CN1042648C - Rotary body suspension device - Google Patents

Abstract

A suspension device for rotary bodies such as rotary hoppers has on one side a metal bearing band which defines a ring-shaped rolling surface (34) and on the other side at least n metal rollers (24), n being an integer higher than 3. The n rollers (24) contact said rolling surface (34). An elastic compressible member (32), preferably a metal web provided with oblong holes (40) parallel to the rolling surface (34), is arranged below the metal bearing band so that the rolling surface is elastically deformed around the contact points (Pi) between the rollers (24) and the rolling surface (34). These elastically compressible members (32) are sized so that the elastic deformation of the rolling surface (34) is sufficient to substantially correct an unequal distribution of the weight of the rotary hopper (14) on the n rollers (24) due to slight surface irregularities of the n rollers (24).

Description

Devices for suspension of swivel bodies

The present invention relates to suspension means for suspending a weight rotating about a substantially vertical axis, such as a rotating funnel. In particular, the invention relates to devices of the type having on one side a metal moving belt forming an endless moving surface and on the other side at least n rollers, where n is an integer greater than 3, in such a way that Arrangement, that is, pressing on the moving surface to support the rotating body.

Such a device is known, for example, from US-A-4812100, in which a suspension device is described together with a rotating hopper of a shaft furnace. In this way, when a rotating funnel is charged, its weight is several hundred tons. If three support rollers are spaced apart at an angle of 120° from each other, each support roller should be sized so that each roller bears at least 1/3 of the weight of the funnel. Of course, it is very important to make the size of the rollers as small as possible. Therefore, the idea of making more than three rollers was born. However, this idea has certain problems in its practical implementation. In practice, if the funnel is supported by four rollers arranged at an angle of 90° apart from each other, it has been realized that each roller is not chosen to be able to carry 25% of the weight of the funnel, but each roller must carry at least 25% of the weight of the funnel 50%. The reason for this paradox is that the four rollers can never be strictly aligned on the same plane.

In the aforementioned document, the problem of distributing the weight of the funnel over more than three rollers is solved by providing four pairs of rollers mounted on a special suspension. Each pair of rollers is actually driven by a shaft rotatable about a radial axis, and each roller is mounted on its shaft using floating bearings mounted on springs.

The basic problem of the present invention is to propose a device of the above-mentioned type, which is much simpler in structure than that described in US-A-4812100 and which is still suitable for substantially adjusting the weight of said heavy objects in more than Uneven distribution on the three rollers.

According to the invention, this problem is solved by a compressible elastic element positioned behind the moving belt so as to elastically deform the moving surface around the point of contact between the roller and the moving surface. Furthermore, the dimensions of these elastically compressible elements are chosen so that said elastic deformation of the moving surface is sufficient to adjust substantially when the weight distribution of said weight is uneven due to small coplanar imperfections of the rollers.

The advantage of the present invention is that the suspension device for n rollers is much simpler than that described in US-A-4812100, while ensuring that the load is evenly distributed to the n rollers from the point of view of load distribution.

Said elastically compressible member may of course be a ring made of elastomer placed under the moving metal belt forming the moving surface. However, it will be appreciated that the resiliently compressible member proposed by the present invention is entirely of metal. According to a preferred embodiment of the invention, these resiliently compressible elements consist essentially of a metal strip with oblong holes parallel to the moving surface. It will be appreciated that this solution is very simple to produce, adds little cost, is maintenance-free and has excellent elastic deformation properties.

The device according to the present invention preferably comprises a very rigid support cylinder coaxial with the axis of rotation, an annular connecting flange supported by the first end surface of the support cylinder and a ring-shaped connection flange fixed on the support projection. The moving band on the edge. And the supporting cylinder has several oval long holes parallel to the moving surface near the connecting flange. When this structure is applied to a revolving funnel, the support cylinder forms a cylindrical vertical wall like a funnel. It will also be appreciated that the moving surface may be fixed either to the rotating body or to the supporting structure.

