US3644054A - Compressor base and intercoolers - Google Patents

Compressor base and intercoolers Download PDF

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Publication number
US3644054A
US3644054A US44034A US3644054DA US3644054A US 3644054 A US3644054 A US 3644054A US 44034 A US44034 A US 44034A US 3644054D A US3644054D A US 3644054DA US 3644054 A US3644054 A US 3644054A
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United States
Prior art keywords
fluid
compressor
stage
intercooler
heat exchangers
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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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US44034A
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English (en)
Inventor
Karol Pilarczyk
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.)
Carrier Corp
Elliott Turbomachinery Co Inc
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Carrier Corp
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Assigned to ELLIOTT TURBOMACHINERY CO., INC. reassignment ELLIOTT TURBOMACHINERY CO., INC. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: CARRIER CORPORATION, A CORP OF DEL.
Assigned to FIRST NATIONAL BANK OF CHICAGO, THE reassignment FIRST NATIONAL BANK OF CHICAGO, THE LICENSE (SEE DOCUMENT FOR DETAILS). Assignors: ELLIOT TURBOMACHINERY CO., INC.
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • F04D29/5826—Cooling at least part of the working fluid in a heat exchanger

Definitions

  • ABSTRACT [73] Assignee: Carrier Corporation, Syracuse, NY.
  • the base further mounts 1/1968 Medgyesy.... 485 11/1969 1 sump the drive structure for the compressor and carries an oi below the drive structure.
  • FIG. 1 is a perspective view of a multistage centrifugal compressor
  • FIG. 2 is a schematic flow diagram showing the relationship of the compressor stages and intercoolers
  • FIG. 3 is a partial cross section side elevation view, with the cross sections being taken in a vertical plane passing through the axes of rotation of the compressor rotor and drive assembly;
  • FIG. 4 is a partial cross section and exploded view of a portion ofthe structure as shown in FIG. 1;
  • FIG. 5 is a cross-sectional view taken on line 5-5 in FIG. 3 showing the air discharge manifold of the intercoolers.
  • the base 1 as shown in FIG. I has mounted rigidly thereon an fluid inlet housing 2 by means of a plurality of bolts (not shown) passing through bolt holes 3, a one-piece cast compressor casing 4 by means of a plurality of bolts 5, a gear housing 6 by means of a plurality of bolts 7, an electric drive motor 8 by means of resilient pads 9, and a control panel 10 by any conventional means.
  • the inlet housing 2 is provided with an annular flange 11 provided with a plurality of peripherally arranged holes 12 for rigidly securing thereto an inlet fluid pipe when assembling the compressor at the use location.
  • An upwardly extending integral mounting arm 13 is provided on the flange 11 for mounting thereto by means of bolts, or the like, a support bracket 14 that carries the diaphragm control mechanism 15 of an inlet valve member 16, with the interposition of a suitable linkage 17.
  • the inlet valve mechanism 15, 16, 17 is conventional per se for throttling the inlet fluid on partial load and for density control in a known manner.
  • the diaphragm control is provided with a pressure feedback tube 18 for this purpose.
  • the multistage impeller rotor and fluid guide structure is contained within the one-piece cast casing 4, which casing is providcd with an axially through cylindrical bore 19, a
  • the drive assembly for the compressor may be of any type.
  • the drive structure may be of the type mentioned in one of applicant's previously identified applications wherein the structure is set forth in detail.
  • Welded steel fabrication is used for constructing the base 1, preferably from stock sheet and plate steel.
  • the front wall 23 is provided with oppositely opening doors 24, which lead to a control and auxiliary component compartment having therein the inlet and outlet water couplings for the intercoolers.
  • the supply 25 and outlet 26 water pipes for the intercoolers extend permanently through the sidewall 27 and are provided at their outer ends with suitable couplings to be connected during installation at the site of use.
  • the basic fluid flow for the compressor is shown in FIG. 2 wherein the impeller of a first stage 28 passes fluid downwardly through a first intercooler 29. Thereafter, the fluid passes through the second stage impeller 30, which directs it downwardly through the second intercooler 31. Finally, the fluid passes upwardly and through the third stage impeller 32 for discharge to the point of use.
  • the impellers 28, 32, 30 form an integral rotor drivingly connected with a spur helical pinion gear 33 that is driven by means ofa drive helical gear 34 mounted on a parallel axis gear drive input shaft 35.
  • the inlet connection is shown in more detail in FIG. 3.
  • a cylindrical mounting portion 36 of the inlet housing 2 is telescopically received over a cylindrical mounting portion 37 with the interposition of an O-ring 38. From the drawing, it is seen that the adjacent cylindrical surfaces of mounting portions 36, 37 are radially spaced from each other so that the O- ring 38 provides the only engaging connection between the inlet housing 2 and the compressor casing 4, while sealing these structures.
  • the inlet housing 2 is independently supported on the base 1 to prevent transmittal of inlet housing vibration, canting, axial movement, radial movement and rotational movement to the compressor casing 4.
