US3878883A - Symmetrical synchronized belt-steering and tensioning system and apparatus for twin-belt continuous metal casting machines - Google Patents

Symmetrical synchronized belt-steering and tensioning system and apparatus for twin-belt continuous metal casting machines Download PDF

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Publication number
US3878883A
US3878883A US350600A US35060073A US3878883A US 3878883 A US3878883 A US 3878883A US 350600 A US350600 A US 350600A US 35060073 A US35060073 A US 35060073A US 3878883 A US3878883 A US 3878883A
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United States
Prior art keywords
belt
steering
roll
casting
pair
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US350600A
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English (en)
Inventor
Robert William Hazelett
John Frederick Barry Wood
Robert J Carmichael
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Hazelett Strip Casting Corp
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Hazelett Strip Casting Corp
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Priority to US350600A priority Critical patent/US3878883A/en
Priority to NO741232A priority patent/NO137422C/no
Priority to ZA00742290A priority patent/ZA742290B/xx
Priority to FR7412609A priority patent/FR2225235B1/fr
Priority to JP49041603A priority patent/JPS594225B2/ja
Priority to SE7404935A priority patent/SE407348B/xx
Priority to AU67724/74A priority patent/AU485986B2/en
Priority to BR2879/74A priority patent/BR7402879D0/pt
Priority to CA197,420A priority patent/CA1025175A/en
Priority to IN820/CAL/74A priority patent/IN141893B/en
Priority to CH508474A priority patent/CH596907A5/xx
Priority to DE2417682A priority patent/DE2417682C2/de
Priority to GB1640274A priority patent/GB1474933A/en
Priority to IT21346/74A priority patent/IT1009832B/it
Priority to BE143147A priority patent/BE813657A/xx
Priority to US05/474,617 priority patent/US3949805A/en
Priority to US05/570,208 priority patent/US3963068A/en
Application granted granted Critical
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B22—CASTING; POWDER METALLURGY
    • B22D—CASTING OF METALS; CASTING OF OTHER SUBSTANCES BY THE SAME PROCESSES OR DEVICES
    • B22D11/00—Continuous casting of metals, i.e. casting in indefinite lengths
    • B22D11/06—Continuous casting of metals, i.e. casting in indefinite lengths into moulds with travelling walls, e.g. with rolls, plates, belts, caterpillars
    • B22D11/0637—Accessories therefor
    • B22D11/0677—Accessories therefor for guiding, supporting or tensioning the casting belts

