US3546913A - Method and means for obtaining high modulus rolling mills - Google Patents
Method and means for obtaining high modulus rolling mills Download PDFInfo
- Publication number
- US3546913A US3546913A US682056A US3546913DA US3546913A US 3546913 A US3546913 A US 3546913A US 682056 A US682056 A US 682056A US 3546913D A US3546913D A US 3546913DA US 3546913 A US3546913 A US 3546913A
- Authority
- US
- United States
- Prior art keywords
- mill
- rolls
- roll
- work
- rolling
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B29/00—Counter-pressure devices acting on rolls to inhibit deflection of same under load, e.g. backing rolls ; Roll bending devices, e.g. hydraulic actuators acting on roll shaft ends
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
- B21B31/02—Rolling stand frames or housings; Roll mountings ; Roll chocks
- B21B31/028—Prestressing of rolls or roll mountings in stand frames
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B37/00—Control devices or methods specially adapted for metal-rolling mills or the work produced thereby
- B21B37/16—Control of thickness, width, diameter or other transverse dimensions
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
- B21B31/02—Rolling stand frames or housings; Roll mountings ; Roll chocks
Definitions
- the mill stand is of the four-high variety and includes pressure means coupled for example to the backup roll structures for applying a predetermined prestressing force to the housing and rolls.
- Means are bearingly inserted between the work rolls and more particularly between the bearing chocks thereof to cause at least a portion of the reactive equivalent of the prestressing force to assume a substantially serpentine path through the work rolls and the backup rolls, their bearing chocks, and associated components.
- the present invention relates to strip or plate, hot or cold rolling mills and the like and more particularly to a prestressed, high modulus mill stand for such mills.
- the roll gap or the separation between the work rolls of the mill stand must remain at precisely the rel quired size.
- the variable separating forces acting upon the work rolls from the deformation of the rolled material is transmitted through the backup rolls to the frame of the mill stand and causes stretching of the frame and deflection and flattening of both the work rolls and the backup rolls.
- the elastic deformation of the mill stand also includes a bowing deformation of the work rolls and the backup rolls. Stretch and other deformations in the mill stand vary the thickness of the rolled material, while bowing deformations of the rolls affect both the planarity and average thickness of the rolled material.
- the problems associated with dimensional control of the strip or plate constitute esssentially the single problem represented by the summation of these mill stand deformations.
- the major facets of this problem comprise variable mill housing stretch and the flattening aspects of roll deforma- "ice tion on the one hand and the variable bowing of the work and backup rolls on the other hand.
- Hot rolling mills having exit speeds of 4000 feet per minute or over and cold rolling mills having speeds in excess of 6000 feet per minute are in use or are contemplated at the present time.
- the rolling material deformation or rolling force (R is the most predominant contributor to gauge variations.
- the inherent accuracy of a rolling mill stand depends upon the mill modulus which is determined by the force required to establish a specific amount of total mill stand deformation.
- the mill modulus is cognizant of the summation of deformation factors including stretch in the mill stand housing, the individual deformations of the screwdowns and bearings chocks, flattening of the work and backup rolls and the maximum bowing displacements of the work and backup rolls.
- the mill modulus can be expressed in terms of tons per lineal inch or in pounds per lineal mil of total mill stand deformation.
- the mill modulus can also be stated as pounds of force required to produce a deviation of one mil or a fraction of a mil in gauge at the center line of the mill stand, and is representative of both gauge and maximum planarity deviations.
- Fox 3,024,679 provides means for variably bending the work rolls, which reduces the inventory of crowned rolls to some extent, but does not eliminate the necessity of gauge control or of changing crowns for substantial changes in rolling schedules.
- the work roll balance cylinders must be deenergized and strip or other rolled material must be threaded through the mill before the Fox arrangement can be activated. As a result, a quantity of strip may be lost.
- the backup rolls are bent by applying forces to projecting or canti lever sections of the backup roll journals.
- the bending forces are in the same direction as the reactive rolling forces with the result that the loads upon the backup roll bearings are multiplied.
