JPS594225B2 - Twin Belt Reinforcement Belt Adjustment - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a belt steering and tensioning device for synchronously and symmetrically steering and tensioning casting pellets for use with wide twin belt continuous casting equipment.

Twin belt casting equipment includes a pair of wide, thin metal casting belts that form the top and bottom surfaces of the casting area within which the hot water is confined and solidified.

A twin belt type continuous casting device is disclosed in US Pat. No. 264, for example.
No. 0235, No. 2904860, No. 303634
No. 8, No. 3041686, No. 3123874,
Same No. 3142873, Same No. 3167830, Same No. 3
228072 and 3310849.

In recent years, as it has become desirable to produce castings with greater precision in length and width, particularly in length, the operational requirements for this type of casting equipment have also become more stringent.

According to the present invention, the width and overall size of the casting apparatus can be increased compared to conventional similar apparatuses.

In a twin-belt casting machine, the upper and lower casting belts support one main roll of the belts and rotate around the circumference of the upper and lower carriage assemblies of the two cantilevered beams. It looks like this.

These main rolls are used to drive, steer and tension the casting belt.

The advantage of the invention stems from the fact that the same roll can be used for tensioning and steering the belt.

A rigid squaring shaft passes through a hollow tensioning and steering roll, tightly aligned and rigidly secured at each end of the roll to a pair of torque arms.

The torque arms provide synchronized and symmetrical steering and tensioning motion of the tensioning and steering rolls and are interlocked with the dual tensioning thrust device and the dual steering device.

Only two large diameter main rolls, one for belt drive and one for belt tensioning and steering, are located at each end of each carriage assembly.

A symmetrical oblong belt path is thus formed and a large tension force is applied to the casting belt to provide a wide mold of the correct shape under operating conditions.

Due to the advantageous geometrical arrangement of the components of the casting belt steering and tensioning device according to the invention, the casting belt is always subjected to a tensioning force that is directly proportional to the fluid pressure of the belt tensioning thrust cylinder or hydraulic cylinder.

Additionally, a preload device eliminates pivot backlash and ensures accurate steering.

Mechanical gains are also contemplated such that the tension thrust force applied to the tension and steering rolls is greater than the thrust force provided by the dual thrust device.

Another advantage of the present invention is that synchronized skew movements of equal magnitude and opposite direction are applied to the pivots of one or two torque arms mounted at opposite ends of the squaring shaft in close condylar relation to each other. This is because the skew movement of the roll is carried out about a predetermined point by means of an axial thrust device, thus providing a symmetrical skew movement of the roll itself.

Each end of the tensioning and steering roll is moved individually at a time to move the axis of the roll relative to the axis of the squaring shaft and set the clearance of the roll's circumference from the pass line of the casting to the desired value. It can be adjusted to

This adjustment is effected by a sleeve associated with the squaring shaft and a single bearing located within the hollow interior of the roll.

Tension-cum-steering roll and scareifg for convenient repair°
It is also possible to construct the assembly consisting of the shaft and the shaft as one unit that can be installed and removed once.

Other features and advantages of the invention will become more apparent from the detailed description of the illustrated embodiments.

In a continuous casting apparatus 10 according to one embodiment of the invention, hot water is supplied to the upstream or inlet end of the continuous casting apparatus between upper and lower flexible endless casting bells 12,14.

The hot water solidifies in the casting zone C (see FIG. 2) defined by 14 spaced apart parallel surfaces on the upper and lower casting belts.

The two casting bells (12, 14) are supported and driven by an upper carriage assembly U and a lower carriage assembly L (see FIGS. 1 and 2).

The carriage assemblies U, L are cantilevered from the main frame 23 as shown in FIG.

In this specification, the side of the carriage assemblies U and L on the main frame 23 side will be referred to as the "inner edge side" and the other side will be referred to as the "outer edge side".

The upper carriage assembly U has two main pulley rolls 16.1
8 (see FIG. 2), a casting belt 12 is placed over them and rotated in the direction of the arrow.

One roll 16 is located near the inlet end of the casting apparatus 100.
is the upstream roll or nip roll, the other roll 1
8 will be referred to as a downstream roll or a tension/steering roll.

Similarly, the lower carriage assembly has an upstream roll (or nip roll) 20 and a downstream roll 22 over which the lower casting belt 14 is adapted to rotate.

upper and lower carriage assemblies for synchronously driving casting bells 12, 14;
25 and a mechanically synchronized drive 26 by a drive motor (not shown).

During the casting operation, the upper carriage assembly U is supported on the lower carriage assembly through four corner support points and one cage spacer.

The thickness of the mold between the opposing casting surfaces of casting bells N2, 14 and hence the thickness of the sheet produced is determined by the exact thickness of those four gauge spacers.

Two closely-fitting side dams 28 (only one shown in FIG. 2) are interposed between the opposing casting surfaces of the casting belt 12 and 140 and are guided by a side dam guide assembly 30 to control the casting apparatus 10. The width of the sheet is determined by wrapping both sides of the sheet to be cast at the nip side, that is, the upstream end.

