• 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:
    1. LOADING DEVICE OF THE MINE OVEN, containing a drive tray, a mechanism for controlling the swing and rotation of the tray with a command organ, a vertical channel for feeding 11shkhtovyh hoppers to the furnace of materials, and the tray is installed between the branches of the fork-suspension having a fixed supporting frame, and the drive-suspension hydroelectric fork is made with the possibility of joint rotation with the tray, characterized in that, in order to increase the service life of the mechanism and facilitate the weight of the structure, the tray is provided with a mechanism With the zoom of the additional rotation of the fork and groove around the second axis and the servo drive to adjust the movement of the tray from the command body, the first hydraulic cylinder is mounted with pins on the fork of the tray and the second on a fixed frame supporting the fork. 2. The device according to claim 1, characterized in that the command body is mounted on the shaft of the plug-under-. by means of a universal joint, connected with the drive of its rotation and rotation, and provided with probes connected to this organ and through the electronic unit of the servo drive with power hydraulic cylinders. 3. The device according to paragraphs. 1 and 2, that is, it is provided with safety mechanisms in the form of elastic joints and clamps. 4. Device on PP. 1, 2 and 3, (L, characterized in that elastic joints and clamps are placed between the universal joint and the shaft. 5. The device according to claims 1, 2 and 3, characterized in that it is provided with an inner, supporting universal joint, and outer rigidly connected to the shaft, frames, on the four corners of which 4 elastic joints and clamps are placed. 4 6. The device according to claims 1, 2 and 3, is characterized in that it is provided with an intermediate frame located between the inner and outer frames, and the elastic joints and retainers are located between the diate and outer frames.
    公开号:SU1106447A3
    申请号:SU823413601
    申请日:1982-03-30
    公开日:1984-07-30
    发明作者:Лежилль Эдуард；Мэлье Пьер
    申请人:Поль Вюрт С.А. (Фирма)；
    IPC主号:
    专利说明:

    The invention relates to ferrous metallurgy, in particular to devices for loading blast furnaces.  The closest to the proposed technical essence and achievable result is the charging device of the shaft furnace, containing the drive tray, the mechanisms of the swing and control controls of the command body, the vertical channel for supplying materials from the hopper to the furnace, the tray being installed between two branches The fork has a fixed support frame, and the hydraulic suspension cylinders are driven by power cylinders, the fork-suspension is made with the possibility of joint rotation with the tray lj.  The disadvantages of this device are that the structural design and the significant mechanical effects that the weight of the chute and suspension fork exert on the command body and drive mechanism.  The purpose of the invention is to increase the service life of the mechanism and facilitate the weight of the structure.  The goal is achieved by the fact that, in the shaft kiln loading device, containing a drive chute, mechanisms of rolling control and chute rotation controls with a command organ, a vertical channel for supplying materials from charge bins to the kiln, the tray being installed between two branches of a suspension fork having fixed support frame, and driven by power cylinders fork-suspension is made with the possibility of joint rotation with the tray, the tray is equipped with a mechanism for additional rotation of the fork and groove around W The axis and the servo drive match the movement of the tray from the command body, while the first hydraulic cylinder is mounted with pins on the fork of the tray and the second is mounted on the fixed frame supporting the fork. The command body can be mounted on the fork of the suspension through a universal joint. its rotation, and rotation, and is equipped with probes connected to this organ and through the electronic unit of the servo drive with the power hydraulic cylinders, the device is equipped with safety mechanisms in the form of elastic joints and ksatorov.  Elastic joints and fittings are located between the universal joint and the shaft.  The device is equipped with an inner, supporting universal joint, and an outer, rigidly connected to the shaft, with frames, in the four corners of which elastic joints and clamps are placed.  The device is provided with an intermediate frame placed between the inner and outer frames, and elastic joints and latches are located between the intermediate and outer frames.  