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  • ABSTRACT A symmetrical belt-steering and tensioning system and BELT-STEERING AND TENSIONING SYSTEM AND APPARATUS FOR apparatus for twin-belt continuous metal casting l'lll chines are disclosed.
  • a rigid squaring shaft passes through a hollow tension and steering roll and is rig- TWIN-BELT CONTINUOUS METAL CASTING MACHINES [75] Inventors: Robert William Hazelett, Winooski;
  • twin-belt casting machines use a pair of thin, wide endless metal casting belts to define the upper and lower surfaces of the region in which molten metal is confined as it is being solidified.
  • twin-belt continuous metal casting machines for example, as shown in US. Pat. Nos. 2,640,235; 2,904,860; 3,036,348; 3,041,686; 3,123,874; 3,l42,873; 3,I67,830; 3,228,072; and 3.3 l0,849.
  • the present invention enables twin-belt casting machines to be built in larger widths and sizes than were previously attained.
  • the upper and lower casting belts are revolved around cantilevered upper and lower carriages carrying main rolls for these belts. These main rolls perform the functions of driving, tensioning and steering the belts.
  • a rigid squaring shaft passes through a hollow tensionsteering roll and is rigidly secured to a pair of rigidly aligned torque arms at opposite ends of the roll. These arms are associated with dual tension thrust means and dual steering means arranged to provide symmetrical synchronized steering action and tensioning movement of the tension-steering roll. Only two large diameter main rolls are used at opposite ends of each carriage, one being the belt-driving roll and the other the tensioning-steering roll. Thus, the belt path is defined as a symmetrical oval shape and a high tension force is applied to the belts to provide an accurate wide mold under operating conditions.
  • Each end of the tension-steering roll can be independently adjusted to displace the tension-steering roll axis with respect to the axis of the squaring shaft for setting the clearance of the roll circumference from the pass line of the cast product.
  • These adjustments are provided by sleeves associated with the squaring shaft and the bearings in the interior of the hollow roll.
  • tension-steering roll and squaring shaft assembly For convenience of servicing the tension-steering roll and squaring shaft assembly can be removed and reinstalled as a complete unit.
  • FIG. 1 is a perspective view of thhe input or upstream end of a continuous strip-casting machine embodying the present invention, as seen looking toward the machine from a position in front and beyond the outboard side of the two belt carriages;
  • FIG. 2 is an elevational view of the machine as seen looking toward the outboard sides of the two belt carriages;
  • FIG. 3 is an elevational view of the downstream main roll for the lower carriage with the associated belt tensioning and steering apparatus, as seen looking upstream, with part of the roll shown broken away;
  • FIG. 4 is a plan sectional view of the apparatus shown in FIG. 3 taken along the line 4-4 in FIG. 3;
  • Flg. 5 is an elevational view of the apparatus as seen from the right in FIG. 3, i.e. an elevational view of the inboard end;
  • FIG. 6 is an enlarged crosssectional view taken along the line 6-6 in FIG. 3 looking toward the left;
  • FIG. 7 is a sectional view taken along the irregular line 7-7 in FIG. 6;
  • FIG. 8 is asectional view taken along the line 88 in FIG. 5;
  • FIG. 9 is a cross-sectional view of the lower main downstream roll taken along the line 9--9 in FIG. 3 looking toward the left.
  • FIG. 9 also shows a portion of the downstream end of the frame of the lower carriage;
  • FIG. I0 is an elevational view of the apparatus as seen from the left in FIG. 3; that is. an elevational view of the outboard end;
  • FIG. 11 is an enlarged cross-sectional view taken along the line 11-11 in FIG. 3 looking toward the right;
  • Fig. 12 is a cross-sectional view through the outboard tension pivot taken along the line IZ-IZ in FIG. I0 looking toward the left;
  • FIG. 13 is a cross-sectional view taken along the line 13-13 in FIG. 3 showing the outboard tension pivot and main roll and downstream end portion of the lower carriage;
  • FIG. 14 is an exploded perspective view of portions of the steering and tensioning apparatus
  • FIGS. 15 and ISA are diagrams for purposes of explanation', and
  • FIGs. l6, l7 and 18 are diagrammatic elevational views, corresponding generally to FIG. 3, showing the downstream main roll and associated belt tensioning and steering apparatus schematically illustrated for purposes of explanation.
  • molten metal is fed into the upstream end or entry of the machine between upper and lower endless flexible casting belts l2 and 14.
  • the molten metal is solidified in a casting region C (FIG. 2 ⁇ defined by the spaced parallel surfaces of the upper and lower casting belts l2 and 14.
  • the two casting belts l2 and 14 are supported and driven by means of upper and lower carriage assemblies which are indicated in FIGS. 1 and 2 at U and L. respectively.
  • the carriage assemblies are supported in cantilevered relationship from a main frame 23, as seen in FIG. 1. Hence the sides of the carriage assemblies near this main frame are referred to as being inboard, while the other sides are referred to as outboard.
  • the upper carriage includes two main pulley rolls l6 and 18 (FIG. 2) around which the casting belt 12 is revolved as indicated by the arrows.
  • the roll 16 near the input end of the machine is referred to as the upstream roll or nip roll and the other roll 18 is called the downstream or tension roll.
  • the lower carriage L includes main upstream (or nip) and downstream pulley rolls 20 and 22, respectively, around which the lower casting belt 14 is revolved.
  • the upstream or nip pulley rolls 16 and 20 of both the upper and lower carriages are jointly driven through universal spindles 24 and 25 and a mechanically synchronized drive 26 by an electrical drive motor (not shown).
  • the upper carriage assembly U is supported on the lower carriage assembly L through gauge spacers located at four corner support points, and the precise thickness of these four gauge spacers establishes the mold thickness dimension between the opposed casting faces of the cast ing belts l2 and 14 and correspondingly the resulting cast metal thickness.
  • Two strands of closely fitting edge dams 28 are interposed between the opposed casting faces of the casting belts and are guided and laterally contained to establish the cast metal width at the nip or upstream end of the casting machine by the edge dam guide assemblies 30. These two strands of edge dams are driven through frictional contact with the driven lower casting belt 14.
  • the two opposed inner casting faces of these edge dam assemblies 28, together with the two opposed casting faces of the upper and lower casting belts l2 and I4 form four synchronized casting faces of a moving mold C.
  • the downstream or tension pulley roll 22 (FIGS. 3 and 4) is made hollow and is mounted concentrically on a strong torque-tube squaring shaft 34 rigidly secured to both the inboard and outboard torque arms 35 (FIG. 6) and 36 (FIGS. 10, II and 13), respectively.
  • These torque arms 35 and 36 are pivotally mounted on the frame 38 of the lower car riage by inboard and outboard pivot shafts 39 (FIG. 8) and 40 (FIGS. 12 and 13), respectively.
  • the pivoted squaring shaft torque-tube 34 serves to keep the torque arms 35 and 36 exactly parallel with each other so that they always move equally and each is always in the same relative position with respect to the frame 38.
  • the inboard and outboard edges of the belt 14 are always maintained under equal lengths of travel.
  • the two torque arms 35 and 36 together with the squaring shaft 34 are urged in the belt tensioning direction by consistent, predictable symmetrical force applying means 41 and 42 acting over the full range of tensioning travel.
  • This force applying means may be embodied as a pair of matched coil or air springs with screw jack adjustment.
  • the consistent, predictable force applying means comprises inboard and outboardfluid power cylinders 41 and 42 (FIG. 4) situated at extreme ends of squaring shaft assembly 34, 35, 36 with each cylinder rod 44 having its end 45 pivoted by a clevis pin 46 to the carriage frame 38.
  • the fluid cylinder 42 at the outboard end of the tension pulley assemblies is mounted by trunnions 48 in its respective torque arm 36 and cylinder support cap 50.
  • the fluid cylinder 41 at the inboard end of the tension pulley assembly is mounted by trunnions 48 in its respective torque arm 35 and combination cylinder support cap and axial thrust member 51.
  • the tension pulley 22 complete with its squaring shaft 34, torque arms 35 and 36, torque arm bearing caps 52 (FIG. 3), cylinder support caps 50 and SI, and fluid cylinders 41 and 42 is symmetrically skewed in a plane perpendicular to the plane of the moving mold C by opposed rotation of the combined pivot and eccentric shafts 39 (FIG. 8) and 40 (FIGS. 12 and 13).
  • the symmetrical skewing of the tension pulley roll 22 relative to the nip pulley roll 20 modifies the belt angle of approach to the tension pulley roll and nip pulley roll and provides accurate tracking or steering of the wide casting belt 14 on these re lated pulley rolls.
  • the center distance between the nip pulley roll 20 and tension pulley roll 22 is maintained consistently across the complete face width of these pulleys for all positions of the tension pulley assembly and for all steering conditions from the neutral skew position to maximum skewed positions in either direction.
