US3910717A - Furnace fan assembly - Google Patents

Furnace fan assembly Download PDF

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Publication number
US3910717A
US3910717A US443340A US44334074A US3910717A US 3910717 A US3910717 A US 3910717A US 443340 A US443340 A US 443340A US 44334074 A US44334074 A US 44334074A US 3910717 A US3910717 A US 3910717A
Authority
US
United States
Prior art keywords
shaft
bearing
fan
fan wheel
furnace
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
Application number
US443340A
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English (en)
Inventor
William L Thome
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Surface Combustion Corp
Grimes Aerospace Co
Original Assignee
Midland Ross Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Midland Ross Corp filed Critical Midland Ross Corp
Priority to US443340A priority Critical patent/US3910717A/en
Priority to CA219,944A priority patent/CA1026291A/en
Priority to JP2030975A priority patent/JPS547604B2/ja
Application granted granted Critical
Publication of US3910717A publication Critical patent/US3910717A/en
Assigned to FL AEROSPACE CORP. reassignment FL AEROSPACE CORP. CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). 9/11/86 AND 1/05/88, OHIO Assignors: MIDLAND - ROSS CORPORATION, CHANGED TO, MIDLAND-ROSS CORPORATION MERGING INTO, MRC MERGER CORP., CHANGED NAME TO
Assigned to SURFACE COMBUSTION, INC. reassignment SURFACE COMBUSTION, INC. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: FL AEROSPACE CORP.
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/059—Roller bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/668—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps damping or preventing mechanical vibrations