- the bending means which are coupled to each cantilevered journal section, delay roll changes by their required removel, and must be readjusted for each change in roll crown or size.
- the degree of deflection of bowing of the backup rolls is a significant factor in computing the overall mill modulus.
- the bowing of the backup rolls becomes substantially invariable.
- a single pair of work or backup rolls that is to say a single crowning compensation, can be employed for all rolled material handled by the mill independently of dimensional variation (both thickness and width) of the rolled material, as long as the maximum rolling force remains within the designed capacity of the mill stand and the prestressing force as described below, remains unchanged.
- only a single crowning compensation is necessary for a given prestressing force regardless of the number of rolling schedules used with such prestressing force.
- the inventory of variably crowned rolls needed by the mill operator can be considerably reduced.
- prestressed mill housings While the use of prestressed mill housings produces some improvement in gauge control, it fails almost entirely to solve the basic problem which in a high speed strip mill must be the complete elimination of the requirement of gauge and planarity corrections. Of greater significance is the failure of prestressed mill housings or partially prestressed mill stands, as proposed heretofore, to exhibit any eifect whatsoever upon that aspect of dimensional control involved in maintaining planarity of the rolled material.
- Theextremely high mill modulus provided by my invention results from the application of prestressing forces to substantially all of the components of the mill stand.
- the adequately high mill modulus provided by my novel mill stand results from the summation of prestressing forces applied to the mill stand housing, the screwdowns, both the backup bearing chocks and the work roll bearing chocks, and the work rolls and backup rolls to cause both preflattening and prebowing thereof.
- the summation of the forces applied to the backup and work rolls equal the total prestressing force of the mill stand.
- the preflattening and prebowing of the work and backup rolls thus established becomes invariable irrespective of subsequently applied rolling forces, as long as the latter forces are maintained at a value below the imposed prestressing force.
- a rolling mill stand comprising a mill housing, a pair of work rolls between which elongated rolled material is to be rolled, a pair of backup rolls respectively engaging said work rolls, individual mounting means for mounting each of said rolls in said housing, pressure means coupled to said backup roll mounting means for applying a predetermined prestressing force to said housing, and additional means bearingly inserted between said work roll mounting means for causing at least a portion of the reactive equivalent of said prestressing force to assume a path through said work rolls and said backup rolls and the mounting means therefor.
- mounting means for each of said work rolls include a pair of bearing chocks coupled respectively to the ends thereof, and said additional means includes a pair of elongated wedge members inserted respectively between juxtaposed pairs of work roll chocks for selectively establishing the work roll gap and the thickness of said material existing from said stand.
- each of said wedge members is provided with stop means thereon engageable with said work roll chocks for determining a roll-changing position of said work roll chocks.
- FIG. 1 is a schematic structural view and force diagram of a partially stressed mill stand in accordance with the prior art for purposes of comparison;
- FIG. 2 is a similar diagram of a fully stressed mill stand arranged in accordance with my invention.
- FIG. 2A is a partial cross sectional view of the apparatus as shown in FIG. 2 taken generally along reference line IIA-IIA thereof;
- FIG. 3 is a partially sectioned side elevational view of an improved mill stand arranged according to our invention and showing an exemplary form of prestressing means utilized therein;
- FIG. 4 is a partial vertically sectioned view of the apparatus as shown in FIG. 3;
- FIGS. 5 and 6 are partial, enlarged sectioned views illustrating operating and roll changing positions of the prestressing means.
- FIG. 7 is a top plan view of the apparatus as shown in FIG. 3.
- FIGS. 1 and 2 of the drawings a marked contrast is immediately evident between the typical prestressed mill housing (partially stressed mill stand 11) of the prior art (FIG. 1) and the fully stressed, high modulus mill stand 33 of our invention (FIG. 2).
- a reactive separating force is applied to legs 9 of bearing chocks 10 of the backup rolls 12 by some means such as a column, wedge or screw, denoted generally by the reference characters 14, are used, and by known means are employed to vary the prestressing force in an attempt to control gauge and compensate for the inherent inaccuracy of these stands.