  • the tension pulley roll 22 rotates freely about its related squaring shaft 34 being supported for withstanding large weight effects arising from the metal product and pulley assembly weight plus the belt tension radial loads by two large diameter anti-friction bearings 56 (FIG. 4) assembled on eccentric sleeves 57 (FIG. 4) which are mounted on the squaring shaft 34.
  • One of these anti-friction bearings 56 is also used as a 2- directional axial thrust bearing to contain any resulting axial thrust forces between the tension pulley roll 22 and the squaring shaft 34. It is preferred that this bearing 56 which contains the axial thrusts be the one located near the centering skewing master thrust assembly 104.
  • These anti-friction bearings 56 are each sealed against ingress of casting machines liquid coolant and foreign material by a seal 58 with cooperating sealing components.
  • Each bearing 56 can be lubricated through a passage 60 (FIG. 4) and maintenance of the lubricant in the bearing is assured by an internal seal 61 with cooperating sealing members.
  • the tension pulley roll 22 is assembled onto its related squaring shaft 34, anti-friction bearings 56, ec centric sleeves 57, sealing and retaining members prior to assembly of the torque arms 35 and 36 onto the ends of the squaring shaft 34 by means of the multiple cap screws 54.
  • Mating machined reference shoulder faces extending axiaily at F and G (FIG. 4) guarantee accurate relative location of the two torque arms 35 and 36 as they are assembled rigidly onto the end faces of the squaring shaft 34.
  • a very rigid connection is provided at the radial joint 64 (FIG. 4).
  • this rigid joint 64 is provided by substantial compression frictional forces obtained at the radial joint 64 by tightening of the multiple cap screws 54 mentioned above, thus assuring a high torsional capacity rigid connection at this joint.
  • outboard cylinder support cap 56 is rigidly connected to the outboard torque arm 36 by a pair of vertically spaced plates 66 (FIGS. 3 and E3) extending above and below the fluid cylinder 42.
  • the inboard cap and axial thrust member 5! is rigidily secured to the inboard torque arm 35 by an other pair of vertically spaced plates 67 (FIGS. 3 and 6) extending above and below the cylinder 41.
  • This strong rigid construction as shown for the squaring shaft 34 and torque arms 35 and 36 permits convenient disassembly of the complete tension pulley roll assembly and assures accurate re-assembly of the tension pulley assembly especially with reference to maintaining the relative positions of the torque arms mounted on the squaring shaft. thus maintaining the matched center distance between nip pulley roll 20 and the tension pulley roll 22 as measured across the complete face width of these rolls.
  • the tension cylinders 41 and 42 each has a line of thrust action as seen in FIG. 14 which has essentially the same angular relationship with respect to a radius R in the respective torque arms 35 and 36 from the axis of the respective pivot shafts 39 and 40 to the axis of the trunnions 48 as the angular relationship between the direction of belt tension force exerted by the taut casting belt and a smaller radius R, in the respective torque arms from the axis of the respective pivot shafts to the axis of the roll 22 on which the belt tension force is acting.
  • a radius R in the respective torque arms 35 and 36 from the axis of the respective pivot shafts 39 and 40 to the axis of the trunnions 48 as the angular relationship between the direction of belt tension force exerted by the taut casting belt and a smaller radius R, in the respective torque arms from the axis of the respective pivot shafts to the axis of the roll 22 on which the belt tension force is acting.
  • the fluid powered thrust cylinders 41 and 42 which are located at the opposite ends of the squaring shaft 34 provide belt tensioning forces at the tension pulley roll 22 proportional to the fluid cylinder pressures utilized and continuously maintained. Accordingly, this belt tensioning apparatus will advantageously, over the normal operating range, accommodate casting belts of different lengths during casting machine operation. with the belt tensioning forces applied by the tension pulley roll 22 remaining essentially directly proportional to the fluid pressure in the thrust means 41 and 42. regardless of significant variation in casting belt lengths. This means that even if the belt happens to stretch with usage, it can still be used conveniently.
  • the essentially constant mechanical advantage provided by this arrangement means that the operator can continue to use a given fluid pressure and be assured that the tension forces have the proper value regardless of whether the belt is new or stretched. smaller or larger.
  • R is greater than R (The axes of the corresponding upper carriage cylinders [not shown] are intentionally displaced below the axis of the squaring shaft for the upper tension pulley 18.)
  • the larger radius R at which the cylinder thrust 140 acts provides force multiplication for it relative to the tension force exerted at R by the taut belt.
  • this relationship provides certain small proportion of the force being exerted by these cylinders 41 and 42 as a preload at the pivot shafts 39 and 40. This pre-loading of the pivot shafts 39 and 4t) and associated eccentric bushings 69, 7t) and 71 (FIGS.
  • both ends of the tension pulley roll 22 can be skewed by the eccentric a maximum of plus or minus approximately lb of an inch from the neutral steering position.
  • the two eccentric pivot portions E of the shafts 39 and 40 each have an eccentricity of approximately /2 of an inch relative to portions A and B and can be rotated approximately 10 above and below the neutral position to accomplish the amount of tension pulley skewing, as indicated.
  • the torque arms 35 and 36 and bearing caps 52 (FIGS. 8 and 12) each are assembled with a self-aligning type spherical bushing assembiy 72 which is seated on the central throw portion E of the eccentric pivot shafts 39 and 40. a pair of sealing members 74 (FIGS.
  • each torque arm and bearing cap 52 are assembled with each torque arm and bearing cap 52 to provide an enclosure for the self-aligning bushing 72 which is thereby sealed against entry of liquid coolant and foreign material.
  • Lubrication of each eccentric pivot shaft 39 and 40 is provided through a lubrication fitting 73 to provide a relatively friction-free steering action with minimum wear on associated parts.
  • the steering synchronizing shaft 75 actuates the outboard steering arm 76 in one direction by means of liners 77 (FIG. 11) and a sliding block 78 contained within a machined recess 79 in the outboard synchronizing arm 80 on this shaft 75.
  • the sliding block 78 is pivotally connected by a pivot pin 81 to the outboard steering arm 76.
  • the synchronizing shaft 75 simultaneously actuates the inboard steering arm 84 (FIG. 6) in the opposite direction by means of a synchronizing arm 85 linked by a pivot 83 and by a connecting rod 86 to the steering arm 84.
  • the length of the connecting rod 86 is adjustable by means of a threaded end portion 86 (FIG. 6) screwed into a clevis 88 which is pivoted at 89 to the synchronizing arm 85.
  • the outboard steering arm 76 is secured by a clamp cap 90 (FIG. 11) onto a square portion 91 (FIGS. 11,12 and 14) of the outboard pivot shaft 40. This square portion of the shaft 40 is straddled by the two larger diameter concentric portions A.
  • the inboard steering arm is fastened by a clamp 92 (FIG 6) onto a square portion 93 (FIGS. 6, 8 and 41) of the inboard pivot shaft 39.
  • the steering synchronizing shaft 75 is pivoted at its extreme ends within bushings 94 (FIG. 7) contained within pillow blocks 96 aligned and fastened to the main carriage frame structure 38 by cap screws 97. As shown in FIGS. 10 and 14, this steering synchronizing shaft 75 is actuated by a fluid power cylinder 99 pivotally connected at 100 to the outboard side of the main carriage frame structure 38, and having a piston rod 101 pivoted at 102 to the outboard synchronizing arm 80 (FIG. 11).
  • the outboard synchronziing arm 80 can be swung in either direction by the cylinder 99, thereby to shift the eccentric E of the inboard pivot shaft 39 up or down and simultaneously to shift the eccentric E of the outboard pivot shaft 40 down or up, respectively.
  • This skewing control assembly 104 prevents the squaring shaft 34 from moving axially, i.e. outboard or inboard, and assures that the point of actual tilting of the shaft 34 is at the desired points and not elsewhere.
  • the skewing control assembly 104 includes mating axial thrust blocks 105 and 106 which are fastened together by cap screws 107 and holding the extended inboard stub shaft outrigger portion 108 of inboard cylinder cap 51 through a selfaligning bushing assembly 110 seated on a reduced di ameter section III of thet extended portion 108.
  • the bushing assembly 110 is retained by lock nut 112 and spacer ring 113.
  • Axial control faces Q and R of the thrust blocks 105 and 106, respectively, are accurately contained by parallel thrust faces T and V on thrust flange I14 and thrust housing 115, respectively.
  • the self-aligning bushing assembly 110 permits the mating axial thrust blocks I and 106 to assume proper contact with thrust housing 115 at the mating faces R and V and with the thrust flange 114 at the mating faces Q and T for all skewed steering positions and belt tensioning positions of the squaring shaft 34.
  • the selfaligning bushing assembly 110 within the axial thrust blocks 105 and 106 is sealed against ingress of liquid coolant and foreign material by seals similar to those shown at 64 in FIG. 12.
  • the thrust housing is mounted onto the carriage frame structure 38 by cap screws 118 (FIGS. 3, 6 and 7) and accurately located and retained against axial thrust loads by keys 119 and 120.