Definitions

  • a furnace fan assembly includes a unique bearing [58] F'eld of Search 415M801 219 C; rangement which materially simplifies the fan struc- 64/1 V; 308/168, 194 ture while permitting the fan assembly to rotate at relatively high speeds without transmitting damaging vi- [561 References C'ted brations to the fan mounting structure.
  • the assembly UNITED STATES PATENTS includes a shaft with a fan wheel adjacent one end 961,670 6/1910 Barnheisel 308/194 thereof-
  • the Shaft is journaled at its pp end in a 1,953,540 4/1934 Ogden 415/175 first bearing and a second bearing is positioned be- 2,226,986 12/1940 Wechsberg et a1.... 415/175 tween the first bearing and fan wheel.
  • the second P1688161 bearing is mounted in a resilient support 2,516,252 7/1950 Pellerin....
  • This invention relates generally to a furnace fan assembly and more specifically to the bearing support thereof.
  • the invention is particularly applicable to high speed furnace fans which circulate a hot gaseous medium and will be described with particular reference thereto. However it will be appreciated by those skilled in the art that the invention may have broader applications and may be applied to low speed fans circulating either a hot or cold gaseous medium.
  • High speed furnace fan assemblies basically comprise a shaft or shafts keyed to one another which have at one end a fan wheel mounted thereto integral therewith.
  • the fan wheel may be directly positioned either vertically or horizontally within the furnace enclosure in which case the shaft extends through the furnace wall and appropriate structure, commonly referred to as a fan bung, is used to mount the assembly to the wall.
  • the fan may be mounted in a duct which is in fluid communication with the furnace in which case the shaft extends through the ductwork; such arrangement being commonly referred to as a scroll-type fan.
  • all such arrangements journal the shaft within the mounting structure by at least an outboard bearing spaced near the end of the shaft opposite the fan wheel and an inboard bearing spaced closer to the fan wheel.
  • the fan vibrates to such an extent that damage may be done to the support structure and/or the furnace wall to which the structure is mounted and/or items such as instruments supported by the furnace wall in the vicinity of the fan.
  • the vibration develops such high lateral forces that the shaft is permanently bent which in turn causes higher vibration forces, etc.
  • the fan wheel has been accurately mounted to the fan shaft to coincide with the center thereof and the fan shaft has been accurately aligned in an expensive aligning machine to coincide with the bearings;
  • the shaft has been significantly increased in diameter to rigidize same and expensive bearings employed to journal the shaft;
  • the inboard bearing is spaced as close as possible to the fan wheel to reduce the tendency of the shaft to whip.
  • Fan assemblies furnished in accordance with the above criteria are obviously costly to manufacture and difficult to assemble. lmportantly, when the inboard bearing is moved closely adjacent the fan wheel, it becomes subjected to the hot gaseous medium within the furnace. To prevent heat failure of the bearing, an expensive water jacket surrounding the bearing is usually furnished with the fan assembly. Finally, such fan assemblies may still be suspect of failing from vibration. That is, investigations have indicated vibration will always occur because of the clearance between shaft and bearings, the tolerances encountered in fixing the fan head to the shaft and aligning same, and importantly the fact that thermal stresses produce cracks in the fan head which shift the center of mass of the fan wheel to produce an imbalance in the fan wheel assembly.
  • a furnace fan assembly which comprises a shaft and a fan wheel on the shaft adjacent one end thereof and in contact with the hot gaseous medium within the furnace.
  • a drive mechanism is provided to rotate the shaft and likewise the fan wheel at some predetermined speed, and the shaft and fan wheel are supported by some form of mounting structure.
  • This structure includes a first bearing adjacent the end of the shaft opposite the fan wheel which bearing journals the shaft therein.
  • a second bearing is also applied to the shaft in a position on the shaft between the first bearing and the fan wheel.
  • the second bearing is affixed to a resilient mount.
  • the second bearing moves in an orbital manner relative the axis of the first bearing while the shaft rotates within the bearings.
  • This motion of the shaft which is achieved because of the resilient bearing support substantially reduces the critical speed of the fan wheel and shaft to a value significantly below the operating speed of the fan assembly.
  • rotating a mass above its critical speed significantly reduces the vibration amplitude which might otherwise occur and the fan assembly is thus stabilized.
  • the resilient bearing support besides permitting the fan assembly to achieve a significantly low critical speed acts as a dampener against excessive vibrations when the furnace fan is accelerated past its critical speed.
  • Yet another object of the subject invention is to provide a high speed furnace fan assembly for circulating a hot gaseous medium which has a greater life expectancy than heretofore possible.
  • FIGS. 1, 2 and 3 illustrate different mounting arrangements of the subject furnace fan assembly
  • FIG. 4 is a known graph indicative of vibration forces transmitted by rotating shaft assemblies.
  • FIG. 3A is a schematic of the scroll fan arrangement shown in FIG. 3.
  • Insulated enclosure 11 is shown as a typical construction defined by an exterior lining 17 of sheet metal construction and a layer of refractory material 18 secured to the interior of lining 17.