- the bearing chocks 16 for the work rolls 18 are confined between the legs of the backup bearing chocks 10 in the conventional manner.
- the lower work roll bearing chock 16 and the lower backup roll bearing chock 10 are inclined generally in the same direction when the mill stand is loaded as by the insertion of strip or plate material 20 between the work rolls 18.
- the upper work roll chock 16 and backup roll chock 10 are also inclined in the same direction but generally opposite to the lower backup roll bearing chocks.
- the various inclinations of the bearing chocks are shown here in exaggerated form for purposes of illustration. In the arrangement of FIG. 1 the inclination of the chocks and, of course the work roll gap S and roll bowing deformation vary depending upon the instantaneous value of LRF, as described herein.
- the mill stand housing 22 is prestressed by means of a pair of cylinders 24 each of which exerts a force (P /2) upon the mill stand housing 22, which force is opposed by the screwdowns 26 at the upper end of the housing 22.
- P /2 a force
- the entire prestressing force is transmitted through the backup roll chocks 10 and the prestressing wedge 14 or similar columnar support.
- the wedges 14 or an equivalent maintains a nominal roll gap width S
- FIG. 2 the radically different force diagram associated with the fully stressed, high modulus mill stand 33 of the present invention is readily apparent.
- a structurally similar mill stand is shown, with similar reference characters with primed accents denoting similar components of FIG. 1.
- a suitable wedge, columnar support, piston and cylinder arrangement, or other suitable separating means denoted generally by the wedges 34, are interposed directly between the work roll bearing chocks 16.
- the total prestressing force (P thus is applied, as in FIG. 1 to the upper and lower ends of the housing 22 of the mill stand 33.
- each of the work roll chocks 16 are inclined in an opposite direction to its associated backup roll
- Conventional bearing housing are provided in the mill stand to permit the aforedescribed inclinations, which, as noted previously, are exaggerated for purposes of illustration.
- each work roll 18 and its associated backup roll 12 are bowed in different directions, for the same reason.
- the bowing desirably is compensated by a negative work roll crown 35 and a positive backup roll crown 37 to provide a fiat strip or plate 20.
- the rolled material if desired, can be provided with a positive or negative crown for guiding purposes as an appropriate selection of roll crowns.
- the gap S retains perfect rectangularity and constant width as long as the summation of rolling forces denoted by force arrows d in the strip material 20' or force arrows r in the work rolls 18 do not exceed the prestressing force P Accordingly, both the thickness of the strip 20 and its planarity are precisely maintained by the work roll 18 regardless of variations in the total rolling force, as long as R P
- every component of the mill stand is prestressed for maximum predeformation with the exception of the relatively small work roll portions 36a adjacent their surfaces 36 (FIG. 2A) which are in actual engagement with the plate or strip 20'. These work roll portions protrude beyond the work roll journals 38 and therefore are not prestressed.
- This area which includes only the work roll portions 36a results in a maximum total deformation of only 0.0042 inch for the entire mill stand of our invention at a design rolling force of 3,500,000 pounds in contrast to 0.0885 inch at 3,000,000 pounds (Table I) for a standard mill and 0.0663 inch at 3,000,000 pounds for a conventional prestressed mill (FIG. 1).
- the prestressing force interposed upon the mill housing 22', the screwdowns 26 (used in our novel mill to enable roll changes not for roll ga control), the prestressing cylinders 24', upper and lower backup roll chocks 10, upper and lower work roll chocks 16, and the backup and work rolls 12', 18 are not intended to be varied during operation of the rolling mill as long as zr P
- the only portions of the entire mill stand 33 which are subject to variable deformation are the work roll surfaces 36 and portions 36a adjacent thereto. Any positive change in rolling force (R during operation of the stand 33 is accompanied by an instantaneous and equivalent unloading of the compression means or wedges 34.