  • the cavity within the axial thrust housing 115 and mating thrust flange 114 is sealed at the inboard side by a housing cap 121 and at the other side by a cover plate 122 loaded by a spring 123 into sealing engagement with the housing 115.
  • actuation of steering synchronizing shaft 75 is provided by fluid power cylinder 99
  • other actuating means 99 for actuating this steering synchronizing shaft can be used, such as an electrically, hydraulically, or manually, driven screw jack, or electrically or hydraulically actuated torque motor applied to the shaft 75.
  • Automatic steering or tracking of each casting belt can be provided by use of a belt edge sensor or microswitch which automatically controls a solenoid valve or electrical switch which thereby appropriately actuates the means 99 for actuating the shaft 75 to provide the necessary skewed steering motion of the squaring shaft 34 and related tension pulley roll 22, as previously described.
  • Each complete tension-steering pulley roll and squaring shaft assembly is completely pre-assembled and can be installed or removed from the casting machine 10 as a complete unit.
  • the two bearing caps 52 are removed from their respective torque arms 35 and 36.
  • the two pins 46 are removed from the ends 45 of the piston rods, as seen most clearly in FIG. 14, and the skewing control thrust housing 115 is disconnected from the frame 38.
  • the hydraulic connections (not shown) are removed from the fluid cylinders 41 and 42. Then this assembly can be removed as a complete unit for servicing, if desired.
  • each pivot shaft 39 and 41 is in a plane perpendiciular to the casting pass line through the mid operating position of the roll so that there is only a very limited up-down motion of the portion of the steering-tensioning roll near the pass line.
  • FIGS. 15 and 15A show the geometrical relationships of the movable members during belt-tensioning action.
  • H indicates the axis of the clevis pin 46
  • J indicates the axis of the trunnions 48 of the cylinder thrust means 41 or 42 at the so-called mid-position".
  • This midposition J corresponds with the mid-position K of the axis of the squaring shaft 34, which is defined as being the position when a radius from the axis M (see also FIG. 15A) of the eccentric E to point K is perpendicular to the plane of the casting region Cv
  • All of the fig ures show the respective parts in this so-called midposition.
  • this mid-position K is approximately midway between the positions occupied when the shortest new belt is taut or the longest used belt is taut.
  • a and B indicate the concentric portions of the pivot shaft 39 and 40, and E indicates the eccentric portion.
  • E indicates the eccentric portion.
  • the point M is shown with the eccentric E at the neutral position.
  • FIG. 15A which is drawn full size, it can be seen that during the symmetrical steering action the axis M of the eccentric E can be swung approximately l0 above and below the neutral position, as indicated at M and M", respectively.
  • the cylinder thrust means 40 or 41 deliver thrust along the line of action which passes through points H and .l.
  • the axis K of the squaring shaft 34 can be swung along an are 141 which is at a radius R from axis M.
  • the trunnion axis .l is swung along an are 142 at a radius R, from point M.
  • the respective position of the axis K along the are 141 are shown by the numbers 1, 2, 3 and 4 drawn within small circles.
  • the corresponding respective positions of the axis .l are shown by these same numbers drawn within small squares.
  • the positions 2 (square) and 2 (circle) are occupied when the shortest new belt is pulled taut.
  • the belt tensioning cylinders 41 and 42 intentionally do not extend (as seen in FIGS. 5 and I0) beyond a projection of the belt path line established by the nip pulley roll 16 or 20 and the tension pulley roll 18 or 22 on each respective carriage assembly to facilitate installation and removal of the casting belts I2 and 14 from the outboard side of the casting machine without mechanical interference.
  • a pointer I34 mounted on the outboard cylinder support member 50 cooperates with a related scale I35 mounted on the frame of the carriage to indicate the precise extended position of the tension pulley roll.
  • This pointer and scale are calibrated to continuously indicate the actual stretched length of the casting belt on the carriage assembly while the machine I is in operation. This reading can conveniently be be observed by the operator.
  • the axis of the pulley roll 22 can be set precisely relative to the axis of the squaring shaft 34, so that the roll is in a balanced position to provide the same amount of clearance at both ends.
  • FIG. I6 is a schematic diagram elevational view corresponding generally to FIG. 3, except that the assembly I04 has been omitted.
  • the cross marks at 72 diagrammatically indicate the centers of the respective selfaligning bushings associated with the inboard and outboard eccentric pivot shafts 39 and 40 (FIGS. 8 and I2).
  • centering skewing assembly 104 It is the function of the centering skewing assembly 104 to cause the center of skewing to be symmetrically located at the point S on a line I44 joining the centers of the cylinders 41 and 42.
  • outriggers I08 are attached to both the inboard and outboard cylinder trunnion support members 50 and 51 and that spherical bushing assemblies 110 and thrust blocks 105, 106 are carried by both Outriggers.
  • the centers of the spherical bushings I I0 are located on the line I44 passing through point S and through the centers of the cylinders 41 and 42.
  • This outrigger carries a spherical bushing I10 and the mating thrust blocks 105 and 106.
  • the spherical center of the bushing I10 is located on the line 144 passing through point S and through the centers of the thrust cylinders 41 and 42.
  • two fixed curved thrust surfaces T' and V are provided concentric about S and in sliding contact with the thrust blocks I05 and 106. In effect, the thrust blocks I05 and I06 are captured between these two curved thrust surfaces T' and V, and thus the roll 22 is forced to skew about the center S.
  • the pair of fixed curved thrust surfaces T' and V can be replaced by the plane parallel surfaces T and V perpendicular to the plane of the casting region C (and also perpendicular to the line 144 passing through the points S).
  • one of the steering pivot points 72 moves down or up and the other steering pivot point 72 moves equally up or down while positive guidance is provided by the two thrust surfaces T and V acting with respect to a spherical bearing 110 on the line 144 through center point S.
  • the surfaces T and V are provided by the thrust flange 114 and thrust housing 115 of the centering skewing thrust assembly 104 which is fixed in position by being attached to the lower carriage frame by the screws 118 and keys in the fixed keyways I19 and I20, as explained above.
  • the respective surfaces and R of the thrust blocks I and 106 slide against these thrust surfaces T and V.
  • the synchornizing arms 80 and 85 (FIG. 14) at the ouboard and inboard ends of the synchronizing shaft 75 are effectively at right angles to each other as seen looking in a direction parallel with the axis of the shaft 75.
  • the inboard synchronizing arm 85 exerts a push-pull action on its connecting rod 86 which swings the steering arm 84.
  • the outboard steer ing arm 80 exerts a direct swinging action on its steering arm 76, and there is no connecting rod involved.
  • the outboard steering arm 76 is swung in the opposite direction from the inboard steering arm 84. They are moved equal amounts in opposite directions when the synchronizing shaft 75 is turned.
  • the present invention may be embodied in twin-belt metal casting machines having belt widths of 116 inches or more for casting slabs of 100 inches in width or more.
  • the belt driving roll 16 or 20 at one end of the carriage U or L and the tension-steering roll 18 or 22 at the other end of the carriage define symmetrical oval-shaped paths. as seen in FIG. 2. for the respective casting belts 12 or 14.
  • These rolls are of large diameter. for example. 30 inches or more in diameter, such that high tension forces can be applied to the belts, for example, these tension forces may be in the range from 8.000 up to 20.000 or more pounds per square inch of belt cross section.
  • the tension force is in the range from approximately 90,000 pounds to l40.000 pounds for each belt path. which accordingly requires a total tension force of 180,000 pounds to 280.000 pounds to be applied by each tension-steering roll.
  • the lower carriage L may be made slightly longer. for example. V2 of an inch longer. than the upper carriage. This means that some of the new casting belts are made approximately V2 inch larger. The slight differential enables new belts to be nested inside of each other for convenience in storage and shipping.
  • a symmetrical belt-tensioning system for use in a twin-belt continuous metal casting machine of the type in which a casting region is defined between spaced parallel portions of two casting belts. said system comprising:
  • a carriage for supporting and revolving a casting belt having a pair of main rolls at opposite ends of a carriage frame. said rolls extending parallel to each other and also parallel to the plane of the casting region for defining an oval shaped path around which the casting belt is revolved,
  • one of said main rolls being hollow.
  • a rigid squaring shaft passing through said hollow roll from one end to the other.
  • a pair of bearings encircling said squaring shaft for mounting said hollow roll on said squaring shaft, one of said bearings being mounted near each end of said hollow roll providing free rotation of said roll about said squaring shaft.