  • An opening 20 is provided in enclosure 11 for receiving a portion of mounting structure 16 and appropriate super structure indicated generally at 21 extends from lining 17 to support mounting structure 16 as by being bolted or welded thereto.
  • the portion of insulated enclosure 11 shown in FIG. 1 is representative of a removable top wall of a furnace which may be employed for various purposes such as annealing or heat treating, carburizing, carbon baking, etc.
  • Fan wheel 14 is generally a relatively heavy casting, iron or steel, which may be secured to shaft 12, adjacent one end thereof by weld or other means. In FIG. 1, fan wheel 14 is cast with an integral shaft portion 30 extending therefrom which is secured to an upper shaft portion 31 to form a two-piece shaft 12.
  • Shaft portions 30, 31 are joined in end-to-end aligned relation with one anotehr by means of respective interfitting male and female tapered end sections or seats 32, 33 thereon which are drawn together into tight interfitting engagement by a draw rod 34 which extends through a bore 35 in upper shaft portion 31 and is threaded into the tapered male end 32 of lower shaft portion 30.
  • the draw rod 34 is tightened to effect a tight interfitting of the tapered end sections 32, 33 with one another, by means of a draw nut 36 threaded onto the projecting upper end of the draw rod 34.
  • Draw nut 36 bears against a puller-thread protecting nut 38 which assures the axial position of a sheave 39 keyed to the end of shaft 12 opposite the fan wheel end.
  • Suitable motor means comprising a motor 40 and belts 41 engaging sheave 39 is provided for rotating shaft 12 and fan wheel 14.
  • first bearing 45 is self-aligning ball bearing which primarily supports shaft 12 and fan wheel 14 within mounting structure 16 against vertical and lateral movement. This is accomplished by first bearing 45 (which importantly is shown as a ball bearing for reasons to be explained hereafter) which is illustrated to be of the self-aligning type and which is fixed to upper housing 25 by an annular seating ledge 51 therein.
  • Spherical support collar 50 is suitably secured in place against rotation within seating ledge 51 by a set screw 53.
  • a second support collar 55 secured to shaft 12 by set screw 56 prevents shaft 12 from moving axially downwardly.
  • Second bearing 46 is preferably a ball bearing although other types of bearings such as needle or sleeve bearings may be employed.
  • second bearing 46 is supported in a resilient mount preferably an elastomer of known high temperature synthetic material although a low temperature material, such as neop'rene, may be used in certain installations.
  • a resilient mount preferably an elastomer of known high temperature synthetic material although a low temperature material, such as neop'rene, may be used in certain installations.
  • Resilient mount 60 is shown to be a rubber-type bushing which receives the outer race 61 of second bearing 46 in a press fit manner.
  • the rubber bushing 60 may be provided with a radial passage 62 extending therethrough which communicates with a grease tube arrangement 63 for lubricating second bearing 46.
  • the second bearing may be of the type having prepacked lubricant therein.
  • the outer periphery 65 of rubber bushing 60 is securely clamped between the flanges of the lower and upper housing portions 23, 25. This may be accomplished by a number of different arrangements and is easily accomplished by providing the upper housing portion 25 with an integral, annular retainer portion 26 at its flanged end which is shown indented at 68 at its interior.
  • Retainer portion 26 has a thickness slightly less than resilient bushing 60 and a boss 67 is provided at the flange end of lower housing portion 23.
  • Boss 67 and indention 68 extend down the end flat faces of rubber bushing 60 a slight distance (Va-Mainches) so that rubber bushing 60 is slightly compressed and thus secured along its outer periphery and edges when housing portions 23, 25 are bolted together as at 24. With the resilient mount 60 thus secured between a fixed framework and second bearing 46, shaft 12 becomes yieldably supported in a cushioned manner for purposes to be explained hereafter.
  • the furnace fan assembly 10 shown in FIG. 2 is similar to that of FIG. 1 and like parts will be identified by like numbers followed by a prime where applicable and will not be described in further detail herein.
  • the arrangement illustrated in FIG. 2 is especially suitable for use with large size fans wherein fan shaft 12' is coupled at its upper end through a flexible or universal joint-type coupling connected directly to the shaft 100 of motor 40' and at its bottom end connected directly to fan shaft 12'.
  • the bearings (not shown) in the motor 40' rotatably secure motor shaft 100 and the universal joint permits skewed alignment of fan shaft 12' with motor shaft 100.
  • the universal joint and the fixed bearings in motor 40 are herein designated as the first bearing 45' as it should be viewed as the functional equivalent of the first bearing 45 shown in FIG. 1.
  • the resilient mount 60 is to that of FIG. 1 and is held compressed to a fixed support by an annular spacer-retainer 26' to firmly grip the outer edges and outer periphery of the rubber-type bushing.
  • Spacer-retainer 26 should be viewed as the functional equivalent of retainer portion 26.
  • This arrangement includes a radiation shield 103 in place of the water jacket of FIG. 1.
  • Shield 103 may comprise a tube which receives shaft 12' in close fitting relationship and has a flanged end 104 for mounting purposes. If desired, the space between shield 103 and opening 20' in enclosure 11 may be filled with suitable packing material in a known manner for cooling purposes. Alternatively, a plurality of radiation shields may surround the shaft with or without insulation therebetween as known to those skilled in the art.
