of the movements between shafts 17 and 33 is achieved by supporting 34 between the driving shafts 17 and 33. These two shafts 17 and 33 drive into motion independently of each other, namely with the help of the drive motor assembly 5 (Fig. 1).
    To enable the simultaneous suspension of the steering
    5 rod 18 and its rotational movement with a rotary sleeve 11 around the axis O of the furnace to perform an independent rotational movement of the lead screw 22 around its longitudinal axis; later, using the support 35, it is suspended on the rotary sleeve 11 or on the rotary node 14, which forms together with turning sleeve mechanical knot. Bearing 35 includes an overhead suspension and, therefore, stationary relative to its own axis, the bearing housing 36, together with the lead screw 22 and the top 27, forms a mechanical assembly and a shaft axle 36 that can rotate in the bearing housing 37, as well as a combination 38 rolling bearings, which consists of a combination of two tapered roller bearings, which can absorb both radial and axial forces (Fig. Or 7). The articulation point between the control rod 18 and the loading and distributing chute 3 describes arcs around the axis of rotation of the chute, when the latter is reciprocatingly about. clones between their both edges by their positions, (Figs. 4 and 5). The central angle corresponding to this arc is the maximum angle of the collar of the distribution chute 3. In order to make this joint point movement possible, the control rods 18 are rotated by a corresponding angle in the plane formed by the shaft and axis O of the furnace. The magnitude of this angle of rotation of the control rod 18 is a function of the angle of rotation of the chute and the length of the rod. FIG. The 5-turn corner of the same forehead 3 and the rod 18 are labeled CL or. FIG. 5 and 6, the first example of the suspension is shown which allows this movement of the rotation of the control rod 18. The support body 37 is mounted in the bracket 39, the free ends of which are suspended by means of the hinges 40 and 41 on the rotary assembly 14. Through this suspension the rotary movement is possible the control rod 18 around the axis defined by the hinges 40 and 41, which runs parallel to the axis of rotation of the distribution trough 3. As the gear 27 forms with the lead screw 22 a mechanical assembly this gear also performs a rotation the rota and therefore, in order for the engagement with the teeth 26 to remain correct during the rotation, it must be convex in the plane of rotation, i.e. in the plane formed by the axis of the gear 27 and the axis O of the furnace, the radius of curvature of these teeth is a function of the angle oC and it is a condition that the angle of the solution that determines this curvature, which in FIG. 5 marked “, must be larger than the angle / b, or the same with it. The passage 20 provided in the disk 21 allows the rotation of the control rod 18 to rotate, therefore its shape is not round, but has an elongation in the radial direction relative to the axis of the furnace. FIG. 7 shows a second embodiment of the suspension with the possibility of rotational movements of the control rod 18. In this case, the housing 37 of the bearing 35 is rigidly connected, for example, by means of a threaded connection with a rotating sleeve, while gear 27, which forms a mechanical assembly with the axle 36 of the bearing shaft , carries the spindle 22 with the help of a universal joint 42. Based on the location of this joint 42 (FIGS. 5 and 6), the rotational movement of the control rod 18 does not change the inclination of the gear 27, so its tooth can be straight. The method is carried out as follows: -h If both gears 16 and 30 are set in motion synchronously, the gear rims 15 and 29 also rotate at the same speed, therefore the support 31 is not operative, while the swivel unit 14 with both gears crowns 15 and 29 thanks to the support 12 yra1tsatsya. In this phase of the movement, the rotary sleeve 11, the distribution chute 3, the control rod 18, the rotary assembly 14, the gear rims 15 and 29 and the suspension of the control rod as well as its gear 27 rotate as a whole around the loading channel, and the gear gear 21 and the ring gear 26 does not perform counter-movements of the engagement. Because of this, the distribution chute 3 rotates at a constant, angle of inclination around the longitudinal axis. About the furnace, therefore, with this process of movement, the feed material is arranged in a circular manner on the smelting bed. If both gears 16 and 30 rotate at different speeds, then this difference in speed is associated with the ring gear 15 and 28, therefore, bearing 31 becomes now operational. The counter-movement between the ring gear 28 and the swivel unit 14 now counter-moves the gear between the gear 27 and the teeth 26, therefore the lead screw 22 is rotated around its own axis in one or the other. Depending on whether the tooth is ahead; the ring crown 28 is the gear crown 15 or behind him. With this flow of movement, an angular movement of the distribution chute 3 is caused. Therefore, by correctly selecting the rotational speed of both gears 16 and 30, the rotational movement of the distribution chute 3 is superimposed on a rotational movement, so that the feed material is laid on the melting bed in a spiral. It is also possible to temporarily stop the gear 16 while maintaining the rotation of the gear 30, as a result of which the distribution chute is angularly moved while the rotation around the axis of the blast furnace is stopped.