Other advantages and characteristics of the present invention will be seen from the detailed description and accompanying drawings of a preferred embodiment of the present invention; for example, a rotary funnel used as a blast furnace, wherein:

Figure 1 is a perspective view of a blast furnace (upper part) equipped with a rotating funnel mounted on a suspension device of the present invention;

Fig. 2 and Fig. 3 are used for explaining the fundamental problem of the present invention; They show respectively the plan view that has three supporting rollers device (Fig. 2) and the device (Fig. 3) with four supporting rollers;

Figures 4A and 4B are linear expansions of a suspension system with four rollers; the system in Figure 4B shows the system in Figure 4A processed in accordance with the present invention;

Fig. 5 is the vertical plane sectional view of the suspension device of the present invention of rotating funnel shown in Fig. 1;

Figure 6 explains schematically the deformation of the moving surface of a preferred embodiment of the device according to the invention with the aid of two figures.

FIG. 1 shows the upper part of a blast furnace 10 which is equipped with a charging device 12 for central charging. The charging device 12 includes an auxiliary funnel identified with reference numeral 14 . This is a rotating hopper which can be rotated about the center line 16 of the blast furnace 10 in order to avoid asymmetric feeding of the batch hopper 15 located below the auxiliary hopper 14 .

The auxiliary funnel 14 is mounted on a platform 18 supported in turn by the superstructure 20 . The superstructure 20 is placed on a furnace wall 22 of the blast furnace 10 . Funnel 14 is suspended from platform 18 by four rollers 24 mounted on platform 18 . These rollers 24 bear on an endless moving belt 26 which surrounds the funnel 14 and closely fits it.

It can also be seen from FIG. 1 that the funnel 14 comprises an upper portion formed by a cylindrical upright wall 28 and a lower portion formed by a conical upright wall 30 . The moving belt 26 is fixed at the lower edge of the cylindrical upright 28 , which edge projects slightly towards the bottom, for the connection between the cylindrical upright 28 and the conical upright 30 . In this way, when the funnel 14 of the charging device 12 of the blast furnace 10 is loaded, its weight is about several hundred tons. This weight has to be borne by the supporting rollers 24 in order to transfer the gravitational force through the platform 18 and superstructure 20 to the furnace wall 22 of the blast furnace 10 .

The basic problem of the present invention is discussed below with reference to FIGS. 2, 3 and 4A. From FIG. 2 it can be seen that three separate support rollers are distributed at 120° to each other. The intersection of the axes of rotation of these three rollers falls on the axis 16 . Obviously, in such an arrangement, when the center of gravity of the funnel falls on the axis 16, the three rollers 24 ₁ , 24 ₂ and 24 ₃ bear 1/3 of the total weight of the funnel 14 respectively. At first glance, it may be expected that in the case of Figure 3, each of the four rollers ₂₄₁ , ₂₄₂ , ₂₄₃ and ₂₄₄ should carry 1/4 of the total weight of the funnel. However, in reality this is not the case. This is because _the four contact points P ₁ , P 2 , P ₃ and P ₄ representing the possible contact of the rollers 24 ₁ , 24 ₂ , 24 ₃ and 24 ₄ with the moving belt 26 never fall on exactly the same plane. As a result, the moving surface is pressed against only three rollers. Figure 4A is a linear development of the device of Figure 3; where the only rollers in contact with the moving surface are ₂₄₁ , ₂₄₃ and ₂₄₄ . In FIG. 3 , it can be seen that the projection G of the center of gravity of the funnel 14 falls on the radius line (0, P ₄ ) with a distance "e" from the point O. The reaction force acting on the rollers is easily calculated as follows:

R ₂ =0; R ₄ =(2e/D)×P; R ₁ =R ₃ =(P/2)×(1-e/D)

In the formula: D is the diameter of the moving ring 32 .

Since the ratio e/D is usually small (in other words, the radial displacement of the center of gravity G of the funnel 14 from 0 is small), this means that the four rollers should be sized so that each roller can bear the weight of the funnel 50% of. It is also important to point out that the moving belt 26 fixed to the lower end face of a cylinder 28 with a vertical axis can be considered as the base of a beam of infinite rigidity. In other words, the moving belt 26 is virtually indeformable.