These two side dams 28 are connected to the lower driven casting belt 1.
be driven by frictional contact with 4.

The two opposing casting surfaces of the side dam 28 are the upper and lower casting bells N2, 140, together with the two opposing casting surfaces of the moving casting C 4.
form two synchronized casting surfaces.

In order to cast metal castings accurately and with excellent surface quality, the two casting bells (12, 14) are, for example, 100 inches (approx.
The entire width of the casting belt, which may be greater than or equal to 54 m), shall be held under uniform, strong tension.

These cast belts 12,14 are relatively thin metal belts, for example steel belts, and require a high total tension to achieve the desired effect.

Also, the casting bells N2,14 must normally be steered so as to be centered and maintained in the desired operating position on the carriage assemblies U,L.

A device for tensioning and steering the lower casting belt 14 on the lower carriage assembly U will be described below, although it will be understood that a similar casting belt tensioning and steering device can also be provided on the upper carriage assembly.

The downstream roll or tensioning and steering roll 22 has a hollow configuration to maintain a properly set and moderate tension on the lower carriage assembly and has an inner torque arm 35 (sixth
(see figure) and the outer edge torque arm 36 (see figures 10 and 11).
It is concentrically attached to a rigid torque tube squaring shaft 34 which is rigidly attached to the torque tube squaring shaft 34 (see FIG. 13).

The torque tube squaring shaft 34 has an inner torque arm 35 (FIG. 6) and an outer torque arm 36.
(Fig. 10, Fig. 11, Fig. 13).

The torque arms 35, 36 are each pivotally connected to the frame 38 of the lower carriage assembly by inner pivots 39 (FIG. 8) and 40 (FIGS. 12 and 13).

A pivotally mounted torque tube squaring shaft 34 moves the torque arms 35, 36 so that the torque arms 35, 36 always have a constant movement and are always in the same relative position with respect to the frame 38. They serve to maintain precise parallel positions with respect to each other.

Therefore, the inner and outer edges of the belt 14 always move the same distance.

Since the cut tube squaring shaft 34 is passed inside the hollow downstream tensioning and steering roll 22, a symmetrical steering device and a symmetrical tensioning device are connected to the same downstream tensioning and steering roll 22. Since they can be mounted together, space inside the carriage assembly and U is greatly saved.

The torque arms 35, 36 and the squaring shaft 34 tension the cast belt 14 by means of a moderately predictable and symmetrical force application device that operates throughout the entire range of the belt tensioning stroke. is energized in a direction that makes it tense.

The symmetrical force applying device can be a pair of matched coil springs or air springs adjusted by screws.

In this embodiment, the symmetrical force application device consists of an inner hydraulic cylinder 41 and an outer hydraulic cylinder 42 (FIG. 4) installed at both ends of the squaring shaft assemblies 34, 35, and 36, with each cylinder A tip 45 of the rod 44 is pivotally connected to the carriage frame 38 by a U-link pin 46.

The outer hydraulic cylinder 42 of the tensioning and steering roll assembly is attached to the torque arm 36 and cylinder support cap 50 by a trunnion 48.

The inner hydraulic cylinder 41 of the tensioning and steering roll assembly is attached to the torque arm 35 and cylinder support cap and axial thrust member 51 by a trunnion 48.

A squaring shaft 34, a torque arm 35, 36, and a torque arm bearing cap 52 (FIG. 3) are used to precisely steer and guide the casting belt 14 over the rolls 20, 22.
, the tensioning and steering roll 22 with the cylinder support cap 50°51 and the hydraulic cylinder 4L42e is mounted on an eccentric bearing 39.
(FIG. 8) and 40 (FIGS. 12 and 13) in opposite directions, they are symmetrically inclined in a plane perpendicular to the plane of the movable mold C.

When the tensioning/steering roll 22 is symmetrically obliquely moved with respect to the nip roll 20 in this manner, the approach angle of the casting belt 14 to the tensioning/steering roll 22 and the nip roll 20 is changed, and a wide casting belt 14 is formed. It is precisely steered and guided on the rolls 20, 22.

Next, a detailed explanation will be given of the steering device which rotates the eccentric pivots 39 and 40v in opposite directions to symmetrically obliquely move the tensioning and steering roll assembly.

The center distance between the nip roll 20 and the tensioning/steering roll 22 is adjusted to the maximum left and right from all positions of the tensioning/steering roll assembly and from the neutral skew position to optimally tension and steer the casting belt 14. It is maintained across the entire width of the rolls 20, 220 for all steering conditions up to the skew position.

Scaling shaft 34. 2 torque arms 35
．． 36 and cap 50.51 and the rigid connection with high torque transmission capacity between the squaring shaft 34 and the torque arm 35.36 by means of a plurality of cap screws 54 under any operating conditions. Even though substantial tension differences occur along the width of the casting belt 140, the center distance is maintained exactly at the desired value throughout the entire width of the casting belt 14.