- Screw 0054 Nut .0053 Breaker block- 0045 Bearing journals .0079 Housing top-- 0029 Housing bottom 0039 Housing post 0051 Total, inch 0350 8 Roll deflection C.L. mill 55 wide 0245 strip, inch. 9 Rprlll 1flattening, 55" wide strip,
- the B Standard Mill is provided with a heavier housing (items No. 3) and a larger backup roll diameter (item No. l(b)) to reduce the stretch in the mill stand housing and the bending deflection of the backup rolls.
- the B Standard Mill produces slightly less total rolling reflection (item No. 11) than that of an A Standard Mill.
- a similarly small improvement is evinced by the Partially Prcstresscd Mill which eliminates the relatively small mill deflections of the mill housing and components associated therewith including the wedge 14 to FIG. 1 (item No. 7).
- the partially stressed mill increases the mill modulus (item Nos. 12 and 13) by substantially twice the amount contributed by the ruggedized or B Standard Mill.
- Item No. 16 shows that a typical Fully Stressed Mill according to our invention (FIG. 2) has a mill modulus of 2456% greater than that of a conventional mill (A Standar while the Partially Stressed Mill (FIG. 1) offers an improvement in mill modulus of only 33%.
- FIGS. 3 and 4 of the drawings an exemplary construction of a novel mill stand incorporating the prestressing arrangement shown in FIG. 2, is illustrated.
- similar reference characters denote similar components of FIG. 2.
- the construction of the mill stand 33 of FIGS. 3 and 4 is essentially similar to conventional mill construction with the exception of the wedge members 34 and components associated therewith and the use of a lighter housing (Table I) having for this purpose deep indentations 41, 43, 45.
- the latter two changes are necessitated by passage of the prestressing force (P through the work roll chocks 16', their bearings 44 and the work rolls themselves (FIG. 2).
- the Work roll bearings 44 are shown as comprising six circumferential rows of roller bearings 46 instead of the usual four rows. Other equivalent bearing means, of course, can be substituted.
- the center lines of the wedges 34 conform to the mill pass line 48 inasmuch as the lateral position of the wedges 34, as subsequently explained, determine the initial height of the work roll gap S (FIG. 2).
- the gap S' can be varied by moving the Wedges transversely of the rolls by means of jack screws 50 driven by motor and gear arrangements denoted generally by the reference character 52 (FIG. 7).
- the jack screw 50 is provided with a shouldered nut 54, which is slidably movable in an expanded cavity portion of piston 56.
- the piston 56 is mounted for reciprocatory movement in cylinder 58 and is secured at its other end to piston rod 60, the distal end of which is connected to the wedge 34.
- the sliding engagement of the jack screw nut 54 within the piston 56 is delimited inwardly by an inner annular shoulder 62 of the piston 56.
- the central wedge portion 64 can be moved transversely of the rolls while in adjusting engagement with the work roll chocks 16' by rotating the jack screw 50 in either rotational direction. This adjustment is made only for the purpose of establising the initial roll gap S' which if correctly set, need not thereafter be changed (for a given rolling schedule).
- the shoulder 62 of the piston 56 is maintained in engagement with the jack screw nut 54 by an opposing force supplied by cylinder 66 having distal end 68 of its piston rod 70 connected to the opposite end of the associated wedge 34.
- each wedge 34 and thus the variation in the work roll gap S' is limited by stop member 72 (FIG. 5) which is normally movable between stop surfaces 74 and camming surfaces 76 of the work roll chocks 16'.
- a similar stop 78 is secured to the other end of the wedge 34 for roll changing purposes as described below in connection with FIG. 6.
- the adjusting movements as defined by the solid and chain outline positions of the stops 72, 78 of each wedge 34 determines the roll gap width and gauge of the material exiting from a given mill stand.
- the wedge 34 need not be moved during the rolling operation to compensate for deviations in gauge, as such deviations are prevented by the use of a fully stressed mill stand as explained above.
- the hydraulic cylinders 66 (FIG. 7) are actuated to quickly move the wedges 34 to their roll changing positions as shown in FIG. 6.