Fig. 1 shows schematically the head of a shaft furnace according to the first embodiment of the charging device, a vertical section along the diametral plane; FIG. 2, section A-A in FIG.  one; in FIG. 3, section BB, in FIG. 1; FIG. 4 is a section through a portion of FIG. 3 at an angle of 90 ° with respect to the plane of this figure; FIG. 5 is a section B-B in FIG.  3; FIG. 6 is a variant of the safety device shown in FIGS. 3 and 5; Fig. 7 is a diagram of the first embodiment of the servo system circuit; Fig. 8 is a second embodiment of a chute movement control mechanism; Fig, 9 is a section of GG in Fig, 8; Fig. 10 shows the actuator of the command organ and the device for driving instructive signals; in fig.  11 shows the principle of operation of the device in FIG.  10, plan view; in fig.  12 is a schematic of an embodiment of the servo system according to FIG.  eight.  In FIG. 1, reference numeral 1 denotes a blast furnace head under pressure, in which the substance to be loaded from the upper sluice (not shown) should be filled in via vertical.  feed channel 2,  located on the vertical axis O in the head of the blast furnace.  The distribution of the feed substance introduced through the channel 2 is carried out with the help of the vibration chute 3, having mainly the shape of a truncated cone.  The vibrating trough 3 is suspended between the branches (one of which 4 is visible) of the plug 5, the fence is installed in the side wall of the orus 6 of the furnace head 1 so that it can rotate around its longitudinal axis.  Regardless of this possibility of rotation of the fork 5 around the axis Ij, the vibration forehead 3 may be turned around its suspension axis X between two legs of the fork 5.  The plug 5 is installed in a hermetic manner in the wall separating the crankcase 7 of the control and the drive from the internal cavity of the furnace head 1, and the crankcase 7 is detachably mounted on the flange 8 of the housing 6.  In order to be able to rotate around the longitudinal axis y, the plug 5 is housed in a ball bearing 9 provided in the separating wall 10.  This ball bearing can be combined with a sealing device 11 to avoid dropping into the crankcase 7.  The sealing device 11 may be absent if a pressure is provided in the crankcase, approximately equal to the pressure in the internal cavity of the furnace head 1. Inside the crankcase 7 there is a command body 12 mounted on the rotating shaft 13, passing through the plug 5 and having the ability to rotate around its axis and.  The shaft is mounted so that its axis is strictly parallel to the axis of rotation X of the groove 3.  The command element 12, which is able to rotate with the shaft around axis 2, as well as around axis Y together with fork 5, therefore has the same degrees of freedom as chute 3 and vice versa.  The command body 12 is informed of the movement carried out by the chute 3.  For this purpose, a motion transmission device 14 is provided inside the plug 5, connected directly or indirectly to the axis X of rotation of the chute 3 on the one hand and, on the other hand, using the lever with the command body 12 so as to form a system in the parallelogram form which transforms the turns of the command body 12 around the axis - &  in turns of trench 3 around the X axis.  The mechanism (FIG.  1) contains the engine 15 installed outside, preferentially; on carter 7.  Two coaxial command shafts 16 and 17 penetrate from the engine 15 through ball bearings, usually glands, into the crankcase 7.  One of these command shafts, in this case the external command shaft 16, carries inside the crankcase 7 a curved guide 18 in the form of an arc of a circle, the angle of which corresponds to the double angle of the maximum incline of the groove relative to axis 0.  The toothed sector 19, which forms a rack and pinion with the gear 20, which is rigidly connected to the inner command shaft 17, is slidably supported on the concave side of the guide 18.  Between the end of the command body 12 and one of the two ends of the gear sector 19, a rotating connection is provided. Rotation of the external command shaft 16 rotates the guide 18 and the gear sector 19 around an axis parallel to the axis N of the furnace and causes a conical precessional movement of the command body 12 around the same axis with.  The movement of the command body 12 is possible due to the coordinated rotation of the fork 5 around the axis Y and the body 12 around the bsi Z, which translates the conical process movement of the body 12 exactly onto the chute 3.  The rotation of the internal command shaft 17 serves to move the toothed sector 19 and to change the angle of inclination of the command body 12 with respect to the axis t.  The command body 12 performs the command and driving functions, actuated by means of a set of levers chute 3.  In doing so, the command body 12 is subjected to strong mechanical effects.  In order to avoid these effects, the command body 12 is deprived of its driving functions in such a way that it performs an exclusively command function.  To ensure that the command body performs only command functions, it is proposed to use hydraulic cylinders for the drive mechanism for rotating the plug 5 and chute 3 instead of extracting this power from the receiving mechanisms of the command body 12.  FIG.  Figure 1 shows the first power cylinder 21, the piston rod 22 of which acts on the lever 23, which is rigidly connected to the rotating shaft 13, to which the command body 12 is connected.  