A squaring shaft 34 around which the tensioning and steering roll 22 freely rotates is mounted on an eccentric sleeve 57 (FIG. 4) mounted on the shaft 34.
It is supported by several large diameter wear bearings 56 (FIG. 4) and is designed to carry the radial loads due to the weight of the metal product, the weight of the roll assembly, and the tension of the casting belt.

One of the wear-resistant bearings 56 can also be used as a two-way homogeneous axial thrust bearing that receives the axial thrust force generated between the tensioning and steering roll 22 and the squaring shaft 34.

It is then desirable to use a wear bearing 56 located near the centering skew thrust assembly 104 as the axial bearing.

The wear-resistant bearing 56 includes a cooperating seal member and is sealed by a single seal 58 to prevent ingress of liquid coolant and foreign matter.

Lubricant is supplied to the wear bearing 56 through a passageway 60 (FIG. 4) and is retained within the wear bearing 56 by an internal seal 61 with a cooperating seal member.

The tension/steering roll 22 must be assembled to the tip of the torque arm 35, 3i squaring shaft 34 with a retaining screw 54.
6, is attached to the eccentric sleeve 57 and the seal/lubricant oil retaining member.

The torque arms 35, 36 can be rigidly attached to the end face of the squaring shaft 34 in precise relative positions by pre-machined axial reference stop surfaces F, G.

Scaling shaft 34 and torque arm 35.36
and the other auxiliary members mentioned above.
The connection of the radial joint 64 is very important in order to prevent slack between the squaring shaft 34 and the torque arms 35, 36 which are also connected to each other when large balancing torques are transmitted to the shaft assembly. It has been firmly established.

As an example, the connection of the joint portion 64 can be made by tightening the cap screw 54 described above to generate a substantial compressive frictional force, thereby making the connection strong enough to withstand strong torsional forces.

The cylinder support cap 50 on the outer edge side is attached to the hydraulic cylinder 42
a pair of spaced apart plates 66 extending above and below the
(Fig. 3, Fig. 13)
is firmly connected to.

The support cap and axial thrust member 51 on the inner edge side is connected to the inner edge side torque arm 35 by a pair of spaced apart plates 67 (FIGS. 3 and 6) extending above and below the hydraulic cylinder 41. is firmly connected to.

Due to the solid structure of the squaring shaft 34 and torque arms 35 and 36 described above, the tensioning and steering roll assembly can be disassembled and reassembled accurately. the relative position of the torque arm 35.36 and the full width of the nip roll 20 and the tensioning and steering roll 22 of said roll 20.2.
Be able to accurately maintain the center distance between 20 and 20.

The belt tension is proportional to the hydraulic pressure in g. Preferably, the thrust line of action 140 (see FIG. 15) of each hydraulic cylinder 41, 420 and the eccentric axis 39 in each torque arm 35, 36 from the axis of the trunnion 48. The angular relationship between the radius R2 and the direction of the belt tension exerted by the cast belt 14 and the eccentric axis 39 in each torque arm 35, 36 on which the belt tension is applied is It is desirable that the angular relationship between the relatively small radius R to the axis of the roll 20 to be made equal to y, so that the mechanical gain based on the same effective leverage is the same as that of the belt tensioning and steering rolls. 22 is provided to the hydraulic cylinders 41, 42 throughout the entire range of movement.

Therefore, in the normal belt length range, the hydraulic cylinders 41 and 42 located at both ends of the squaring shaft 71340 tension the belt in proportion to the constantly maintained working hydraulic pressure, regardless of the belt length. It is also provided to the steering roll 22.

Therefore, within normal operating ranges, the belt tensioning mechanism can accommodate casting belts of different lengths during operation of the continuous casting apparatus, and the belt tensioning force exerted by the tensioning and steering roll 22 will vary depending on the length of the casting belt. Hydraulic cylinder 41.4, regardless of belt length fluctuations, even when the belt length fluctuates significantly.
20 It is almost directly proportional to the hydraulic pressure.

This means that the cast belt can still be used even when the length of the cast belt increases with use.

Additionally, the approximately constant mechanical gain provided by the belt tensioning mechanism described above means that the casting belt may be new or fully stretched, short or long, regardless of the continuous use of hydraulic pressure. This means that it can be assumed that an appropriate tension is always generated, regardless of the

In conventional casting equipment that uses toggle action, when the casting belt stretches, the toggle often moves closer to the over-center position; Although greater tension forces are generated than in the case of belts, in the casting apparatus according to the invention the tension forces on the belt are always equal to or less for a given hydraulic pressure, regardless of whether the belt is stretched or not. is g
It is a constant value.

The mechanical gain based on this leverage and the preloading described below results in y equal cylinder force 41.420 thrust forces being applied to both ends of the squaring shear 71340, which thrust forces approximately equal effective belt tension. converted into power.

In other words, the desired symmetrical belt tensioning action is provided at both ends of the tensioning and steering roll 220.

The preload mechanism eliminates backlash and achieves precise steering and mechanical gain.The axis of the 420 trunnion 48 is the first
As can be seen from FIGS. 3 and 15, the lower tensioning and steering roll 22 is intentionally offset above the axis of the squaring shaft 34 (R2>R construction).