  • the complete compressor may be supplied to a user and the user may rigidly couple his inlet fluid pipes directly to the inlet housing 2, without fear that forces relating to the coupling and inlet pipes will be transmitted to the compressor casing. Further, the stresses due to tightening of the connections between the inlet casing and fluid supply pipes will not be transferred to the compressor casing.
  • the removable barrel structure of the compressor includes separate shrouds, diffusers, and annular fluid guide elements all received in a stacked relationship within the cylindrical bore 19 of the one-piece compressor casing 4.
  • the compressor casing 4 is provided with integrally cast passages extending between the barrel assembly and the base 1. Particularly, a first passage 39 extends between the bore 19 and the planar surface 20 to conduct fluid from the discharge of the first stage, second passage 40 extends from the bore 19 to the planar surface 20 to conduct the fluid into the third-stage inlet, third passage 41 extends from the bore 19 to the planar surface 20 to conduct fluid discharged from the second stage and fourth passage 42 extends from the bore 19 to the planar surface 20 to conduct fluid to the inlet of the second stage.
  • the base 1 is provided with a top wall 21, opposed sidewalls 27 and 43, opposed front and back walls 23 and 44, and a bottom wall 45, which together form a substantially closed main chamber containing the intercooler structure.
  • the top wall 21 is provided with a plurality of passages, also shown in FIG. 4, extending between the passages 39-42 and the intercooler main chamber.
  • the top plate 21 is provided with holes 46 that align with passages 39, holes 47 that align with passage 42, hole 48 that aligns with passage 40 and hole 49 that aligns with passage 41.
  • Two parallel partition walls 50 which are parallel to the walls 27, 43, extend completely from the top wall 21 to the bottom wall 45 and extend from the front wall 23 to the backwall 44 to form a central manifold chamber 51.
  • Additional partition walls 52 subdivide the manifold chamber into three aligned subchambers, with the outside subchambers 53 being in fluid communication between the holes 47 in the top wall and correspondingly aligned holes in the left-hand partition wall 50, and with the inside subchamber 54 being in fluid communication between the hole 48 and a hole 55 in the right-hand partition wall 50 as shown in FIG. 3.
  • the main intercooler chamber is further divided into a first intercooler chamber 55 to the left of the partition walls 50 and a second intercooler chamber 56 to the right of the partition walls 50, as seen in H6.
  • identical and interchangeable parallel tube fluid heat exchangers 57 are mounted on shelves 58 within their respective intercooler chambers 55, 56 so that they may be horizontally slid into and out of the base 1 after the releasably secure back wall 44 is removed.
  • the pipes 25, 26 are provided with releasable couplings 59 for uncoupling the heat exchangers, without affecting the location of the pipes 25, 26.
  • the baffles 60 formed in the nozzletype passages 61 constitute separators that will take the cooled fluid from the heat exchangers having condensed droplets therein, accelerate this cooled fluid and substantially reverse the flow of the accelerated cooled fluid to separate the condensate. Further, moisture will be removed from this separated fluid by means of demister 62. Thereafter, the relatively dry fluid will pass through respective holes in the partition walls 50 so that the fluid from the intercooler chamber 55 will pass into the submanifold chambers 53 and fluid from the intercooler 56 will pass into the submanifold chamber 54. It is noted that the left-hand passage 61 is substantially larger than the right-hand passage 61 as shown in FIG.
  • the base 1 is provided with an oil sump 63, which is in direct communication with the interior of the gear housing 6.
  • the compressor base of the present invention separately and rigidly mounts a rigid comprcssor casing and a rigid fluid inlet casing, and provides a telescopic coupling therebetween having only a flexible interengagement by means of the O-ring 38.
  • the users rigid fluid inlet pipes may be rigidly connected directly to the fluid inlet casing 2 for support thereof, without fear that the stresses produced by the rigid supply Coupling will be transmitted to the compressor casing 4.
  • this O-ring seal 38 and flexible coupling will accommodate misalignment and tolerances as between the casings 2 and 4, as well as preventing force transmittal therebetween because of the considerable radial spacing between the telescoping cylindrical portions 36, 37.
  • the inlet casing may be advantageously used for a conventional type of inlet valve, without fear that forces associated with the inlet valve will be transmitted to the compressor casing.
  • the compressor casing is of a one-piece cast construction with integral fluid passages between stages communicating between each stage and intercoolers within the base, respectively, so that no bulky, costly and cumbersome external piping connections are required.
  • the base has a top compressor supporting wall that is provided with integral passages aligned respectively in fluid communication with the compressor casing integral passages so that fluid is conducted from the first and second stages downwardly into the intercooler chambers and upwardly from the intercooler chambers into the second and third stages.
  • the base is further of a compact construction in that it requires very little extra room over that of the plan view dimensions associated with the compressor casing and inlet fluid casing, with respect to its enclosure for housing intercoolers, centrifugal separators, and demisters.