  • FIG. 3 illustrates still another embodiment of the furnace fan assembly of the subject invention which is similar to that shown in FIGS. 1 and 2 and like parts will be identifiedby like numbers followed by a double prime and will not be described in further detail herein.
  • the furnace fan assembly 10 in FIG. 3 is especially suitable for use with large scroll-type fan arrangements known to those skilled in the art and schematically illustrated as 300 in FIG. 3A wherein the fan extends horizontally through a duct or insulated enclosure 11" which is in communication with the furnace.
  • the mounting structure 16" consists of a solid stepped base for supporting first and second bearings 45", 46". Bearings 45", 46" may comprise ball bearings, each of which is mounted into half-moon supports 200, 201 which in turn are secured to the mounting structure 16'.
  • first bearing 45 would comprise a self-aligning bearing similar to that shown in FIG. I and the secondv bearing 46" would be affixed to resilient mount 60" which would simply comprise a block of resilient material.
  • first and second bearings 45", 46" could comprise known pillow block bearings.
  • This force through G increases in a radially outwardly direction as the rotational speed to of the shaft increases until the critical speed of the shaft and wheel is reached.
  • the critical speed is defined to occur when the rotational speed of the fan wheel and shaft reaches the natural frequency of lateral vibration of the fan assembly defined as w 7 which in turn is a function of the rigidity of the shaft and wheel and the mass thereof.
  • the fan shaft and wheel are.yieldably instead of rigidly supported by virtue of the resilient mount 60 which is shown in each of the embodiments illustrated.
  • This resilient mounting is believed to accomplish two important functions.
  • the resilient mount 60 permits the critical speed of the shaft 12 and fan wheel 14 to be considerably reduced to a value typically between 200 and 400 rpm. That is, shaft 12 rotates within the bearings 45, 46 while the fan wheel and shaft are orbiting about or relative to the first bearing 45.
  • This orbiting path which the shaft and fan wheel assume may be viewed as a cone with its base defined by the movement of the fan wheel and the cone apex at or approximately near the center of first bearing 45.
  • first bearing 45 is a ball bearing which is an ideal bearing for permitting such cone shaped movement.
  • rigidity of the system of the subject invention is considerably reduced from that of the prior art explained above the critical speed significantly decreased.
  • the critical speed when the critical speed is exceeded the force acting through the center of gravity of the fan wheel is directed inwardly with the result that the orbital path of shaft and fan wheel is significantly reduced to stabilize the system. In terms of design criteria this occurs when (/00 is greater than the square root of 2 and may be expressed in terms of operating speeds of the embodiments illustrated as an operating speed of at least 800-900 rpm.
  • the second feature of the resilient mount 60 is that it provides a dampener to the fan assembly which permits the shaft and fan wheel to pass through critical speed without imparting excessive vibrations to the mounting structure 16 and/or insulated enclosure 11.
  • the dampening factor of the resilient mount as same relates to the graph shown in FIG. 4 is not exactly known but is believed to be a function of the position of the mount on a shaft, the hardness of the resilient mount and the dimensions thereof.
  • Fans manufactured in accordance with the invention have utilized'rubber bushings 60 having a hardness between durometer readings of 40-70 which were mounted outboard of enclosure 11 and approximately l-/2 inches in thickness and depth. Such fans have not exhibited excessive vibrations when passing through the critical speed. In this connection it is believed that because the critical speed of the fan assembly is very low, there is rapid acceleration past the critical speed at a time when the mass centrifugal force is at relatively low value.
  • a furnace fan assembly for circulating a hot gaseous medium in a furnace, said assembly comprising:
  • first bearing means including a self-aligning type bearing adjacent the end of said shaft opposite said 'fan wheel for journaling said shaft in a manner which permits said shaft to rotate in a conical path with the apex of said conical path at the center of said bearing,
  • resilient means supporting said second bearing for permitting orbital movement of said second bearing relative the axis of said first bearing while said shaft rotates withinsaid second bearing, said resilient means also dampening vibration of said shaft and said fan wheel while same orbit about said first bearing.
  • said first bearing is defined as including said motor means rotatably driving a motor shaft and a universal joint directly driven by said motor shaft and driving said fan shaft.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Solid-Phase Diffusion Into Metallic Material Surfaces (AREA)
  • Heat Treatments In General, Especially Conveying And Cooling (AREA)
  • Furnace Details (AREA)
US443340A 1974-02-19 1974-02-19 Furnace fan assembly Expired - Lifetime US3910717A (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US443340A US3910717A (en) 1974-02-19 1974-02-19 Furnace fan assembly
CA219,944A CA1026291A (en) 1974-02-19 1975-02-12 Furnace fan assembly
JP2030975A JPS547604B2 (enrdf_load_stackoverflow) 1974-02-19 1975-02-18