- the wedge stops 72, 78 are then positioned in contact with complementary surfaces 82 and 84 respectively of the work roll chocks 16' to separate the work roll chocks 16' while the work rolls 18 are being withdrawn therefrom and new rolls substituted.
- the hydraulic cylinders 66 When the hydraulic cylinders 66 are thus actuated, the pistons 56 are slidably withdrawn from engagement with the jack screw nuts 54 to permit quick movement of the wedges 34 to the left as viewed in FIG. 3.
- the desired work roll gap S' (FIG. 2) is established by movement of the wedges 34, as described above, with the central tapering portions 64 of the Wedges in engagement with the associated work roll chocks 16' (FIGS. 3 and 5). With the work roll gap S thus established, a strip 20' or other material to be rolled is then threaded between the work rolls 18 and the rolling operation is commenced. Vernier adjustment in the roll gap S' can be made if desired by adjusting the valving arrangement 31 associated with the cylinders 24'.
- a method for the dimensional control of elongated rolled material reduced in a rolling mill including the steps of mounting work rolls and back-up rolls within said mill and in respective engagement with me another, storing in said mill substantially constant orce at least equal to the maximum rolling force required for the reduction of said material, directing at least a portion of said force to maintain a predetermined opening between work rolls of said mill, transferring at least a portion of the stored force to the material for reduction between said work rolls, diverting a reactive equivalent of said stored force in a path entirely through said work rolls and said back-up rolls, positioning said work roll mounting independently of said back-up roll mounting, and maintaining said rolling force within a predetermined range extending below said constant force, whereby substantially all of the components of said mill are prestressed and predeformed to eliminate subsequent deformation during the rolling operation and to maintain dimensional stability of said material irrespective of variations in rolling force within said range and within the limits imposed by said constant force.
- a rolling mill stand comprising a mill housing, a pair of work rolls between which elongated rolled materialis to be rolled, a pair of back-up rolls respectively engaging said work rolls along contact areas coextending substantially with the length of roll faces thereof, individual mounting means for mounting each of said rolls in said housing, means for positioning said back-up roll mounting means independently of said work roll mounting means, prestressing pressure means coupled to said backup roll mounting means for applying a predetermined prestressing force to said housing only directly through said contact areas, and additional prestressing means bearingly inserted between said work roll mounting means for urging said work rolls apart and for causing a reactive equivalent of said prestressing force to assume a path through said work rolls and said backup rolls including the roll faces thereof.
- mounting means for each of said work rolls include a pair of bearing chocks coupled respectively to the ends thereof, and said additional means includes a pair of elongated wedge members inserted respectively between juxtaposed pairs of said work roll chocks for selectively establishing the work roll gap and the thickness of said material exiting from said stand.
- each work roll and the adjacent one of said backup rolls are bowed in opposite directions by said prestressing force.
- each of said wedge members is provided with stop means thereon engageable with said work roll chocks for determining a roll-changing position of said work roll chocks.
- each of said work rolls is provided with a negative crown
- each of said backup rolls is provided with a positive crown
- bearing chocks are provided with additional stop surfaces disposed adjacent the path of movement of said stop means for determining the limits of roll gap adjusting movement of said wedge members.