  • a pair of parallel torque arms rigidly secured to opposite ends of said squaring shaft.
  • a pair of pivot mountings positioned on opposite sides of the carriage frame for mounting the respective torque arms on the carriage frame.
  • one of said force applying means being associated with each of said torque arms urging both of said torque arms simultaneously to swing about said pivot mountings for moving said one roll in a direction away from the other roll for tightening the casting belt on said carriage.
  • the axis of said squaring shaft being swingable along an are about said pivot mountings.
  • one of said bearings encircling said squaring shaft is arranged to transmit axial thrust between said squaring shaft and said hollow roll.
  • skewing axis control means are mounted on said carriage frame.
  • said skewing axis control means being effectively coupled to said squaring shaft near one end for preventing said squaring shaft from moving in an axial direction to assure that said hollow roll is skewed about a predetermined point.
  • the one of said bearings which is arranged to transmit axial thrust is located near the same end of said squaring shaft to which said skewing axis control means are effectively coupled.
  • a symmetrical belt tensioning and steering system for use in a twin-belt continuous metal casting machine as claimed in claim 2, in which:
  • said skewing axis control means provides first and second thrust surfaces facing in opposite directions
  • said squaring shaft has an outrigger rigidly coupled thereto
  • a self-aligning bushing assembly is mounted on said outrigger, and
  • a pair of thrust blocks are secured to said bushing assembly providing third and fourth thrust surfaces facing in opposite directions and mating in sliding engagement with said first and second thrust sur faces respectively.
  • a symmetrical synchronized belt-steering and tensioning system for use in a twin-belt continuous metal casting machine of the type in which a casting region is defined between spaced parallel portions of the two casting belts, said system comprising:
  • a carriage for supporting and revolving a casting belt, said carriage having a frame with a pair of main rolls at opposite ends of the carriage frame, said rolls extending parallel to each other and also par ailel to the plane of the casting region for defining an oval shaped path around which the casting belt is revolved,
  • At least one of said main rolls being hollow
  • a pair of bearings encircling said squaring shaft for mounting said one hollow roll on said squaring shaft.
  • one of said bearings beings mounted near each end of said one hollow roll providing free rotation of said roli about said squaring shaft, pair of torque arms rigidly secured to opposite ends of said squaring shaft, said torque arms being parallei, pair of pivot mountings positioned on opposite sides of the carriage frame for mounting the respective torque arms on the carriage frame,
  • a symmetrical synchronized belt-steering and tensioning system for use in a twin-belt continuous metal casting machine as claimed in claim 5, in which:
  • said pair of force-applying means operate to swing the axis of said squaring shaft along an arc about said pivot mountings
  • said pair of pivot mountings each include a selfaiigning spherical connection for allowing said skewing steering movement of said one hollow roll to be accomplished regardless of the position of said squaring shaft along said are from said second position to said fourth position.
  • a symmetrical synchronized belt-steering and tensioning system for use in a twin-belt continuous metal casting machine as claimed in claim 6, in which:
  • said third position of said squaring shaft axis and the effective centers of said spherical connections are arranged in a plane perpendicular to the plane of the casting region.
  • a symmetrical synchronized belt-steering and tensioning system for use in a twin-belt continuous metal 5 casting machine as claimed in claim 5, in which:
  • one of said bearings encircling said squaring shaft is arranged to transmit axial thrust between said squaring shaft and said one holloe roll, and
  • skewing axis control means are mounted on said car- 4O riage frame being effectively coupled to said squaring shaft near one end for preventing said squaring shaft from moving in an axial direction to assure that said one hollow roll is skewed about a prede- 4s termined point.
  • a symmetrical synchronized belt-steering and ten sioning system for use in a twin-belt continuous metal casting machine as claimed in claim 6, in which:
  • said pair of consistent, predictable force-applying means is a pair of fluid power cylinders positioned on opposite sides of the carriage frame each having a piston rod extending from one end, said fluid power cylinders and piston rods acting along respective lines of thrust between said carriage frame and points of application on the respective torque arms,
  • each of said lines of thrust having essentially the same angular relationship with respect to a radius R in the respective torque arms from the effective centers of said pivot mountings to said points of application as the angular relationship between the di rection of belt tension force exerted by the taut casting belt on said one hollow roll and a radius R, in the respective torque arms from said effective pivot mounting centers to the axis of the hollow roll,
  • a symmetrical synchronized belt-steering and tensioning system for use in a twin-belt continuous metal casting machine as claimed in claim 5, in which:
  • said pair of consistent, predictable force-applying means act between said carriage frame and points of application on said torque arms
  • said points of application on said torque arms being at a greater radius from the effective centers of the respective pivot mountings than the radius from the axis of said one hollow roll to the effective centers of the respective pivot mountings
  • said pair of steering means are a pair of rotatable eccentric shafts positioned on opposite sides of the carriage frame and included in the respective pivot mountings,
  • a pair of steering arms are provided on opposite sides of the carriage frame, said steering arms being eonnccted to the respective rotatable eccentric shafts,
  • said synchronizing means is a steering synchronizing shaft extending across the carriage between its opposite sides and being coupled to said pair of steering arms for moving said steering arms in opposite directions upon actuation of said synchronizing shaft,
  • a symmetrical synchronized belt-steering and tensioning system for use in a twin-belt continuous metal casting machine as claimed in claim 5, in which:
  • said pair of consistent, predictable force-applying means are a pair of fluid power cylinders each having a piston rod extending therefrom with trunnions on each of the cylinders,
  • each of said torque arms including a cylinder support member rigidly connected to the torque arm and extending parallel to and spaced from the torque arm.
  • the cylinders being mounted between the respective torque arms and said cylinder support members with said trunnions being journaled in the torque arm and bearing support member, respectively, and with the piston rods being pivotally connected to the carriage frame by pivot pins, and
  • the cylinders are sufficiently short to lie within a projection of the belt path line passing around said hollow roll to facilitate installation and removal of the casting belt without mechanical interference.
  • a symmetrical synchronized belt-steering and tensioning system for use in a twinbelt continuous metal casting machine as claimed in claim 12, in which:
  • one of said bearings encircling said squaring shaft is arranged to transmit axial thrust between said squaring shaft and said one hollow roll
  • skewing axis control means are mounted on said carriage frame, said skewing axis control means being effectively coupled to said squaring shaft near one end at a point on a line extended through the axes of said trunnions for both of said cylinders for preventing said squaring shaft from moving in an axial direction along said line to assure that said hollow roll is skewed about a predetermined point on said line mid-way between said cylinders.
  • a symmetrical synchronized belt-steering and tensioning system for use in a twin-belt continuous casting machine as claimed in claim ll, in which:
  • a pair of self-aligning spherical bushings are pro vided, one of said bushings being mounted on each of said eccentric shafts, and
  • a symmetrical synchronized belt-steering and tensioning system for use in a twin-belt continuous metal casting machine of the type in which a casting region is defined between spaced parallel portions of the two casting belts, said system comprising:
  • a frame for supporting and revolving a casting belt, said frame having a pair of main rolls at opposite ends, said rolls extending parallel to each other and also parallel to the plane of the casting region for defining an oval shaped path around which the casting belt is revolved,
  • At least one of said main rolls being hollow
  • a pair of bearings encircling said squaring shaft for mounting said one hollow roll on said squaring shaft, one of said bearings being mounted near each end of said one hollow roll providing rotation of said roll about said squaring shaft,
  • a pair of consistent, predictable force-applying means positioned on opposite sides of the carriage frame, one of said force-applying means being associated with each of said torque arms urging both of said torque arms simultaneously to swing about said pivot mountings for moving said one hollow roll in a direction away from the other main roll for tightening the casting belt,