    As can be seen, the radial extent of the annular chamber 4 is determined by the dimensions of the rotary assembly 14 and the gear rims 15 and 28. If the dimensions of these elements are to some extent a function of the dimensions and power of the blast furnace, then nevertheless, considered in aggregate, are relatively small As a result, an annular chamber with a rather limited radial 4 is formed. In turn, only a small width of the annular disk 21 occurs, i.e. the surface, which is directly exposed to the heat of the furnace In addition, the effect of thermal radiation through the loading channel 2 can be reduced to a minimum, since it is possible to cool it. the wall of this loading channel 2. In order to produce such cooling, it is sufficient (Fig. 8) to provide a double wall 43., 44. as a result, a cavity 45 is created to circulate a cooling fluid, such as water. The implementation of this cooling does not cause any technical difficulties, since the loading channel 2 is stationary.
    FIG. 8 shows the inner liner 46 of the loading channel. This lining 46 consists of a material with good resistance properties to shocks that occur when the feed material falls, in order to protect the side wall of the loading channel 2 and to prevent premature wear.
    If the operating mode of the furnace is designed so that the reduced surface of the disk 21 in conjunction with the cooling of the wall of the loading channel 2 is not enough to maintain a sufficiently low temperature in the annular chamber 4, then the proposed charging device allows additional cooling of the most heat-affected surfaces disc 21 and part of the sleeves 11.
    From FIG. 8 is followed by the possible implementation of such additional cooling. In this exemplary embodiment, the feed channel 2 with an intermediate ring 47, which is provided with several inlet and outlet openings for the coolant, is connected to the wall 13. These inlet and outlet openings are distributed around the perimeter of the ring 47 in different quantities depending on the volume and need coolant flow. This ring 47 has an internal opening in which the continuation 48 of the rotary sleeve 11 rotates. The inlet and outlet channels 49 terminate in annular grooves 50 and 51 in the opening of assembly 47, where these annular grooves are provided on both sides with seals 52 to ensure tightness during installation . The disk 21 is double-walled 53, 54, as a result of which an intermediate space 55 is formed to circulate the coolant. The cooling fluid is supplied to the intermediate space 55 by means of a pipe 56, which partially intersects the extension 48 of the rotary sleeve and ends at the level of the annular grooves 50. Such a pipeline, which is only partially represented and indicated by the number 57, allows the coolant to be discharged through the annular groove 51. Of course,
    0 you can divide the cavity 55 in the disk 21 by using partitions on. compartments of an appropriate shape, for example in the form of a spiral, to thereby achieve the forced passage
    5 coolant through the entire cavity 55 ..
    The flow rate of the coolant in the cooling system of the disk 21 and the temperature of this fluid is controlled depending on the cooling needs. The simplest method is to control the working process of this cooling system using thermocouples and thermoelements and thereby automate the cooling system in order to maintain a more or less constant temperature in chamber 4. This cooling system allows
    0 connection with the relative small surface of the disk 21 and, due to the special arrangement of the drive mechanism of the distribution chute, refuse to cool the internal: Space of the chamber 4 by
    5 inert gas.