The transmission device 14 is also hinged on the lever 23 so that the action of the power cylinder 21 causes the rotation of the commands of the 7th to 12th body around the axis 2 and simultaneous rotation of the groove around its axis of suspension X.  Taking into account that the end of the piston rod 22, which is hinged on the lever 23, must perform an end movement around the axis 2, the power cylinder 21 must be able to rotate around an axis parallel to the axis Z.  For this purpose, the power cylinder 21 is mounted by means of pins 24 at the rear end of the plug 5, Second cylinder 25 (FIG.  2) acts perpendicular to the first power cylinder 21 and is mounted with trunnions (not shown) on the wall of chamber 7, its rod 26 is directly hinged on the fork 5 to rotate the latter with the help of a ball bearing 9 around the Y axis.  In fact, the plug 5 is double, containing, in addition to the two branches, between which the chute 3 is suspended, two branches at the opposite end for mounting the rotating shaft 13.  FIG.  Figure 3 shows the mounting of the rotating shaft 13 between two branches 27 and 28 of the plug.  Installation details are shown only for branch 28.  The ball bearings 29 allow the shaft to rotate around an axis, while the sealing means (not allowed, allow the coolant to circulate within the entire fork 5.  The rotation of the shaft 13 around the axis is transformed by means of the levers 30 into the movement of the transmission mechanism in the form of a double fork moving inside the fork 5. To facilitate dismantling, it is preferable to make the lever 13 of several pieces, which is realized by screw 31 (Fig.  3) axially passing through the end of the shaft and providing rigidity.  Both parts, held together (item 32) with a screw 31, are predominantly provided with cheeks, each of which contains a ring of radial grooves.  The mounting of shaft 13 in branch 27 is similar to that described for branch 28.  The connection between the command body 12 and the shaft 13 is provided by a universal joint 33, allowing for some freedom of movement of the org by 12 relative to the shaft 13 and vice versa.  The universal joint 33 can have various forms, in particular the shape of a ball joint (the universal joint 33 is shown as an example. The organ 12 is mounted on a shaft 34 located in the frame 35 and allowing the rotation of the organ 12 around the axis E.  Frame 35 is installed by means of spikes 36, allowing it to rotate around a second axis, perpendicular to the Z axis.  The turns made at the level of the universal joint 33, either by the action of the engine 15, or by the action of the chute 3, are determined by a pair of probes 37 and 38, combined with a command shaft 12 and rigidly fixed on the shaft 13.  These probes, in fact, are the sensing organs of the two position sensors 39 and 40, signaling any deviation from the neutral position, a deviation that must be compensated for by a coordinated action on the power cylinders 21 and 25.  The probe 37 detects deviations by turns occurring at the level of the spikes 36, and controls the compensation of their turns, affecting the power cylinder 25.  A probe 38, which is offset by 90 ° with respect to the probe 37, similarly detects rotations carried out around the Z axis, and controls the compensation of these rotations by acting on the power cylinder 21.  FIG.  6 shows the control action performed by the sensor 40.  Such sensors are well known, they can be electrical, mechanical, hydraulic and optical.  When the action of the engine on the command body 12 or the action of the chute 3 on the shaft 13 causes or allows displacement dx from its neutral position, the position sensor 40 produces an electrical signal 1 (& x), which is a function of the difference between the actual position of the probe 38 and its neutral position.  This signal may, in addition, be positive or negative in the direction of action on the probe 38.  This signal t is sent to a proportional controller 41, for example, a PID (differential-integral proportional controller) type.  The controller 41 acts on the servo-hydraulic unit 42, containing the high-speed valve, in the hydraulic circuit of the hydraulic power cylinder.  Servo-hydraulic unit 42 establishes the hydraulic circuit of the working fluid, either in one or in another direction, following whether signal I is positive or negative.  In other words, the sign of the signal I determines the direction of movement of the piston rod 22 of the power cylinder and the direction of rotation of the groove around the axis X.  This action on the power cylinder is carried out in the opposite direction to the action that causes displacement of the AH, on the probe, and takes place until the probe again takes up its neutral position, t. e.  until signal I becomes zero.  The servo-hydraulic unit 42, moreover, is conceived in such a way as to vary the flow rate of the hydraulic working body in the power cylinder circuit depending on the amplitude, t. e.  the speed of rotation around the axis of the groove, reported by the piston, is a function of the value of U X.  A control circuit similar to the control circuit in FIG.  6, is combined with the probe 37 to control the power cylinder 25 and the rotation of chute 3 around the axis Y.  