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Continuous Casting (AREA)
  • Forging (AREA)
US350600A 1973-04-12 1973-04-12 Symmetrical synchronized belt-steering and tensioning system and apparatus for twin-belt continuous metal casting machines Expired - Lifetime US3878883A (en)

Priority Applications (17)

Application Number Priority Date Filing Date Title
US350600A US3878883A (en) 1973-04-12 1973-04-12 Symmetrical synchronized belt-steering and tensioning system and apparatus for twin-belt continuous metal casting machines
NO741232A NO137422C (no) 1973-04-12 1974-04-04 Apparat for stramning av baand i kontinuerlige metallstoepemaskiner med to baand
ZA00742290A ZA742290B (en) 1973-04-12 1974-04-09 Symmetrical synchronized belt-steering and tensioning system and apparatus for twin-belt continuous metal casting
JP49041603A JPS594225B2 (ja) 1973-04-12 1974-04-10 ツインベルトレンゾクキンゾクチユウゾウヨウ ノ ドウキテキ カツ タイシヨウテキニ ベルトオソウコウシキンチヨウスル ソウチ
SE7404935A SE407348B (sv) 1973-04-12 1974-04-10 Bandgjutmaskin
AU67724/74A AU485986B2 (en) 1973-04-12 1974-04-10 Symmetrical synchronized belt-steering and tensioning system and apparatus for twin-belt continuous metal casting
BR2879/74A BR7402879D0 (pt) 1973-04-12 1974-04-10 Aparelho para tensionar e dirigir correia
FR7412609A FR2225235B1 (enrdf_load_stackoverflow) 1973-04-12 1974-04-10
CA197,420A CA1025175A (en) 1973-04-12 1974-04-11 Symmetrical synchronized belt-steering and tensioning system and apparatus for twin-belt continuous metal casting
IN820/CAL/74A IN141893B (enrdf_load_stackoverflow) 1973-04-12 1974-04-11
CH508474A CH596907A5 (enrdf_load_stackoverflow) 1973-04-12 1974-04-11
DE2417682A DE2417682C2 (de) 1973-04-12 1974-04-11 Bandspannvorrichtung für eine Zwillingsband-Stranggießmaschine
GB1640274A GB1474933A (en) 1973-04-12 1974-04-11 Twin-belt continuous casting machine
IT21346/74A IT1009832B (it) 1973-04-12 1974-04-12 Sistema ed apparecchio per orien tare e tensionare in modo simme trico e sincronizzato le cinghie di una macchina a doppia cinghia per la colata continua di un me tallo
BE143147A BE813657A (fr) 1973-04-12 1974-04-12 Procede et dispositif pour la tension et le guidage synchronise et symetrique de courroies jumelees de machines a couler en continu un metal
US05/474,617 US3949805A (en) 1973-04-12 1974-05-30 Symmetrical belt tensioning system and apparatus for twin-belt continuous casting machines
US05/570,208 US3963068A (en) 1973-04-12 1975-04-21 Symmetrical synchronized belt-steering system and apparatus for twin-belt continuous metal casting machines