Also, although not shown in the drawing, the upper carriage assembly U
The axis of the hydraulic cylinder 41.degree. 420 is intentionally offset below the axis of the squaring shaft 34 of the upper tensioning and steering roll 18.

Line of action of thrust force on hydraulic cylinders 41, 420 1400
Since the radius is relatively large, the thrust force will be multiplied compared to the tension force exerted by the tensioned belt along radius R1.

The installation described above will depend on the position of the hydraulic cylinder 41°42
In addition to the fact that the thrust force of the cylinder 4 is multiplied,
Some of the force exerted by 1,42 is applied to eccentric pivot 39,40 as a preload force.

Eccentric shafts 39, 40 and associated eccentric bushings 69, 70, 7N (Figs. 18, 12) and other weights of the centering bushing assembly 72 and tensioning roll assemblies associated with eccentric shafts 39, 40. Since the recessed members are preloaded in this way, any buckling experienced by the eccentric pivots 39, 40 and their associated bushing members is eliminated.

Therefore, when the hydraulic cylinders 41, 42 are located in the selected position with respect to the torque arms 35, 36 and the cylinder caps si, so, the eccentric pivots 39, 40
0 Since the specific load area is moderately preloaded, the effects of mechanical component tolerances are removed, mechanical hysteresis is prevented, and precise steering is achieved.

As shown in FIG. 14, two eccentric pivots 39.40 provide a symmetrical and synchronized steering action to the tensioning and steering rolls.
When rotated synchronously in the opposite direction, the tension and steering roll 22
is subjected to a controlled symmetrical oblique action in a plane perpendicular to the casting surface C of the metal product being cast.

Each eccentric pivot 39,40 has a large diameter concentric shaft portion A, a small diameter concentric shaft portion B, and the shaft portion A.

Concentric portion B is eccentric with respect to B and has a smaller diameter than concentric shaft portion A.
It has a central shaft portion E with a larger diameter.

As can be seen from FIGS. 15 and 15A, both ends of the tension/steering roll 22 are moved up to ±1/8 (about o, o 3175) from the neutral steering position by the eccentric central shaft portion E.
cm) Can be moved diagonally.

Eccentric axis 39.400 Eccentric The central axis portion E has an eccentricity of approximately 1/2 (approximately 0.127 cm) with respect to the shaft portions A and B, and as shown in the figure, the tension and steering roll 22 Approximately 10 degrees above and below the neutral position each time the skew amount is achieved.
It can be rotated.

Torque arms 35, 36 and bearing cap 52 (eighth
12) is assembled by a single spherical centering bushing assembly 72 seated on an eccentric central shaft portion E with an eccentric pivot 39.400.

A pair of sealing members 74 (FIGS. 8 and 12) are assembled with each torque arm 35, 36 and bearing cap 52 to form an enclosure for the bushing assembly 72 and provide liquid coolant to the bushing assembly 72. to prevent foreign matter from entering.

The eccentric pivots 39, 40 are lubricated by lubricating fittings 73 to prevent wear and tear on associated parts and the generation of friction associated with steering operations.

As shown in FIG. 15A, the eccentric pivots 39 and 40 are thus rotated over a limited range by mechanically synchronized counter-rotation, which will be explained in more detail below. Pivot point M of roll 22 provides very uniform equidistant downstream-upstream movement in self-centering bushing assembly 72.

Therefore, the nip roll 20 is moved by the tensioning and steering roll 22 which runs obliquely in the plane M-K (FIG. 15) perpendicular to the casting surface C.
It maintains parallelism with 1.

The pivot point of the tensioning and steering roll assembly is located downstream as described above.
When a small distance is moved in the upstream direction, the hydraulic cylinders 41, 420 and the piston rod 44 move slightly forward or backward during one belt steering cycle to follow such movement.

In the neutral position (FIG. 15A), a plane 95 passing through the centers of the concentric shaft portions A and B and the center M of the eccentric shaft portion E is the casting surface C.
is parallel to

Mechanically synchronized rotation of the eccentric pivots 39.degree. 40 in opposite directions is effected by a steering synchronization shaft 75 (FIG. 14).

The steering synchronization shaft 75 is housed in a notch 79 of an outer synchronization arm 80 attached thereto, and operates the outer steering arm 76 in one direction by means of a liner 77 (FIG. 11) and a slide block 78.

The slide block 78 is pivotally connected to the outer steering arm 76 by a pivot pin 81.

Synchronization shaft 75 simultaneously operates inner steering arm 84 (FIG. 6) in opposite directions with synchronization arm 85 connected to steering arm 84 by pivot 83 and connecting rod 86.

The length of the connecting rod 86 is U, which is pivoted 85 to the synchronizing arm 85.
'Adjusted by a threaded end 86 (FIG. 6) screwed into a Jink 88.

The outer edge side steering arm 76 has an outer edge side pivot 400 square portion 91
(FIG. 11, FIG. 12, FIG. 14) is fixed by a clamp cap 90 (FIG. 11).

The two concentric shaft portions A are located so as to straddle the square portion 91 of the pivot 40.