Figure 4B shows a modified version of the suspension shown in Figure 4A with four rollers according to the invention. Note that the moving belt 26 has been mounted on elastically compressible elements 32 such that the moving surface 34 of the moving belt 26 is elastically deformable around the point of contact Pi between the roller 24 _i and the moving belt 26 . The entire system consisting of the moving belt 26 and the elastically compressible elements 32 should be dimensioned more specifically so that the local elastic deformation of the moving surface 34 at the rollers 24i is substantially sufficient to be able to adjust the weight of the funnel 14 on the four rollers 24 Unequally distributed. As a result of this prearranged local deformation, the moving surface 34 at the rollers ₂₄₁ and ₂₄₃ has been bent, while in Figure 4A the reaction forces _R1 and _R3 here are both about 50% of the total funnel weight . Due to the local deformation at the rollers ₂₄₁ and ₂₄₃ , the vertical wall 28 is slightly dented. At this time, the roller ₂₄₂ is in contact with the moving surface 34 . At the same time, the weight of the funnel has been significantly redistributed among the four rollers. In other words, the element 32 makes the moving metal belt 26 sufficiently elastic to correct the effect of defects in the coplanarity of the four rollers 24i by local deformation and thus to obtain a greater weight of the funnel 14 on the four rollers 24i. good distribution.

FIG. 6 shows the insertion of the compressible belt element 32 between the moving belt 26 and the almost infinitely rigid cylindrical upstanding wall 28 . It can be seen that the compressibility of the belt 32 is obtained simply by the judicious act of perforating the cylindrical upstanding wall 28 adjacent the moving belt 26 with an oblong oblong hole 40 parallel to the moving surface 34 . The holes 40 are distributed in a rotationally symmetrical manner on the vertical wall 28 and are preferably arranged in two rows, one above the other. Please note that the upper row of elliptical long holes 40 is displaced relative to the lower row of elliptical long holes, in such a way that the upper row of holes covers the material between two adjacent holes in the lower row. The effect of this particular arrangement of oblong oblong holes 40 will be discussed below with the aid of A and B of FIGS. 6 .

In A and B of Figure 6, the element 32 is modeled by two ideal beams 34' and 42' superposed together. Beam 34' simulates moving surface 34 from a deformation point of view. The beam 42' simulates the fiber strip between the upper and lower rows of oblong holes 40. Beam 34' is pressed against beam 42' by two elastic supports 44. The resilient support is the spacer area (ie, the standing wall material) between the lower row of holes 40 . These spacing areas are directly below the upper row of holes 40, and they can be elastically deformed toward the direction of these elliptical long holes. Beam 42' rests on rigid support 46. The latter is the material of the vertical wall 28 directly below the lower row of holes 40 .

The two real beams 34' and 42' shown in A of Fig. 6 are in a non-deformed state (reaction force R=0). B of FIG. 6 shows the deformation of two real beams 34' and 42' when a large local load Rmax acts perpendicularly on the beam 34' and in line with the first rigid support 46. It can be seen that, between the supports 44, due to the presence of the first row of holes 40, the beam 34' is free to deform. Rigid support 46 simulates the almost infinitely rigid vertical wall 28 above this hole; it is virtually unaffected by this deformation. In addition, due to the function of the upper row of holes 40, the elastic supporting member 44 elastically bends under the load R. Taken together, these two deformations represent the local deformation of the moving surface at the contact point Pi of the local force R. It should be noted that a mathematical model such as the use of finite elements for such a structure with elliptical slotted holes has made it possible to describe the situation, in the case of a specific application, when a funnel of the type described above is supported by more than three When supported, the values achievable by the local elastic deformation of the moving surface 32 are very large, large enough to seriously affect the distribution of the funnel weight on the rollers. The mathematical model with the structure of the elliptical slot can also lead to certain conclusions about the size of the selected elliptical slot 40 . Considering the actual conditions related to the production of elliptical long holes, the conclusions that can be summarized are as follows:

- the shape of the hole: rectangular with rounded ends;

- The size of the hole: the length of the hole is preferably the length of the arc whose center angle is less than 10°; the height of the hole is about 1/4 of its length;

-Arrangement of the holes: two overlapping holes; the distance between two adjacent holes in the same row is about 80% of the hole length; the holes in the second row are symmetrical to the plane of symmetry of the two holes in the first row.

Those skilled in the art will be able to optimize or modify these parameters for each application and model the above-mentioned application by means of, for example, the finite element method.