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US350600A US3878883A (en) 1973-04-12 1973-04-12 Symmetrical synchronized belt-steering and tensioning system and apparatus for twin-belt continuous metal casting machines

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US05/474,617 Division US3949805A (en) 1973-04-12 1974-05-30 Symmetrical belt tensioning system and apparatus for twin-belt continuous casting machines
US05/570,208 Division US3963068A (en) 1973-04-12 1975-04-21 Symmetrical synchronized belt-steering system and apparatus for twin-belt continuous metal casting machines

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US3878883A true US3878883A (en) 1975-04-22

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US (1) US3878883A (enrdf_load_stackoverflow)
JP (1) JPS594225B2 (enrdf_load_stackoverflow)
BE (1) BE813657A (enrdf_load_stackoverflow)
BR (1) BR7402879D0 (enrdf_load_stackoverflow)
CA (1) CA1025175A (enrdf_load_stackoverflow)
CH (1) CH596907A5 (enrdf_load_stackoverflow)
DE (1) DE2417682C2 (enrdf_load_stackoverflow)
FR (1) FR2225235B1 (enrdf_load_stackoverflow)
GB (1) GB1474933A (enrdf_load_stackoverflow)
IN (1) IN141893B (enrdf_load_stackoverflow)
IT (1) IT1009832B (enrdf_load_stackoverflow)
NO (1) NO137422C (enrdf_load_stackoverflow)
SE (1) SE407348B (enrdf_load_stackoverflow)
ZA (1) ZA742290B (enrdf_load_stackoverflow)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4008750A (en) * 1975-04-15 1977-02-22 Alcan Research And Development Limited Continuous casting of metals
US4239081A (en) * 1979-05-30 1980-12-16 Asarco Incorporated Side dam apparatus for use in twin-belt continuous casting machines
US4260008A (en) * 1979-05-30 1981-04-07 Asarco Incorporated Side dam apparatus for use in twin-belt continuous casting machines
FR2492696A1 (fr) * 1980-10-27 1982-04-30 Hazelett Strip Casting Corp Procede et dispositif de coulee continue de metal, du type a deux bandes
US4537243A (en) * 1980-10-22 1985-08-27 Hazelett Strip-Casting Corporation Method of and apparatus for steam preheating endless flexible casting belt
EP0295080A3 (en) * 1987-06-08 1989-10-11 Nippon Steel Corporation Twin belt type casting machine and method of casting by using the same
US4921037A (en) * 1988-07-19 1990-05-01 Hazelett Strip-Casting Corporation Method and apparatus for introducing differential stresses in endless flexible metallic casting belts for enhancing belt performance in continuous metal casting machines
US5125217A (en) * 1990-07-31 1992-06-30 Ishida Scales Mfg. Co. Ltd. Apparatus for pulling bag-making material for form-fill-seal packaging machine
US5477912A (en) * 1993-09-28 1995-12-26 Aluminum Company Of America Roll for use in a belt caster and an associated method
US5735783A (en) * 1995-06-02 1998-04-07 Raahen Tevo Oy Arrangement in connection with a spreader roll drive
EP0868953A3 (en) * 1997-03-04 1999-02-03 Hazelett Strip-Casting Corporation Method and apparatus for steering a casting belt in a continuous metal-casting machine
US6482141B1 (en) 2001-07-25 2002-11-19 Spencer Johnston Company Flexible end supporting arrangement for direct drive adjustable spreader rolls
US6843762B2 (en) 2000-12-18 2005-01-18 Spencer Johnston Company Spreader roll
US7156147B1 (en) 2005-10-19 2007-01-02 Hazelett Strip Casting Corporation Apparatus for steering casting belts of continuous metal-casting machines equipped with non-rotating, levitating, semi-cylindrical belt support apparatus
US20110020972A1 (en) * 2009-07-21 2011-01-27 Sears Jr James B System And Method For Making A Photovoltaic Unit
US20110036530A1 (en) * 2009-08-11 2011-02-17 Sears Jr James B System and Method for Integrally Casting Multilayer Metallic Structures
US20110036531A1 (en) * 2009-08-11 2011-02-17 Sears Jr James B System and Method for Integrally Casting Multilayer Metallic Structures
CN112046982A (zh) * 2020-08-12 2020-12-08 久恒理树 一种自动导引搬运装置及其作业方法