Similarly, the inner edge side steering arm has an inner edge side pivot shaft 390 and a rectangular portion 9.
3 (Figs. 6, 8, and 14) with clamp 92 (
(Fig. 6).

Both ends of the steering synchronization shaft 750 are pivotally connected to bushings 94 (FIG. 7).
is stored inside.

The steering synchronization shaft 75 is shown in FIGS. 10 and 14.
It is thus operated by the hydraulic cylinder 99.

The hydraulic cylinder 99 is pivotally mounted 100 on the outer edge side of the frame 38.
The piston rod 101 of the hydraulic cylinder 99 is pivoted 102 to the outer synchronizing arm 80.
01 (Figure 11).

The outer synchronizing arm 80 can therefore be swung in either direction by the hydraulic cylinder 99, and the eccentric shaft portion E of the inner pivot 39 is thereby moved upwardly and downwardly and at the same time outwardly. Eccentric shaft portion E of edge side pivot 40
moves upward or downward in the opposite direction to the eccentric portion E of the inner edge side pivot 39.

Control of the Oblique Steering Axis To achieve optimum steering of the cast belt, the squaring shaft 34 is centered around the desired steering point S (see also Figure 18) during the belt steering cycle. A steering skew axis control assembly 104 (FIGS. 3 and 4) is provided to cause the vehicle to skew.

Regarding the steering guidance function, see Fig. 16, Fig. 17, and Fig. 1.
This will be explained in detail later with reference to FIG.

The skew control assembly 104 serves to prevent the squaring shaft 34 from moving axially, ie, outwardly or inwardly, and to maintain the squaring shaft 34 tilted at the desired point.

The skew control assembly 104 includes axial thrust blocks 105 and 106 that engage with each other, and the thrust blocks 105 and 106 are connected to each other by a cap screw 107 and project from the inner edge of the inner cylinder cap 51. Short shaft portion 108fzr: It is held down via an alignment bushing assembly 101 seated on the small diameter portion of the short shaft portion 108.

Centering bushing assembly 110 is retained by lock nut 112 and spacer ring 113.

Axial working end surface Q of thrust blocks 105, 106
, R are opposed to the parallel thrust surface T, (2) of the thrust load gear 114 and the thrust housing 115.

The alignment bushing assembly properly contacts and engages the axial thrust blocks 105, 106 with the thrust housing 115 at engagement surfaces R, V when the squaring shaft 34 is in any skew maneuvering and belt tensioning positions. Make proper contact with the thrust flange 114 at faces Q and T.

The centering bushing assembly 110 within the axial thrust blocks 105, 106 is sealed by a seal similar to seal 64 of FIG. 12 to prevent liquid coolant or foreign matter from entering the interior.

The thrust housing 115 is attached to a cap screw 118 (Fig. 3,
6 and 7) to the frame 38,
The keys 119 and 120 are positioned accurately to avoid receiving axial thrust loads.

The internal cavity of the axial thrust housing 115 and the thrust flange 114 that engages therewith is sealed on the inner edge by a housing cap 121 and on the outer edge in a position in sealing engagement with the thrust housing 115 and biased by a spring. It is sealed by a cover plate.

While the squaring shaft 34 and the tensioning and steering roll 22 concentrically attached to the shaft 34 are making oblique movements to steer the casting belt 14, the eccentric pivot 39.
The required axial movement of the centering bushing assembly 72 (FIGS. 8 and 12) engaging the eccentric shaft section E with respect to the 400 eccentric shaft section E takes place simultaneously with the rotation of the eccentric pivot 39,40. , thus providing a smooth steering action.

Each eccentric axis. Aligning bushing assembly 7 engaged with 39.40
The axial thrust force exerted on the eccentric pivots 39, 40 during the axial movement of the flange bushes 124 (
8 and 12) and a thrust cap 126 attached to the frame 38 by a retaining screw 128.

The illustrated actuation of the steering synchronization shaft 75 is performed by a hydraulic cylinder 99, but other actuations such as an electric or hydraulically driven screwdriver, an electric or hydraulically driven torque motor, etc. equipment may be used.

Automatic steering of the casting belt is achieved by automatically controlling a solenoid valve or electric switch using a belt edge sensor or microswitch, and an actuator 99 of the steering synchronization shaft 75.
This is accomplished by activating the squaring shaft 34 and the tensioning/steering roll 22 associated therewith from time to time to effect the required diagonal steering movement.

The assembly consisting of the tensioning and steering roll and squaring shaft can be easily removed.

The tensioning and steering roll and squaring shaft assembly illustrated in FIGS. 3, 4, and 14 can be fully preassembled and installed or removed from the continuous casting apparatus 10 as one complete unit. can do.

When removing the assembly, remove the two bearing caps 52 from their respective torque arms 35, 36.

Next, as best illustrated in FIG. 14, remove the pin 46 from the tip 45 of the piston rond, pull the skew control thrust housing 115 away from the frame 38,
Remove the hydraulic piping (not shown) from the hydraulic cylinders 41, 42.