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US443340A US3910717A (en) 1974-02-19 1974-02-19 Furnace fan assembly

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US3910717A true US3910717A (en) 1975-10-07

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US443340A Expired - Lifetime US3910717A (en) 1974-02-19 1974-02-19 Furnace fan assembly

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US (1) US3910717A (enrdf_load_stackoverflow)
JP (1) JPS547604B2 (enrdf_load_stackoverflow)
CA (1) CA1026291A (enrdf_load_stackoverflow)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4044570A (en) * 1975-02-28 1977-08-30 Hitachi, Ltd. Refrigerator
FR2684141A1 (fr) * 1991-11-26 1993-05-28 Creusot Loire Dispositif d'entrainement en rotation d'une turbine de brassage des gaz a l'interieur d'un four.
GB2373295A (en) * 2001-03-14 2002-09-18 Howden Power Ltd Method of enhancing the aerodynamic performance of a fan
US20070189889A1 (en) * 2004-03-31 2007-08-16 Tadashi Yokoi Cantilever type vertical axis wind turbine
US20130049594A1 (en) * 2011-08-29 2013-02-28 Tai-Her Yang Electric axial-flow fan having turbine type waterproof enclosure and application thereof
JP2014052164A (ja) * 2012-09-10 2014-03-20 Koyo Thermo System Kk 熱処理装置
US20160018160A1 (en) * 2014-07-18 2016-01-21 Baxley Equipment Co. Fan for drying of lumber
US20210121031A1 (en) * 2019-10-24 2021-04-29 Makita Corporation Dust extractor

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5767085A (en) * 1980-10-09 1982-04-23 Takasago Kogyo Kk Roof tile smoking device

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US961670A (en) * 1905-10-17 1910-06-14 Frederick R Barnheisel Rotary bearing for suspended shafts.
US1953540A (en) * 1929-12-17 1934-04-03 Ermin F Plumb High temperature resistant fan
US2226986A (en) * 1938-03-07 1940-12-31 Coppus Engineering Corp Blower for annealing furnaces and the like
US2244197A (en) * 1936-03-25 1941-06-03 Hessler Christian Rudolph Bearing
US2516252A (en) * 1948-07-07 1950-07-25 Pellerin Norvin Leroy Extractor drive shaft lubricator
US2597405A (en) * 1946-09-28 1952-05-20 American Tool & Machine Co Combined bearing and stabilizing mechanism for centrifugal separators
US2704695A (en) * 1951-07-03 1955-03-22 Ricefield Louis Self-aligning bearings
US3094273A (en) * 1959-06-25 1963-06-18 Ametek Inc Fan assembly