  • the intercoolers are identical and the demisters are identical to provide for interchangeability and inexpensive manufacture.
  • the separators are formed by baffles that are identical although assembled in mirror image fashion. The fluid flows downwardly through the intercoolers through a restricted passage formed by the separator baffles so that the cooled fluid approaches or reaches sonic velocity before it is sharply and reversely guided upwardly through the demisters, so that during this reversal, droplets of condensate will be discharged downwardly where they will be collected and removed if desired.
  • the fluid moving upwardly through demisters is further directed upwardly through submanifold chambers located centrally between the two intercooler chambers for discharge through the top wall of the base.
  • Construction of the base is rigid and relatively inexpensive in that it is of welded steel fabrication employing only planar sheets and plates, with the partition walls forming the submanifold chambers considerably contributing to the rigidity of the entire structure by providing cross bracing.
  • the portion of the base under the drive mechanism, particularly an electric motor and gear train, is of relatively shallow construction due to the greater height of these components and forms a sump for the oil lubrication system.
  • this sump is in direct communication with the gear housing.
  • the intercoolers are mounted within their respective intercooler chambers by means of shelves so that they may be slid horizontally in one direction out of the base, after the removal of the adjacent releasably mounted wall.
  • the wall opposite from the releasably mounted wall is provided with access means so that rigid cooling liquid supply and exhaust pipes may be quickly coupled and uncoupled from the intercoolers.
  • the demisters are mounted on respective shelves to be horizontally slid out of their respective intercooler chambers in the same direction'as the heat exchangers, for purposes of repair, replacement or the like.
  • a multistage compressor comprising: a base; a compressor rotor having at least two impellers; casing means rigidly secured on said base and rotatably supporting said compressor rotor for providing at least two compression stages, said casing means having an integral fluid outlet for the first stage and an integral fluid inlet for the second stage; said base including an upper wall, sidewalls, and a lower wall forming therebetween a substantially closed intercooler chamber, and said upper wall having an integral chamber inlet in fluid communication directly with said first stage fluid outlet, and an integral chamber outlet in direct fluid communication with said second-stage fluid inlet.
  • said casing means includes a one-piece cast casing having an axially through cylinder bore receiving concentrically therein said compressor rotor and a downwardly facing horizontally planar surface; said casing means inlets and outlets extending between said bore and said planar surface, with their respective ends opening upwardly and downwardly; said base upper wall having an upwardly facing substantially horizontally planar surface engaging the entire casing planar surface.
  • the compressor of claim L including liquid gas heat exchanger means mounted in said intercooler chamber in fluid communication between said chamber fluid inlet and said chamber fluid outlet; and chamber partition means forming a constricted passage for the fluid downstream of said heat exchanger means for passing the fluid downwardly and sharply reversing the fluid upwardly to discharge condensed liquid therefrom.
  • the compressor of claim 5 including partition wall means in said base forming three aligned manifold subchambers, with the two outside manifold subchambers being in fluid communication with said second-stage fluid inlet and the middle manifold subchamber being in fluid communication with said third stage inlet.
  • the compressor of claim 5 including generally vertical partition wall means in said base forming at least two manifolds extending vertically for substantially the entire height of said intercooler chamber and being respectively in direct fluid communication through said upper wall with said second-stage fluid inlet and said third-stage fluid inlet.
  • said heat exchangers are identical; said base having shelf means mounting each of said heat exchangers for relative horizontal sliding in the same direction for removal and assembly; said base having one sidewall being perpendicular to said direction and being removable to provide access for assembly and withdrawal of said heat exchangers; rigid inlet and outlet liquid conduits on the other side of said heat exchangers opposite from said one sidewall having releasable coupling means fluid connecting them respectively to said heat exchangers; and said base having removable wall means on said other side for providing access to said releasable couplings.
  • demister means operatively mounted in each of said intercooler subchambers respectively downstream from said heat exchangers; and fluid guide means for respectively directing fluid from said heat exchangers downwardly and then reversely upwardly through said demister means.
  • each of said heat exchangers is mounted above the corresponding interconnecting passage means and each of said demister means is mounted below the corresponding interconnecting passage means.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US44034A 1970-06-08 1970-06-08 Compressor base and intercoolers Expired - Lifetime US3644054A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US4403470A 1970-06-08 1970-06-08