- said drive means include opposing drive mechanisms coupled to each of said wedge members, said mechanisms being capable of moving the associated wedge members relatively rapidly in a single one of said transverse directions and independently of the other associated drive mechanism for rapid insertion of said stop means between said bearing chocks.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Control Of Metal Rolling (AREA)
- Metal Rolling (AREA)
Description
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US68205667A | 1967-11-13 | 1967-11-13 |
Publications (1)
Publication Number | Publication Date |
---|---|
US3546913A true US3546913A (en) | 1970-12-15 |
Family
ID=24738013
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US682056A Expired - Lifetime US3546913A (en) | 1967-11-13 | 1967-11-13 | Method and means for obtaining high modulus rolling mills |
Country Status (4)
Country | Link |
---|---|
US (1) | US3546913A (en) |
DE (1) | DE1807617A1 (en) |
FR (1) | FR1587193A (en) |
GB (1) | GB1204750A (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1996026022A1 (en) * | 1995-02-24 | 1996-08-29 | Demag Italimpianti S.P.A. | Shoulder for rolling mill stand with open-type uprights |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1980570A (en) * | 1932-08-13 | 1934-11-13 | United Eng Foundry Co | Rolling mill |
US2430410A (en) * | 1943-03-27 | 1947-11-04 | Carnegie Illinois Steel Corp | Working pass control for rolling mills |
GB647039A (en) * | 1948-10-18 | 1950-12-06 | Albert Thomas Hughes | Improvements in or relating to rolling mills, rod mills, calenders, and the like |
US3242711A (en) * | 1961-06-28 | 1966-03-29 | Fox Ind Inc | Rolling mill structures |
CA760698A (en) * | 1967-06-13 | D. Stone Morris | Prestressed rolling mill | |
US3422655A (en) * | 1964-05-13 | 1969-01-21 | United Eng Foundry Co | Prestressed rolling mill |
US3611150A (en) * | 1967-06-02 | 1971-10-05 | Hermann Martin Timm | Radio receiver housing forming a continuous shape with control knobs |
-
1967
- 1967-11-13 US US682056A patent/US3546913A/en not_active Expired - Lifetime
-
1968
- 1968-10-08 GB GB47732/68A patent/GB1204750A/en not_active Expired
- 1968-10-23 FR FR1587193D patent/FR1587193A/fr not_active Expired
- 1968-11-07 DE DE19681807617 patent/DE1807617A1/en active Pending
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CA760698A (en) * | 1967-06-13 | D. Stone Morris | Prestressed rolling mill | |
US1980570A (en) * | 1932-08-13 | 1934-11-13 | United Eng Foundry Co | Rolling mill |
US2430410A (en) * | 1943-03-27 | 1947-11-04 | Carnegie Illinois Steel Corp | Working pass control for rolling mills |
GB647039A (en) * | 1948-10-18 | 1950-12-06 | Albert Thomas Hughes | Improvements in or relating to rolling mills, rod mills, calenders, and the like |
US3242711A (en) * | 1961-06-28 | 1966-03-29 | Fox Ind Inc | Rolling mill structures |
US3422655A (en) * | 1964-05-13 | 1969-01-21 | United Eng Foundry Co | Prestressed rolling mill |
US3611150A (en) * | 1967-06-02 | 1971-10-05 | Hermann Martin Timm | Radio receiver housing forming a continuous shape with control knobs |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1996026022A1 (en) * | 1995-02-24 | 1996-08-29 | Demag Italimpianti S.P.A. | Shoulder for rolling mill stand with open-type uprights |
Also Published As
Publication number | Publication date |
---|---|
GB1204750A (en) | 1970-09-09 |
DE1807617A1 (en) | 1969-08-07 |
FR1587193A (en) | 1970-03-13 |
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Owner name: MESTA AND MELLON BANK, N.A., MELLON SQUARE, PITTSB Free format text: SECURITY INTEREST;ASSIGNOR:MESTA MACHINE COMPANY;REEL/FRAME:003861/0980 Effective date: 19810529 |
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Owner name: MESTA MACHINE COMPANY SEVENTH AVE., WEST HOMESTEAD Free format text: RELEASED BY SECURED PARTY;ASSIGNOR:MELLON BANK, N.A., A NATIONAL BANKING ASSOC. AS AGENT (SEE DOCUMENT FOR DETAILS);REEL/FRAME:004101/0198 Effective date: 19830114 Owner name: PENNSYLVANIA ENGINEERING CORPORATION, 32ND ST., A Free format text: MORTGAGE;ASSIGNOR:MESTA ENGINEERING COMPANY A PARTNERSHIP;REEL/FRAME:004101/0185 Effective date: 19830214 Owner name: MESTA ENGINEERING COMPANY, 32ND ST. A.V.R.R., PITT Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:MESTA MACHINE COMPANY;REEL/FRAME:004099/0627 Effective date: 19830215 |