Other important features of the proposed apparatus will now be described with reference to FIG. 5, which is a cross-sectional view of one corner of the funnel 14 enclosed within a circle in FIG. It can be seen that an annular connecting flange 50 is welded to the deformable element 32 . The moving belt 26 is connected to the connecting flange 50 by means of bolts. It is preferably divided into 5 annular sectors distributed at 72°. Therefore, it is never possible for two rollers to press against the same segment of the moving belt, nor for the two rollers to be at the joint between two segments. In this way, the segments of the moving belt 26 divided into n+1 pieces "transmit" the reaction forces of the rollers to the moving surface 34, which results in an advantageous effect. The groove 52 at the periphery of the flange also ensures that the moving belt segments are easily and properly positioned on the flange 50 . These segments can in fact be regarded as consumable parts that should be replaced periodically. The moving belt 26 defines a tapered moving surface 34 . The apex of the cone forming this surface is located below the moving surface and on the axis of rotation 16 . It should also be noted that the moving belt 26 is preferably of hollow section. The running surface of the roller 24 is convex in such a way as to ensure that the roller 24 makes practical point contact with the conical running surface along the contact circumference. In order to ensure the optimum force obtained by the deformable element 32, the contact circumference should coincide with the projection of the midline of the cross-section of the cylinder 28 on the moving surface.

Those skilled in the art will readily apply the teachings of the present invention to more than four rolls. In an arrangement of the type shown in Figure 1, four pairs of rollers separated at an angle of 90° from each other will preferably be used. On the platform 18 , these pairs of rollers are mounted at the four most rigid places of the platform 18 , namely at the junctions of the connection between the platform 18 and the upper structure 20 .

The suspension device of the present invention has been described above with reference to a rotating funnel. But it can also be used for other axis-rotating loads (eg, tanks, rotating conveyor chutes, rotating platforms, etc.) when more than three support rollers are used to reduce the load-bearing problems of a single roller.

Claims (14)

1, is used for hanging the suspension system of the weight that centers on a basic vertical pivot (16) rotation, this device comprises, at it metal moving belt (26) on an annular movement surface (34) is arranged on one side, have n metal rolls (24) at least at its other side, wherein n is the integer greater than 3, this n roller (24) is arranged by a kind of like this mode, promptly is pressed in described translational surface (34) and goes up to support axis (16) rotation of described rotator (14) around described basic vertical rotation, it is characterized in that:

Resiliency compressible part (32) is positioned at metal moving belt (26) back, thereby make point of contact (Pi) the on every side flexible distortion of translational surface between roller (24) and translational surface (34), the size of selected described resiliency compressible part (32), when causing the weight distribution of described weight body (14) on roller (24) inhomogeneous with box lunch because of the little defective that exists on the coplane that n roller (24) arranged, described recoverable deformation is enough to this is adjusted significantly.

2, device according to claim 1 is characterized in that described compressible elastomeric spare is made up of the metal strip (32) that has the oval slotted hole (40) that is parallel to translational surface (34).

3, device according to claim 1 is characterized in that having:

One with rotating shaft coaxle and the very big support cylinder body (28) of rigidity,

A ring-type flange connector (50) that supports by first end face of described support cylinder body (28),

A moving belt (26) that is fixed on the described supporting flang (50),

Described support cylinder body (28) is locating to have the oval slotted hole (40) parallel with translational surface near flange connector (50).

4, device according to claim 2 is characterized in that being parallel to translational surface (34) and has two row's oval slotted holes (40) at least, and wherein there is displacement in the first platoon leader hole with respect to the second platoon leader hole.

5, device according to claim 4 is characterized in that the second platoon leader hole is below the spatial vertical between the first platoon leader hole.

6, device according to claim 2, the length that it is characterized in that oval slotted hole (40) make circular arc right central angle less than 10 °.

7, device according to claim 2 is characterized in that the end of oval slotted hole (40) is a circular arc.

8, device according to claim 2 is characterized in that these oval slotted holes (40) distribute with the revolution symmetric mode around rotation axis (16).

9, device according to claim 3 is characterized in that moving belt (26) has hollow section.

10, device according to claim 3 is characterized in that moving belt (26) is divided into n+1 cyclic secter pat.

11, device according to claim 3 is characterized in that the contact circumference between moving belt (26) and the roller (24) is corresponding with the cross section projection of described support cylinder.

12, device according to claim 1 is characterized in that translational surface (34) is a conical surface, form this surperficial conial vertex and be positioned on the rotation axis, and roller (24) has the translational surface that protrudes protuberance.

13, device according to claim 1 it is characterized in that translational surface (34) is connected with article for rotation (14), and roller (24) is rigidly fixed on the support platform (18).

14,, it is characterized in that described weight is a rotatable hopper according to each described device in the claim 1 to 13.

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