Probes 37 and 38 are therefore experiencing the double action of the command body 12 and of the chute 3 through the intermediation of the plug 5 and the shaft 13.  On the part of the command body 12, the probes 37 and 38 receive instructive data through the action of the propeller. From the side of the gutter 3, the probes 37 and 38 continuously receive information regarding the actual position of this gutter.  As long as the actual position data does not comply with the instructive data, the sensors 39 and 40 support signals 1 for actuating the corresponding power cylinders in order to reduce the signals I.  Consequently, there is an auto-adjustment of the position or orientation of the groove 3 in terms of the position prescribed by the engine 15.  If a damage occurs at the input or at the output of the command body, for example, electrical damage to the engine 15 or damage to the hydraulic circuits of the power hydraulic cylinders, the servo system is more than able to cancel the comp.  by sensing signal 1 so that AH tends to increase in an uncontrolled manner.  To prevent such situations, fuse sensors 43 and 44 are located near sensors 39 and 40, which are also position sensors similar to sensors 39 and 40.  Sensors 43 and 44 turn on the signal when U X exceeds a predetermined absolute value, a threshold that immediately blocks the hydraulic circuit and double charger.  In order to avoid, despite the presence of sensors 43 and 44, any risk of destruction due to a delayed response, the duration of which is the time elapsing between the action on sensors 43 and 44 and the result of their operation, an additional safety device is provided, the first embodiment of which is shown on FIG.  3 and 5, and the second in FIG.  6  According to the first embodiment (FIG.  3 and 5) a hinge 33 is provided inside the frame 45, inside the corresponding frame 46, mounted on the rotating shaft 13.  The frames 45 and 46 are held together by only four pairs of elastic locks 47 provided at their four corners.  Each of these fixators contains, for example, a pair of plates 48 and 49 superimposed on one and the other side of the frames 45 and 46 in such a way as to block their separation.  The plates 48 and 49 are held in this arrangement as shown in FIG.  3 by the action of two springs 50 and 51, which are powerful enough to. to maintain the configuration shown in FIG. H and 5.  However, when an extreme load appears on one of the two frames 45 and 46, and the other of them cannot follow the movement caused by this load, one of the plates 48 and 49 is inferior to the action of the corresponding spring, and the frames 45 and 46 can completely diverge. in relation to 5 to another without risk of destruction.  For example, when due to damage in the hydraulic circuit, such as leakage, the corresponding ram is no longer able to maintain the position of the chute in accordance with the instructive signals, the latter, under the action of its own weight, tends to tilt into a vertical position and drag the command body 12, which itself It lives by the engine.  Thus, the command 12 and its drive mechanism is not able to withstand the load exerted by chute 3, and in the absence of a safety system, severe destruction occurs.  On the contrary, with such a system, in the event of such damage, a simple disconnection of the two frames 45 and 46 occurs, which can then be easily re-inserted into place.  FIG.  6 shows a second embodiment of the safety device.  According to this embodiment, the frame 52, carrying the universal joint 33 with the command body 12, is held in the outer frame 53 rigidly fixed on the rotatable shaft 13 by means of an elastic cardan clamp. For this purpose it is provided. an intermediate frame 54 placed between the frames and 53, the inner frame 52 can rotate around the axis 55, corresponding to the Z axis, inside the intermediate frame 54, while the latter rotates inside the outer frame 53 around the axis 56, perpendicular to the axis 55.  This design is held together by a series of elastic clamps similar to clamps 47 with plates and springs (Figs. 3 and 5). Two clamps 57 and 58 hold the inner frame 52 relative to the intermediate frame 54 and prevent rotation around the axis 55, Two Other elastic latches 59 and 60 prevent rotation of the intermediate frame 54 around the axis 56 inside the outer frame 53. As well as according to the previous version, the latches are inferior to n by the action of normal force and allow the different frames to move apart around the axes 55 and / or 56, whilerem as according to the embodiment of FIG.  3 and 5, the extension causes a complete release of the inner frame 45 relative to the outer frame 46 according to the embodiment of FIG. 5, the structure remains held together due to the presence of the axes 55 and 56 of rotation.  Indeed, even in the case of a general disconnect, t, e, disconnecting the inner frame 52 with respect to the intermediate frame 54 and disconnecting the latter with respect to the outer frame 53, a simple restoration of its structure: through appropriate manual rotation of the different frames as long as they are held elastic locks, always remains possible.  