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US961670A (en) * 1905-10-17 1910-06-14 Frederick R Barnheisel Rotary bearing for suspended shafts.
US1953540A (en) * 1929-12-17 1934-04-03 Ermin F Plumb High temperature resistant fan
US2244197A (en) * 1936-03-25 1941-06-03 Hessler Christian Rudolph Bearing
US2226986A (en) * 1938-03-07 1940-12-31 Coppus Engineering Corp Blower for annealing furnaces and the like
US2597405A (en) * 1946-09-28 1952-05-20 American Tool & Machine Co Combined bearing and stabilizing mechanism for centrifugal separators
US2516252A (en) * 1948-07-07 1950-07-25 Pellerin Norvin Leroy Extractor drive shaft lubricator
US2704695A (en) * 1951-07-03 1955-03-22 Ricefield Louis Self-aligning bearings
US3094273A (en) * 1959-06-25 1963-06-18 Ametek Inc Fan assembly

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4044570A (en) * 1975-02-28 1977-08-30 Hitachi, Ltd. Refrigerator
FR2684141A1 (fr) * 1991-11-26 1993-05-28 Creusot Loire Dispositif d'entrainement en rotation d'une turbine de brassage des gaz a l'interieur d'un four.
GB2373295A (en) * 2001-03-14 2002-09-18 Howden Power Ltd Method of enhancing the aerodynamic performance of a fan
US20040042893A1 (en) * 2001-03-14 2004-03-04 Mulholland Ronald G. Method of enhancing the aerodynamic performance of a fan
GB2373295B (en) * 2001-03-14 2005-05-18 Howden Power Ltd Method of enhancing the aerodynamic performance of a fan
US6971840B2 (en) 2001-03-14 2005-12-06 Howden Power Limited Method of enhancing the aerodynamic performance of a fan
US20070189889A1 (en) * 2004-03-31 2007-08-16 Tadashi Yokoi Cantilever type vertical axis wind turbine
CN102966932A (zh) * 2011-08-29 2013-03-13 杨泰和 具涡轮式防水罩的电动轴流扇及其应用
US20130049594A1 (en) * 2011-08-29 2013-02-28 Tai-Her Yang Electric axial-flow fan having turbine type waterproof enclosure and application thereof
US8829795B2 (en) * 2011-08-29 2014-09-09 Tai-Her Yang Electric axial-flow fan having turbine type waterproof enclosure and application thereof
CN102966932B (zh) * 2011-08-29 2017-04-12 杨泰和 具涡轮式防水罩的电动轴流扇及其应用
JP2014052164A (ja) * 2012-09-10 2014-03-20 Koyo Thermo System Kk 熱処理装置
KR101457785B1 (ko) * 2012-09-10 2014-11-03 고요 써모 시스템 가부시끼 가이샤 열처리 장치
US20160018160A1 (en) * 2014-07-18 2016-01-21 Baxley Equipment Co. Fan for drying of lumber
US9513054B2 (en) * 2014-07-18 2016-12-06 Baxley Equipment Co Fan for drying of lumber
US20210121031A1 (en) * 2019-10-24 2021-04-29 Makita Corporation Dust extractor
US11672396B2 (en) * 2019-10-24 2023-06-13 Makita Corporation Dust extractor

Also Published As

Publication number Publication date
JPS547604B2 (enrdf_load_stackoverflow) 1979-04-09
CA1026291A (en) 1978-02-14
JPS50118911A (enrdf_load_stackoverflow) 1975-09-18

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Legal Events

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AS Assignment

Owner name: SURFACE COMBUSTION, INC., OHIO

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:FL AEROSPACE CORP.;REEL/FRAME:005091/0582

Effective date: 19880608

Owner name: FL AEROSPACE CORP.

Free format text: CHANGE OF NAME;ASSIGNORS:MIDLAND-ROSS CORPORATION MERGING INTO;MRC MERGER CORP., CHANGED NAME TO;MIDLAND - ROSS CORPORATION, CHANGED TO;REEL/FRAME:005240/0352

Effective date: 19880926