    The cooling of the disk 21 is an extreme measure and the embodiment of FIG. 8 is presented only to illustrate the possibility
    O cooling the disk 21, if such cooling becomes necessary in an exceptional case. In this regard, it is possible to indicate the beneficial effect of cooling the ring 57, which
    5 is fixed at the height of the disk 21 on the wall of the annular chamber 4. This ring 5.7 minimizes the radial extent of the moving parts, in particular the disk 21, namely due to
    0 stationary parts, in particular a ring 57, the cooling of which does not represent any technical problem 4y, since in the hollow inner space of the ring it can be simple
    5 way to make coolant circulate. The cross section of this cooling ring 57 preferably has a triangular shape, which facilitates slippage of deposited dust relative to the inside of the furnace. In addition, it is possible to provide a fastening with a variable height of the ring 57, - as a consequence, the width of the gap between the disk 21 and this ring 57 is set as desired. The lubrication of the 4 different parts of the annular chamber in the inner space occurs automatically, periodically or continuously. In particular, it is possible to provide on the rotary sleeve 11 a tank for lubricating grease with a mechanical piston pump, which is automatically driven by a gear ring. It is possible to provide a supply of grease in the lower part, sleeves 23 and perform the lower extreme part of the spindle 22 in the form of a piston, as a result, each time a certain amount of grease is squeezed out through the channel, which was observed in the inner space of this spindle 2, when the spindle is inserted to the bottom of the sleeve 23. FIG. 9 schematically shows the execution of the drive unit 5 for the automatic drive of both gears 16 and 20. The first drive system, mainly consisting of {not shown) engine and worm gear 58, provides a direct drive shaft 17 with gear 16 for the production of rotary gears. the movement of the rotary sleeve 11 and the distribution chute 3 around the vertical axis O. Second: the actuating theme / consisting of the second electric motor 59, which together with the transmission housing 60 forms a mechanical unit and is mounted above the drive -system 58 is connected through the gland by a driven shaft 17. The current is supplied to the rotating body of the engine 59. It passes through the sliding contacts 62. The output shaft 63 of the engine 59 through the gland 64 enters the inner space of the transmission body 60 and thereby leads to the movement of the dual delayed gear, due to this, the desired rotational speed is achieved. The last gear of the double gear is located on the shaft 33 and, accordingly, directly drives the gear 30, which produces the movement of the turning distribution chute. It should be noted that both the gear housing 60 and the gear housing 58 have an oil bath to ensure good lubrication. If the worm gear 58 is operative, and the motor 59 is not driven through the contacts 62, then the drive unit 59, the gearbox 60, as well as both shafts 17 and 30 rotate around the vertical axis as a whole, as a result of which both gears. 16 and 30 have the same rotational speed, and thus the loading chute 3 is set in motion with a constant inclination around the longitudinal axis O of the blast furnace. However, this rotation of the entire drive unit is superimposed to control the inclination of the loading chute by driving the motor 59 and, through a gear train in the transmission housing 60, the shaft 33 rotates in one direction or another, thereby disrupting the synchronous movement of the gears 30 and 16. Also, the slope of the distribution chute 3 is changed without rotation, while the chute is around the longitudinal axis of the furnace. by simply actuating only the engine 59, while the worm gear is 58 n It does not work, therefore only the AOR gear wheel rotates. The modeling and reproducing device 65 of the movement of the angle-swapping of the distributing force is based on the registration of the revolutions effectively performed by the engine. This simulation system consists of a miniature set of differential and glider transmissions to reproduce the actual engine speed 59. The movements thus obtained are fed to the device 66, which serves to monitor and control, either automatically or not automatically, the movements of the distribution trough. This device 66 continuously informs the operator about the angular position of the distribution trough. The rotational movement of the distribution chute around the vertical axis of the furnace is also reproduced. In this case, it is only necessary to provide a second modeling and reproducing system that reproduces the revolutions of the shaft 17. This second system is directly controlled by the worm gear 56 or the output shaft 67 of the first device 65. The stop 68 prevents the stationary contacts 62 and the device 62, 65 and 66 during rotation of the engine 59 and gearbox 6. The application of the proposed boot device provides a reduction in the cost of its manufacture in comparison with the known and ensures its reliable operation in shaft furnaces.