It is possible to provide other safety systems that perform the same functions.  For example, instead of a safety system between the command body 12 and the plug 5, it is possible to provide a safety system between the command body 12 and its driver. mechanism.  Such a safety system may, for example, be formed by a friction clutch at the level of the command shafts 16 or 7 or between them and their corresponding engine, Fig.  8-11 illustrate the second embodiment when the command body and its factory mechanism remain completely independent of the suspension device of the chute 3.  The elements corresponding to the elements of the previous embodiment are denoted by the same numbers.  According to this embodiment, the angular position of the groove 3 is constantly monitored using two sensors 61 and 62.  The slider 61 determines the actual angular position of the trough relative to the X axis and transmits signals proportional to the amplitude of the rotation of the lever 23 around the Z axis, t. e.  turns of the gutter 3 around the X axis.  Sensor 62 also detects movements around axis Y and excites and transmits signals proportional to the amplitude of rotation of plug 5 and chute 3 around axis Y.  FIG.  10 and 11, a command body 63 is shown which can be installed at a suitable place, for example, in the engine room, and is actuated by the appropriate driving mechanism 64.  The command element 63 is mounted on the corresponding frame 65 by means of a universal joint, as opposed to the universal joint 66, which allows the command body 63 to rotate around two X axes.  Y /, perpendicular to each other and corresponding respectively to the axes X and Y of rotation of the trough in 1-o / 1 chke.  111 The movement of the command body 63, for example, conical precession, giving instructions for the movement of the chute in the form of instructive signals, this movement represents respectively the angular movements of the command body 63 around the X and Y axes in the cardan 66.  These angular movements of the organ are determined by two sensors 67 and 68 which correspond to sensors 61 and 62 and co-control cobTBeTCTBeHHO turn around the axes X j and Y |.  FIG.  12 is a mnemonic diagram illustrating the relationship between the device in FIG.  9, which provides indications, and the device in FIG.  8, which should perform them.  The command chain is combined with the power cylinder 21 to rotate around the X axis. .  A similar circuit is provided for actuating the ram to rotate about the y-axis.  Suppose that the command authority 63 is rotated around its axis of rotation X by an angle oi.  This is an instructive value for the chute, t. e.  the latter should occupy the inclined position of the axis relative to the vertical axis 0.  This rotation of the command organ 63 around the X axis is noted by a sensor 67, which excites an electrical signal f (ot), a function of amplitude and direction of rotation.  Suppose that at the moment when the command body is in the required position, the chute will be tilted at an angle p relative to axis 0.  This position is measured by a sensor 61, which detects the positions and the rotation about the x axis.  This sensor therefore produces an I f (and) signal which represents the actual position of the chute.  Signals emitted by sensors 61 and 67 are sent to controller 69, similar to controller 41 in FIG.  7  This controller compares the signal emitted by both sensors 61 and 67 and excites correction signals depending on this comparison.  If by chance the angle ot is equal to the angle jb, the signals f (c () and I f (|) are equal and the controller 69 excites no signal.  In contrast, if | i is different from the otv. A correction signal, excited by the regulator 69, is applied to the servo-hydraulic actuator 70, which determines the direction of circulation of the sub-hydraulic working fluid of the hydraulic cylinder 21 depending on the sign of the corrective signals.  The piston of the power cylinder 21 moves, therefore, to one side or the other, depending on whether the correction signals are positive or negative.  This command lasts until the angle becomes equal to the angle “6” and the correction signals become zero.  As with the previous embodiment, the servohydraulic actuator 70 also determines the flow rate of the hydraulic working fluid, depending on the amplitude of the correction signals.  When the command body 63 is driven into a circular conical precessional motion, at the level of the universal joint 66, constant turns are made around two axes X and Y.  These constant turns actuated, therefore permanently, hydraulic chains combined with two power cylinders 21 and 25 so that the same turns were carried out around axes X and Y.  Considering that according to the embodiment shown in FIG.  8 and 10, the command organ is separated from the gutter suspension system; it is not necessary to provide safety devices to prevent the risk of destruction in case of damage in the hydraulic circuit or in the drive system of the command organ.