The assembly can then be removed as a unit for repair if desired.

When the belt tension scaling shaft 34 and the torque arms 35, 36 connected thereto and the support cap 51.50 swing about the eccentric pivot 39.40, the hydraulic cylinder 4
0.410 The tensioning and steering roll 22 moves in an arc throughout the entire range of the belt tensioning stroke.

Even though the tensioning/steering roll 22 makes a limited circular arc movement through such an operating process, the circumference of the tensioning/steering roll 220 is intentionally slightly deviated from the casting pass line, so that the tension/steering roll 22 is not combined with the roll 22. cast belts are not affected in any way.

Furthermore, since the axis of each eccentric pivot 39, 40 lies in a plane passing through the intermediate operating position of the tensioning and steering roll 22 and perpendicular to the casting pass line, the portion of the tensioning and steering roll 220 near the pass line is extremely limited. FIGS. 15 and 15A are explanatory diagrams showing the geometrical relationships of the movable members during belt tensioning.

H represents Ul, the axis of the first ink pin 46, and J represents the axis of the trunnion 48 of the hydraulic cylinders 41, 42 in the "intermediate" position, respectively.

This intermediate position J corresponds to an "intermediate position" K of the axis of the squaring shaft 34.

This "intermediate position" is defined as the position where one radius from axis M of eccentric shaft E (see also FIG. 15A) to point A is perpendicular to casting plane C.

All figures from FIG. 1 to FIG. 18 depict parts in such "intermediate positions."

The ``intermediate position'' K is between the position occupied by each part when the shortest new belt is worn and the position occupied by each part when the longest used belt is hung.

A and B represent the eccentric shaft portions of the eccentric shaft 39 and 40, and E represents the eccentric shaft portion thereof, respectively.

In FIG. 15, point M represents the axis of eccentric shaft portion E when it is in the neutral position.

In FIG. 15A, shown on an enlarged scale, during a symmetrical steering action, the axes M of the eccentric shaft section E are denoted as M and M', respectively, 1 thus above and below the neutral position. It is possible to oscillate approximately 10° in each direction.

The hydraulic cylinders 40, 41 have a line of action 1 passing through points H and J.
The thrust is supplied along the line 40.

The squaring shaft 34 can swing along an arc 141 with a radius R1 centered on the axis M'jk.

At the moment when this movement is caused, the axis J of the trunnion 48 swings along an arc of radius R2 about the axis Rf.

The position on the axis along the arc 141 is the circled number L2,
It is represented by 3,4.

The corresponding axis J position is the same number 1 enclosed in a square.
．． It is represented by 2, 3, 4.

Position 1 is a position where the hydraulic cylinders 40, 41 are in the retracted position, the squaring shaft 34 is retracted, and the casting belt 14 is removed and replaced.

Position 2 is the position when the new bell (with the minimum length) is hung and tensioned.

Position 3 is the intermediate position described above.

Position 4 is the position when the worn belt is hung and tensioned.

The hydraulic cylinders 41, 42 are connected to the carriage assemblies L, U so that the casting belts 12, 14 can be installed and removed from the outer edge of the continuous casting apparatus without mechanical interference.
nip rolls 16, 20 and tension/steering rolls 18 of
.

In FIG. 10, a pointer 134 is attached to the outer cylinder cap 50, and the pointer 134 is attached to the frame 38 of the carriage assembly and cooperates with a scale 135 to accurately extend the tensioning and steering roll 22. The location is now displayed.

Pointer 134 and scale 135 are calibrated to continuously indicate the actual elongation of casting belt 14 in the carriage assembly during operation of continuous casting apparatus 10.

This display should be placed in a position that is easy for the user to read.

Separate adjustment of the gap between the ends of the tensioning and steering roll and the casting pass line Selection and setting of the variable gap width between the tensioning and steering roll 220 circumference and the casting pass line C by machining its inner diameter This is accomplished by an eccentric sleeve 57 (FIG. 4), each positioned eccentrically relative to the concentric outer surface, and an eccentric ring 130 associated with the eccentric sleeve 57.

a sleeve 57 and a ring 130 that engages the sleeve 57;
and rear set screw 132 (FIG. 4) adjusted to a special angular position with respect to the squaring shaft 34! Scaling each sleeve 57 by screwing it into the screw hole 133.
When secured to the shaft 34, the angular position of the eccentricity between the axis of the tensioning and steering roll 22 and the axis of the squaring shaft 34 is set.

A plurality of screw holes 133 are provided in each sleeve 57 to facilitate this adjustment (FIGS. 3 and 9).

As a result, the outer circumferential surface of the tension/steering roll 22 is set at a predetermined deviation from the casting pass line C (that is, the gap width).

The gap width is adjusted when the eccentric shaft E is in the neutral steering position and the axis K of the tensioning and steering roll 22 is in the intermediate position 3.

Since the gap width adjustment members 57, 130, 132, and 133 are provided at both ends of the squaring shaft 340, they can be set accurately with respect to the axis of the squaring shaft 34, which is the axis of the tensioning and steering roll 22. , and the tensioning and steering roll 22 can be positioned in an equilibrium position that provides the same amount of clearance at both ends.