    权利要求:
    Claims (8)
    [1]
    1. A shaft furnace loading device containing a vertical cylindrical chamber and a stationary loading channel accommodated therein is a sleeve coaxial with it with an annular disk and a tray suspended thereon, a mechanism for rotating the sleeve and a mechanism for rolling the tray with a vertically movable rod, different in that in order to reduce the cost of its manufacture and to ensure reliable operation, the rod is made of two telescopic elements, the upper of which, in the form of a lead screw, is hingedly suspended on the sleeve,
    and the lower, in the form of a sleeve, is hingedly connected to a tray.
    [2]
    2. A device according to claim 1, characterized in that the rotation and swing mechanism is made in the form of gears suspended on coaxial drive vertical shafts and interacting with two gear wheels, one of which is connected to the drive sleeve and the other with the lead rod screw .
    [3]
    3. The device according to claim 2, characterized in that it is provided with a support on which the gear rims are hung and wired, in the form of a rotary ring, supported on the inner bearing fixed
    on the wall of the cylindrical chamber and the outer bearing supported on the drive sleeve.
    [4]
    4. A device according to Claim 1, characterized in that the lower telescopic element is connected in the upper part with a bronze nut, the internal thread of which corresponds to the external thread of the spindle.
    [5]
    5. The device according to claims 1-4, which is tied by the fact that the hinged suspension of the vertical bar is made in the form of a universal universal joint and is mounted on a gear mounted on a vertical shaft fixed in a bearing rigidly connected to the sleeve.
    [6]
    6. A device as claimed in Claims 1-5, characterized in that the stationary loading channel and the annular disk are made with cavities connected to the refrigerant supply and removal systems.
    [7]
    7. The device according to claims 1-6, characterized in that the inner wall of the cylindrical chamber on the level of the non-annular disk is provided with a hollow ring connected to the system for supplying and discharging the refrigerant.
    [8]
    8. A device as claimed in Claims 1 to 7, characterized in that the drive unit is located outside the cylindrical tube, the gear shaft connected to the sleeve is connected to a worm gear drive motor which is horizontally placed, and the drive shaft gear drive shaft is connected
    0 with a vertically placed engine through the gearbox.
    Sources of information taken into account in the examination
    1, Patent of France No. 2324737, cl. From 21 to 7/18, 1974,
    ff.
    FIG. 7
    I
    Fig.8
    类似技术:
    公开号 | 公开日 | 专利标题
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    同族专利:
    公开号 | 公开日
    FR2433722A1|1980-03-14|
    LU80112A1|1979-01-19|
    CS227672B2|1984-05-14|
    JPH0311221Y2|1991-03-19|
    ATA495679A|1982-10-15|
    AU523908B2|1982-08-19|
    JPS63167153U|1988-10-31|
    BE878113A|1979-12-03|
    NL7906153A|1980-02-19|
    BR7806954A|1980-04-22|
    GB2027860A|1980-02-27|
    UA7059A1|1995-03-31|
    NL191152C|1995-02-16|
    IT7925030D0|1979-08-09|
    CA1143152A|1983-03-22|
    ES483341A1|1980-04-01|
    FR2433722B1|1982-10-01|
    GB2027860B|1982-11-17|
    AT371148B|1983-06-10|
    DE2929204A1|1980-02-28|
    NL191152B|1994-09-16|
    AU4928679A|1980-02-21|
    US4273492A|1981-06-16|
    DE2929204C2|1987-11-26|
    IT1162769B|1987-04-01|
    JPS5528392A|1980-02-28|
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    LU91412B1|2008-01-30|2009-07-31|Wurth Paul Sa|Charging device for distributing bulk material|
    LU91565B1|2009-05-07|2010-11-08|Wurth Paul Sa|A shaft furnace charging installation having a drive mechanism for a distribution chute.|
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    LU80112A|LU80112A1|1978-08-16|1978-08-16|
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