    FIG. 2
    1106447
    13 Z
    fig.c
    28
    13
    ifl S O 11 2S L ,,, A:
    (rig. 3
    FIG. ten
    67
    66
    ev
    权利要求:
    Claims (6)
    [1]
    1. LOADING DEVICE OF A SHAFT FURNACE, containing a drive tray, a mechanism for controlling the swing and rotation of the tray with a command body, a vertical channel for feeding materials from the hoppers into the furnace, the tray installed between two branches of a fork-suspension device with a fixed supporting frame, and driven by power hydraulic cylinders, the suspension fork is made to rotate jointly with the tray, characterized in that, in order to increase the service life of the mechanism and lighten the weight of the structure, the tray is equipped with a mechanism ohms of additional rotation of the fork and the chute around the second axis and a servo-driver for coordinating the movement of the tray from the command body, while the first hydraulic cylinder is mounted with pins on the fork of the tray suspension, and the second on a fixed frame supporting the fork.
    [2]
    2. The device according to p. ^ Characterized in that the command authority is installed on ; to the fork-suspension shaft by means of a universal joint, connected to the drive of its rotation and rotation and equipped with probes connected to this body and through an electronic servo drive unit with power hydraulic cylinders.
    [3]
    3. The device according to paragraphs. 1 and 2, characterized in that it is equipped with safety mechanisms in the form of elastic joints and clamps.
    [4]
    4. The device according to paragraphs. 1, 2 and 3, characterized in that the elastic joints and retainers are placed between the universal joint and the shaft.
    [5]
    5. The device according to paragraphs. 1, 2 and 3, characterized in that it is provided with an internal supporting universal joint and an external rigidly connected to the shaft, frames, in the four corners of which are placed elastic joints and clamps.
    [6]
    6. The device according to paragraphs. 1, 2 and 3, characterized in that it is provided with an intermediate frame located between the inner and outer frames, and elastic joints and latches are located between the intermediate and outer frames.