Description of Symmetrically Synchronized Skew Adjustment Operation Turning now to FIG. 16, which is a schematic elevational view corresponding generally to FIG. 3, except that centering skew assembly 104 is not shown. The operation of the centering skew assembly 1040 will be explained with reference to FIG.

The cross mark 72 corresponds to the eccentric pivots 39, 40 on the inner edge side and the outer edge side.
(FIG. 8 and FIG. 12) schematically represents the center position of each centering bushing assembled together.

Eccentric pivot 3 if centering skew assembly 104 is not present
9.40 and the centering bushing 72 mean that the squaring shaft 34 is centered at the midpoint C-1 of the center position 72 of the bushing.
and the tension/steering roll 22 are made to move diagonally.

Therefore, as shown in a highly exaggerated manner in FIG. 16, the upper part of the tension roll 22 vibrates back and forth, causing the casting belt 14 to
The hydraulic cylinders 41, 427all tend to twist in the lateral direction, giving a significantly different oblique effect to the upper and lower running zones.

This lateral movement component of the hydraulic cylinders 41, 420 tends to cause the piston rods of the cylinders 41, 420 to become stuck.

Theoretically, it is desirable to cause the tension/steering roll 22 to move obliquely around point C-2 at the center of the rotation axis of the tension/steering roll 22 as shown in FIG. 17.

This is because the upper and lower running bands of the casting belt 14 are then subject to an equal oblique action.

However, since the centers of the hydraulic cylinders 41 and 420 are at a level above point C-2, a lateral motion component of the hydraulic cylinders 41 and 420 still exists.

Taking these conflicting factors into account, the center of skew is located at the midpoint S of the hydraulic cylinders 41, 42.

The skew center is aligned by the action of the skew assembly 1040.
It should be located symmetrically to a point S on the straight line connecting the centers of the hydraulic cylinders 41 and 420.

To explain the operation of the centering skew assembly 1040, the overhang member 108 is attached to the trunnion support member 5 on the inner edge side and the outer edge side.
0.51 and that the spherical bushing assembly 110 and thrust blocks 105, 106 are supported by two outriggers 108.

The center of the spherical bushing 110 is at the point S and the hydraulic cylinder 41
, 420 are located on a straight line 144 passing through the center.

When the fixed curved surface T' on the circumference of a circle centered on point SY is in a position where it makes sliding contact with each of the thrust blocks 105 at both ends of the tension/steering roll 220, the tension/steering roll 22 moves around the curved surface T'. ′, it is forced to move diagonally around point S.

Compared to the width of the tensioning and steering roll 220 or the distance 144, the curved thrust surface T', which has less oblique movement and less rotational movement around point S, can be replaced by a flat thrust surface T that is perpendicular to the casting area. (In other words, at a very small angle, the values of the sine and the cutoff are equal to g, so it can be replaced by the curved surface T''& flattened surface T).

Instead of using two projecting members 108, it is also possible to use only one projecting member attached to the inner edge side trunnion support member 51.

The outrigger member comprises a spherical bushing 110 and interengaging thrust blocks 105,106.

The center of the spherical bushing 110 is the point S and the hydraulic cylinder 41,
It is located on a straight line 144 passing through the center of 420.

Therefore, two fixed curved thrust surfaces T/ and V/ are provided on the circumference of a concentric circle with the point S in the middle and in sliding contact with the slide blocks 105 and 106.

In reality, the thrust blocks 105, 106 are captured by their curved thrust surfaces T/, V/, and the tension/steering roll 22 is forced to move obliquely about point S.

In this embodiment as well, since the range of oblique movement is small compared to the width of the tensioning and steering roll 220 and the length of the straight line 144, the fixed curved thrust surfaces T, V are in the plane of the casting area C (therefore point S is A flat parallel plane T perpendicular to the passing straight line 144),
It can be replaced by V.

When one steering axis point 72 moves downward or upward during steering, the other steering axis point 72 moves upward or downward.

The two thrust surfaces T, V acting on a straight line 144 with respect to the spherical bearing 110 provide reliable guidance of its movement.

As a result, a symmetrical diagonal movement about the desired center point S will be achieved.

As described above, the thrust surfaces T and V are connected to the fixed keyway 119.
Centering diagonal thrust assembly 1 fixed in position by attachment to frame 38 of the lower carriage assembly by a key and screw 118 engaged at 120
04 thrust flange 114 and thrust housing 115.

Each of the surfaces Q and R of the slide blocks 105 and 106 is in sliding contact with their thrust surface T t V.

It is advantageous to locate the centering skew thrust assembly 104 on the inner edge of the carriage assembly because it reduces rattle on the outer edge and facilitates operation.

However, the thrust assembly 104 can also be located on the outer edge side.

If desired, a pair of thrust assemblies can be used as shown in FIG. 17.

It is effective to install the synchronizing arms 80 and 85 (FIG. 14) at the outer and inner ends of the synchronizing shaft 75 so that they are perpendicular to each other when viewed in a direction parallel to the axis of the synchronizing shaft 75. be.