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US3644054A true US3644054A (en) 1972-02-22

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US (1) US3644054A (fr)
CA (1) CA936504A (fr)
CH (1) CH520875A (fr)
DE (1) DE2128232B2 (fr)
FR (1) FR2096062A5 (fr)
GB (1) GB1357184A (fr)
NL (1) NL7107687A (fr)
SE (1) SE371474B (fr)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3912000A (en) * 1972-04-19 1975-10-14 Worthington Cei Multi-cooling housing for a multi-stage compressing system
US4288204A (en) * 1978-03-02 1981-09-08 Klein, Schanzlin & Becker Ag Support for multi-stage compressors
US4830580A (en) * 1985-03-04 1989-05-16 Nippon Air Brake Co., Ltd. Two-stage air compressor unit
US5362207A (en) * 1993-06-09 1994-11-08 Ingersoll-Rand Company Portable diesel-driven centrifugal air compressor
US5613843A (en) * 1992-09-11 1997-03-25 Hitachi, Ltd. Package-type screw compressor
US6018962A (en) * 1998-12-16 2000-02-01 American Standard Inc. Centrifugal compressor oil sump demister apparatus
US6572350B2 (en) * 2000-06-30 2003-06-03 Hitachi, Ltd. Screw compressor
US6692235B2 (en) * 2001-07-30 2004-02-17 Cooper Cameron Corporation Air cooled packaged multi-stage centrifugal compressor system
US20040031286A1 (en) * 2002-08-06 2004-02-19 York International Corporation Suction connection for dual centrifugal compressor refrigeration systems
US20130251555A1 (en) * 2012-03-26 2013-09-26 Pedro Ismael DePAZ Power system arrangement
US20140086733A1 (en) * 2012-09-24 2014-03-27 Samsung Techwin Co., Ltd. Compressing system
US20150330409A1 (en) * 2014-05-14 2015-11-19 Ingersoll-Rand Company Air compressor system
US20150337861A1 (en) * 2014-05-23 2015-11-26 Howden Roots Llc Apparatus to support components of a fluid handling system and implementation thereof
US9677551B2 (en) 2015-08-21 2017-06-13 Ingersoll-Rand Company Compressor and oil drain system
DE102016113067A1 (de) * 2016-07-15 2018-01-18 Man Diesel & Turbo Se Getriebeturbomaschine
US10087797B2 (en) 2015-08-21 2018-10-02 Ingersoll-Rand Company Compressor and oil drain system
US20210048034A1 (en) * 2016-09-27 2021-02-18 Atlas Copco Comptec Llc Integrated oil system manifold
US11067081B2 (en) * 2015-12-22 2021-07-20 Kobe Steel, Ltd. Screw compressor

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6564839B1 (en) 2000-11-01 2003-05-20 The Goodyear Tire & Rubber Company Pneumatic tire having a load dependent adaptive footprint shape

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB563532A (en) * 1941-12-20 1944-08-18 Sulzer Ag Improvements in or relating to centrifugal pumps
US3001692A (en) * 1949-07-26 1961-09-26 Schierl Otto Multistage compressors
US3203352A (en) * 1962-05-24 1965-08-31 Schafranek Gustav Multiple pump assembly
US3355096A (en) * 1966-02-15 1967-11-28 Ingersoll Rand Co Multi-stage intercooled compressor
US3361073A (en) * 1964-10-30 1968-01-02 Sulzer Ag Casing for multi-stage centrifugal pump
US3476485A (en) * 1967-09-18 1969-11-04 Dresser Ind Multistage centrifugal compressor

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB563532A (en) * 1941-12-20 1944-08-18 Sulzer Ag Improvements in or relating to centrifugal pumps
US3001692A (en) * 1949-07-26 1961-09-26 Schierl Otto Multistage compressors
US3203352A (en) * 1962-05-24 1965-08-31 Schafranek Gustav Multiple pump assembly
US3361073A (en) * 1964-10-30 1968-01-02 Sulzer Ag Casing for multi-stage centrifugal pump
US3355096A (en) * 1966-02-15 1967-11-28 Ingersoll Rand Co Multi-stage intercooled compressor
US3476485A (en) * 1967-09-18 1969-11-04 Dresser Ind Multistage centrifugal compressor