    类似技术:
    公开号 | 公开日 | 专利标题
    SU1106447A3|1984-07-30|Shaft furnace charging arrangement
    CA2589314C|2014-04-08|Device for distributing material into a furnace
    SU833167A3|1981-05-23|Shaft furnace loading device
    US3814403A|1974-06-04|Drive for furnace charge distribution apparatus
    US4514129A|1985-04-30|Furnace charging installation
    SU576969A3|1977-10-15|Charge distributor of blast furnace loading apparatus
    CA1173241A|1984-08-28|Process for actuating an oscillating spout in anenclosure under pressure, apparatus for theperformance of this process and charging installation for a shaft furnace equipped with such an apparatus
    PT1613895E|2007-12-31|A furnace and its method of operation
    US4820105A|1989-04-11|Apparatus for charging a shaft furnace
    US4273492A|1981-06-16|Charging device for shaft furnaces
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    RU2542954C2|2015-02-27|Loose material distribution device with distribution spout supported by cardan suspension
    RU2228364C2|2004-05-10|Device for distributing loose materials during loading
    US5299900A|1994-04-05|Installation for charging a shaft furnace
    US20040200348A1|2004-10-14|System for directional angle aiming of a weapon
    US4032024A|1977-06-28|Apparatus for distribution of charge material in shaft furnaces, particularly high pressure blast furnaces
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    SU1493113A3|1989-07-07|Charging arrangement for shaft furnace
    RU2103376C1|1998-01-27|Charge distributor for charging apparatus of blast furnace
    KR890001443B1|1989-05-03|Tilt drive for metallurgical vessels
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    KR20010100003A|2001-11-09|Bell and hopper for a shaft furnaces
    SU1749016A1|1992-07-23|Manipulator
    CN88101374A|1988-10-05|Proofread and correct the method and apparatus of decline passway in the shaft furnace feeding equipment
    SU727228A1|1980-04-15|Ore disintegrating mill
    同族专利:
    公开号 | 公开日
    US4493600A|1985-01-15|
    ZA821571B|1983-01-26|
    CA1173240A|1984-08-28|
    AU545919B2|1985-08-08|
    EP0065084A1|1982-11-24|
    UA7062A1|1995-03-31|
    CS262408B2|1989-03-14|
    DE3261667D1|1985-02-07|
    SU1138038A3|1985-01-30|
    EP0065084B1|1984-12-27|
    LU83370A1|1983-03-24|
    IN157546B|1986-04-19|
    JPH0416523B2|1992-03-24|
    JPS57192208A|1982-11-26|
    AU8164182A|1982-11-25|
    AT10949T|1985-01-15|
    UA7060A1|1995-03-31|
    KR890002651B1|1989-07-22|
    CS216182A2|1988-08-16|
    BR8202579A|1983-04-19|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE2104116A1|1971-01-29|1972-08-10|Demag Ag, 4100 Duisburg|Blast-furnace burden distributor - allows dumping at any point across furnace|
    LU77547A1|1977-06-16|1977-09-19|
    JPS5546347A|1978-09-27|1980-04-01|Ishikawajima Harima Heavy Ind|Raw material distributor for vertical furnace|
    JPS5746545Y2|1978-12-23|1982-10-13|
    JPS5671783A|1979-11-13|1981-06-15|Ishikawajima Harima Heavy Ind|Stock distributor for vertical furnace|LU84303A1|1982-07-28|1984-03-22|Wurth Paul Sa|METHOD AND DEVICE FOR CONTROLLING THE MOVEMENT OF AN OSCILLATING CHUTE AND APPLICATION TO A LOADING INSTALLATION OF A TANK OVEN|
    LU87341A1|1988-09-22|1990-04-06|Wurth Paul Sa|LOADING SYSTEM FOR A TANK OVEN|
    LU87938A1|1991-05-15|1992-12-15|Wurth Paul Sa|LOADING SYSTEM FOR A TANK OVEN|
    LU90433B1|1999-09-03|2001-03-05|Wurth Paul Sa|Bulk material distribution device with rotating chute - variable tilt angle|
    DE10334417A1|2003-06-20|2005-01-05|Z & J Technologies Gmbh|Furnace head or gout closure|
    LU91683B1|2010-04-22|2011-10-24|Wurth Paul Sa|Device for distributing bulk material with a distribution spout supported by a cardan suspension|
    JP4667528B1|2010-05-10|2011-04-13|英生 住野|Dehumidification shape retainer for shoes and manufacturing method thereof|
    LU92494B1|2014-07-07|2016-01-08|Wurth Paul Sa|DEVICE FOR LOCKING THE CHUTE ON THE ENDS OF THE TRUNKS, IN A TANK OVEN LOADING SYSTEM|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    LU83370A|LU83370A1|1981-05-18|1981-05-18|DEVICE FOR CONTROLLING THE MOVEMENT OF AN OSCILLATING CHUTE AND INSTALLATION FOR LOADING A TANK OVEN EQUIPPED WITH SUCH A DEVICE|
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