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2380833A1 (fr) * 1977-02-18 1978-09-15 Alcan Res & Dev Machine de coulee continue de metaux
CN101920318B (zh) * 2010-09-20 2012-12-19 中国重型机械研究院有限公司 一种连铸驱动辊的双向驱动结构的设计方法

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3167830A (en) * 1960-12-08 1965-02-02 Hazellett Strip Casting Corp Continuous metal casting apparatus
US3310849A (en) * 1965-02-15 1967-03-28 Hazelett Strip Casting Corp Continuous metal casting apparatus
US3621987A (en) * 1968-09-05 1971-11-23 Grace W R & Co System for guiding the travel of a belt supported by a rotary drum
US3682362A (en) * 1971-03-15 1972-08-08 Rockford Servo Corp Web edge sensing and guiding apparatus

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3399582A (en) * 1967-12-26 1968-09-03 Henry Robert Randall Shaft adjustment apparatus and power transmission means

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3167830A (en) * 1960-12-08 1965-02-02 Hazellett Strip Casting Corp Continuous metal casting apparatus
US3310849A (en) * 1965-02-15 1967-03-28 Hazelett Strip Casting Corp Continuous metal casting apparatus
US3621987A (en) * 1968-09-05 1971-11-23 Grace W R & Co System for guiding the travel of a belt supported by a rotary drum
US3682362A (en) * 1971-03-15 1972-08-08 Rockford Servo Corp Web edge sensing and guiding apparatus

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4008750A (en) * 1975-04-15 1977-02-22 Alcan Research And Development Limited Continuous casting of metals
US4239081A (en) * 1979-05-30 1980-12-16 Asarco Incorporated Side dam apparatus for use in twin-belt continuous casting machines
US4260008A (en) * 1979-05-30 1981-04-07 Asarco Incorporated Side dam apparatus for use in twin-belt continuous casting machines
US4537243A (en) * 1980-10-22 1985-08-27 Hazelett Strip-Casting Corporation Method of and apparatus for steam preheating endless flexible casting belt
FR2492696A1 (fr) * 1980-10-27 1982-04-30 Hazelett Strip Casting Corp Procede et dispositif de coulee continue de metal, du type a deux bandes
US4367783A (en) * 1980-10-27 1983-01-11 Hazelett Strip-Casting Corporation Method and apparatus for continuous casting of metal under controlled load conditions
EP0295080A3 (en) * 1987-06-08 1989-10-11 Nippon Steel Corporation Twin belt type casting machine and method of casting by using the same
US4905753A (en) * 1987-06-08 1990-03-06 Nippon Steel Corporation Twin belt type casting machine
AU607226B2 (en) * 1987-06-08 1991-02-28 Mitsubishi Heavy Industries, Ltd. Twin belt type continuous casting
US4921037A (en) * 1988-07-19 1990-05-01 Hazelett Strip-Casting Corporation Method and apparatus for introducing differential stresses in endless flexible metallic casting belts for enhancing belt performance in continuous metal casting machines
US5125217A (en) * 1990-07-31 1992-06-30 Ishida Scales Mfg. Co. Ltd. Apparatus for pulling bag-making material for form-fill-seal packaging machine
US5477912A (en) * 1993-09-28 1995-12-26 Aluminum Company Of America Roll for use in a belt caster and an associated method
US5735783A (en) * 1995-06-02 1998-04-07 Raahen Tevo Oy Arrangement in connection with a spreader roll drive
EP0868953A3 (en) * 1997-03-04 1999-02-03 Hazelett Strip-Casting Corporation Method and apparatus for steering a casting belt in a continuous metal-casting machine
US6026887A (en) * 1997-03-04 2000-02-22 Hazelett Strip-Casting Corporation Steering, tensing and driving a revolving casting belt using an exit-pulley drum for achieving all three functions
EP1588788A3 (en) * 1997-03-04 2006-03-08 Hazelett Strip-Casting Corporation Tensioning, steering and driving a revolving casting belt using an exit-pulley drum for achieving all three functions
US6843762B2 (en) 2000-12-18 2005-01-18 Spencer Johnston Company Spreader roll
US6482141B1 (en) 2001-07-25 2002-11-19 Spencer Johnston Company Flexible end supporting arrangement for direct drive adjustable spreader rolls
US7156147B1 (en) 2005-10-19 2007-01-02 Hazelett Strip Casting Corporation Apparatus for steering casting belts of continuous metal-casting machines equipped with non-rotating, levitating, semi-cylindrical belt support apparatus
US20110020972A1 (en) * 2009-07-21 2011-01-27 Sears Jr James B System And Method For Making A Photovoltaic Unit
US7888158B1 (en) 2009-07-21 2011-02-15 Sears Jr James B System and method for making a photovoltaic unit
US20110036530A1 (en) * 2009-08-11 2011-02-17 Sears Jr James B System and Method for Integrally Casting Multilayer Metallic Structures
US20110036531A1 (en) * 2009-08-11 2011-02-17 Sears Jr James B System and Method for Integrally Casting Multilayer Metallic Structures
CN112046982A (zh) * 2020-08-12 2020-12-08 久恒理树 一种自动导引搬运装置及其作业方法
CN112046982B (zh) * 2020-08-12 2022-05-17 久恒理树 一种自动导引搬运装置及其作业方法

Also Published As

Publication number Publication date
CA1025175A (en) 1978-01-31
IN141893B (enrdf_load_stackoverflow) 1977-04-30
JPS5026725A (enrdf_load_stackoverflow) 1975-03-19
DE2417682A1 (de) 1974-11-07
NO137422B (no) 1977-11-21
FR2225235A1 (enrdf_load_stackoverflow) 1974-11-08
ZA742290B (en) 1975-03-26
BR7402879D0 (pt) 1974-11-19
AU6772474A (en) 1975-10-16
SE7404935L (enrdf_load_stackoverflow) 1975-01-20
IT1009832B (it) 1976-12-20
DE2417682C2 (de) 1985-01-10
NO137422C (no) 1978-03-01
GB1474933A (en) 1977-05-25
FR2225235B1 (enrdf_load_stackoverflow) 1978-11-17
NO741232L (no) 1974-10-15
BE813657A (fr) 1974-07-31
SE407348B (sv) 1979-03-26
JPS594225B2 (ja) 1984-01-28
CH596907A5 (enrdf_load_stackoverflow) 1978-03-31

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