The inner side synchronizing arm 85 pushes and pulls the connecting rod 86 once, and the steering arm 84 is thereby swung.

The outer edge steering arm 80 provides direct swing motion to the steering arm 76.

No connecting rod is provided on the outer edge side. Therefore, the outer edge steering arm 76 swings in the opposite direction to the inner edge steering arm 84.

The steering arms 76, 84 move equally in opposite directions when the synchronization shaft 75 rotates.

Conclusion The apparatus of the present invention is suitable for casting slabs with a belt width of 1167 mm or more for casting slabs of 100 mm wide or more.
It can be incorporated into a sheet belt type casting machine.

Belt driven roll 16. at one end of carriage assembly U,L.
20 and the belt tensioning and steering rolls 18 and 22 at the other end form oblong symmetrical passages for the respective casting bells 12, 14 (see FIG. 2).

The rolls 16, 1B, 20, 22 are, for example, 30 (approximately 76
．． 20 cm) or larger, and can exert a tensile force on the belt 12.14 of 8,000-20,000 pounds per square inch of belt cross-section.

Belt thickness is approximately 0.040// (approximately 0.01016
cm) to about 0.060// (about o, o 1524
cm), belt width is 116// (approximately 2.9464 m)
), a tension force of 20,000 p,so,i, will result in a tension force of approximately 9,000 pounds to 14,000 bonds being exerted on each belt passage, resulting in each tension roll 18,
A total tension of 180,000-280,000 bonds is exerted by 22.

The lower carriage assembly U may be slightly longer than the upper carriage assembly U, for example 0.5 cm longer.

This means that for some new cast belts, it is approximately 0.5 (
(approx. 0.127 cm).

Since the lengths of the belts are slightly different, the two belts can be fitted together, which is very convenient for storage and shipping.

Since most casting equipment operates in harsh environments and high temperatures, care is taken to minimize the number of exposed sliding surfaces to prevent wear and corrosion of critical surfaces. However, it is particularly desirable that the parts of the apparatus of the present invention be made of wear-resistant and corrosion-resistant materials.

[Brief explanation of drawings]

FIG. 1 is a perspective view of the feed side of a continuous strip casting apparatus according to an embodiment of the invention, viewed from a forward position on the outer edges of the upper and lower carriage assemblies; FIG. 1 is an elevational view of the device shown in FIG. 1 viewed from the outer edge, and FIG. 3 is an elevational view of the downstream main roll of the lower carriage assembly and the associated belt tensioning and steering device looking upstream. Figure 4 is a cross-sectional view taken along line 4-4 in Figure 3, and Figure 5 is a view taken from the right side of Figure 3. An elevational view of the inner end of the same device as seen above, Figure 6 is Figure 3 (7) 6-6.
Enlarged sectional view taken along the line and looking towards the left, No. 7
The figure is a cross-sectional view taken along line 6-6 in Figure 6.
Figure 8 is a sectional view taken along line 8-8 in Figure 5, and Figure 9 is a cross-sectional view taken along line 9-9 in Figure 3, looking leftward and downstream. 10 is a cross-sectional view of the lower main roll, also showing a portion of the downstream end of the frame of the lower carriage assembly; FIG. Figure 11 is an enlarged sectional view taken along line 1111 in Figure 3 and viewed to the right, and Figure 12 is an enlarged cross-sectional view of Figure 10.
13 is a cross-sectional view of the outer edge side tension axis taken along the line 12-12 in the figure and viewed toward the left.
FIG. 14 is an exploded perspective view of various parts of the steering and tensioning device; FIG. Figure 15A is an explanatory diagram of the operation of the present invention, Figures 16 to 18
The figure is a schematic elevational view, generally corresponding to FIG. 3, showing the downstream main roll and associated belt tensioning and steering system schematically for purposes of illustration. 12.14: Casting belt, 16,1B, 20°22:
Main roll, 34: Fixed axis, 35, 36:) Luk arm,
38: Carriage frame, 39° 4g: f* □, 4
i, 42・Force application device・56゛Bearing 0

Claims (1)

[Claims] A belt tensioning device for a twin-belt continuous metal casting machine of the type in which the casting zone is formed between intervals of two casting belts, the casting belt having a pair of main rolls at each end supporting and rotating. In a belt tensioning device comprising a carriage framer for moving, said rolls extending parallel to each other around which said casting belt rotates: one of said main rolls is hollow, and a fixed axis is attached to one end of said hollow roll; to the other end, a pair of bearings surrounding the shaft supporting the hollow roll on the shaft, one bearing supported near each end of the hollow roll. the roll is rotatable about the shaft, a pair of parallel torque arms are fixed to opposite ends of the shaft, and a pair of pivots are mounted on opposite sides of the carriage frame. each torque arm is supported on the carriage frame, and a pair of force application devices tension the casting belt on the carriage frame, one in a direction away from the other roll. a belt tensioning device associated with each of said torque arms for pushing both of said torque arms to rotate simultaneously about said pivot;