Cited By (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3912000A (en) * 1972-04-19 1975-10-14 Worthington Cei Multi-cooling housing for a multi-stage compressing system
US4288204A (en) * 1978-03-02 1981-09-08 Klein, Schanzlin & Becker Ag Support for multi-stage compressors
US4830580A (en) * 1985-03-04 1989-05-16 Nippon Air Brake Co., Ltd. Two-stage air compressor unit
US5613843A (en) * 1992-09-11 1997-03-25 Hitachi, Ltd. Package-type screw compressor
US5362207A (en) * 1993-06-09 1994-11-08 Ingersoll-Rand Company Portable diesel-driven centrifugal air compressor
US6018962A (en) * 1998-12-16 2000-02-01 American Standard Inc. Centrifugal compressor oil sump demister apparatus
US6572350B2 (en) * 2000-06-30 2003-06-03 Hitachi, Ltd. Screw compressor
US6679689B2 (en) * 2000-06-30 2004-01-20 Hitachi, Ltd. Screw compressor
US20080273991A1 (en) * 2001-07-30 2008-11-06 Cameron International Corporation Air cooled packaged multi-stage centrifugal compressor method
US20040184927A1 (en) * 2001-07-30 2004-09-23 Kolodziej Robert M. Air cooled packaged multi-stage centrifugal compressor system
US6692235B2 (en) * 2001-07-30 2004-02-17 Cooper Cameron Corporation Air cooled packaged multi-stage centrifugal compressor system
US7819634B2 (en) 2001-07-30 2010-10-26 Cameron International Corporation Air cooled packaged multi-stage centrifugal compressor method
US7832992B2 (en) 2001-07-30 2010-11-16 Cameron International Corporation Air cooled packaged multi-stage centrifugal compressor system
US6910349B2 (en) 2002-08-06 2005-06-28 York International Corporation Suction connection for dual centrifugal compressor refrigeration systems
US20040031286A1 (en) * 2002-08-06 2004-02-19 York International Corporation Suction connection for dual centrifugal compressor refrigeration systems
US20130251555A1 (en) * 2012-03-26 2013-09-26 Pedro Ismael DePAZ Power system arrangement
CN103671179B (zh) * 2012-09-24 2017-11-03 韩华泰科株式会社 压缩系统
US20140086733A1 (en) * 2012-09-24 2014-03-27 Samsung Techwin Co., Ltd. Compressing system
US20150330409A1 (en) * 2014-05-14 2015-11-19 Ingersoll-Rand Company Air compressor system
US10047766B2 (en) * 2014-05-14 2018-08-14 Ingersoll-Rand Company Air compressor system
US20150337861A1 (en) * 2014-05-23 2015-11-26 Howden Roots Llc Apparatus to support components of a fluid handling system and implementation thereof
US9677551B2 (en) 2015-08-21 2017-06-13 Ingersoll-Rand Company Compressor and oil drain system
US10087797B2 (en) 2015-08-21 2018-10-02 Ingersoll-Rand Company Compressor and oil drain system
US11067081B2 (en) * 2015-12-22 2021-07-20 Kobe Steel, Ltd. Screw compressor
DE102016113067A1 (de) * 2016-07-15 2018-01-18 Man Diesel & Turbo Se Getriebeturbomaschine
US20210048034A1 (en) * 2016-09-27 2021-02-18 Atlas Copco Comptec Llc Integrated oil system manifold

Also Published As

Publication number Publication date
CA936504A (en) 1973-11-06
NL7107687A (fr) 1971-12-10
CH520875A (de) 1972-03-31
FR2096062A5 (fr) 1972-02-11
DE2128232B2 (de) 1975-07-31
SE371474B (fr) 1974-11-18
DE2128232A1 (de) 1971-12-16
GB1357184A (en) 1974-06-19

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Legal Events

Date Code Title Description
AS Assignment

Owner name: ELLIOTT TURBOMACHINERY CO., INC., A CORP OF DELAWA

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST. SUBJECT TO LICENSE RECITED.;ASSIGNOR:CARRIER CORPORATION, A CORP OF DEL.;REEL/FRAME:004499/0922

Effective date: 19851220

AS Assignment

Owner name: FIRST NATIONAL BANK OF CHICAGO, THE,ILLINOIS

Free format text: LICENSE;ASSIGNOR:ELLIOT TURBOMACHINERY CO., INC.;REEL/FRAME:004940/0562

Effective date: 19871109

Owner name: FIRST NATIONAL BANK OF CHICAGO, THE, ONE FIRST NAT

Free format text: LICENSE;ASSIGNOR:ELLIOT TURBOMACHINERY CO., INC.;REEL/FRAME:004940/0562

Effective date: 19871109