US3919858A - Direct liquid refrigerant supply and return system - Google Patents
Direct liquid refrigerant supply and return system Download PDFInfo
- Publication number
- US3919858A US3919858A US467318A US46731874A US3919858A US 3919858 A US3919858 A US 3919858A US 467318 A US467318 A US 467318A US 46731874 A US46731874 A US 46731874A US 3919858 A US3919858 A US 3919858A
- Authority
- US
- United States
- Prior art keywords
- refrigerant
- header
- return
- heat exchange
- receptacle
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/0263—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by varying the geometry or cross-section of header box
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25C—PRODUCING, WORKING OR HANDLING ICE
- F25C3/00—Processes or apparatus specially adapted for producing ice or snow for winter sports or similar recreational purposes, e.g. for sporting installations; Producing artificial snow
- F25C3/02—Processes or apparatus specially adapted for producing ice or snow for winter sports or similar recreational purposes, e.g. for sporting installations; Producing artificial snow for ice rinks
Definitions
- ABSTRACT A refrigerant system in which liquid halocarbon compound refrigerant is delivered at pressures in excess of evaporation pressure through metering outlets in a supply header of an evaporator in a manner to provide uniform cooling throughout the evaporator and utilizing a return header and 1iquid-vapor lift apparatus to return vaporized and unevaporated refrigerant to an accumulator-separator of the refrigeration system.
- This invention relates generally to direct liquid refrigerant systems of various kinds which may be used as the cooling means for ice rinks and the like and relates specifically to a direct refrigerant supply and return system which provides a substantially uniform refrigerant flow through an evaporator having multiple, single pass, parallel heat exchange pipes and which includes a vaporliquid lift apparatus to enable unevaporated refrigerant to be entrained in the vaporized refrigerant and returned to an accumulator-separator of a refrigeration system.
- Direct liquid refrigerant systems have presented problems due to the difficulty of maintaining substantially constant flow at predetermined pressures throughout the heat exchange area of the system.
- An example of structures in the prior art is US. Pat. No. 3,466,892 to Holmsten which discloses a multiple parallel pipe heat exchange system.
- This patent discloses a centrally fed supply header which supplies refrigerant fluid to a series of parallel pipes that are connected at one end to the supply header and connected at the opposite end to a return header having a central discharge pipe.
- This structure at ordinary rates of flow does not provide uniform refrigerant flow through the parallel pipes and thus cooling effect fluctuates as the pressure variance causes a change in the temperature gradient of the system.
- the present invention includes a supply and return system for use with a halocarbon compound or other refrigerant to provide a direct heat exchange structure for an ice rink or the like.
- the system has a supply header which is flooded throughout its length and which supplies liquid refrigerant to multiple, parallel, single pass heat exchange pipes through self-cleaning metering valves.
- the supply header feeds the heat exchange pipes in a diametric relationship to the order in which the heat exchange pipe delivers vapor and unevaporated liquid refrigerant to a return header, thereby providing uniform cooling through the heat exchange area.
- the system includes a stepped variable capacity return header which maintains substantially constant pressure within the heat exchange pipes and cooperates with a liquid-vapor lift apparatus in such a manner as to allow unevaporated refrigerant to be entrained in the vaporized refrigerant stream and thus return the unevaporated refrigerant to an accumulator-separator of a refrigeration system in an uninterrupted flow with the vaporized refrigerant.
- Another object of the invention is to provide a system which maintains an even distribution of refrigerant at nearly uniform pressures throughout the multiple pipes of the evaporator.
- FIG. 1 is a top plan view of the direct liquid supply and return system and schematically illustrating its relationship to an accumulator-separator of a refrigeration system.
- FIG. 2 is an enlarged side elevation of the return header of the system.
- FIG. 3 is an enlarged end view thereof.
- FIG. 4 is an enlarged fragmentary section taken along the line 4-4 of FIG. 1.
- FIG. 5 is an enlarged vertical section of the vaporliquid lift assembly.
- a refrigerant supply and return system 10 having an evaporator E for use with a conventional refrigeration system 11 of an ice rink or the like 12.
- the conventional refrigeration system 11 includes a separating and delivery apparatus or accumulator-separator 13 having a liquid control L and in which vaporized refrigerant is separated from unevaporated liquid refrigerant returning from the supply and return system 10.
- the separated refrigerant vapor in the accumulator-separator 13 is discharged through a suction line 14 to one or more compressors 15 which compress the vapor and discharge the same through lines 16, oil separator 17, and line 18 to a condenser 19.
- the compressors 15 could be provided with speed change controls; however, two compressors normally are provided with each compressor having a 50% capacity reduction.
- a system such as that illustrated in FIG. 1, usually operates at 50%, 75% or 100% of its capacity depending upon operating conditions.
- the liquid level control L regulates the amount of liquid refrigerant which is discharged from the receiver 20 into the accumulator-separator 13 so that a substantially constant liquid level is maintained therein.
- refrigerant 22 (Chlorodifluoromethane) is used as the direct heat exchange media.
- liquid refrigerant is delivered under pressure by a pump Pfrom the accumulator-separator 13 to a supply pipe 26 having check valve C.
- the supply pipe 26 carries the liquid refrigerant to the receiving end or inlet 27 of supply header 28.
- the refrigerant feed to the supply header is substantially constant and at a rate equal to at least full capacity of the evaporator and usually at a greater capacity.
- the supply header 28 is provided with a plurality of generally upright discharge pipes 29 within each of which is mounted a metering valve 30.
- Each metering valve 30 includes a body 31 having a vertically disposed tapered bore 32 and a concentric tapered counterbore 33.
- the tapered bore 32 is threaded for at least a portion of its length and threadedly receives a metering plug 34 having an axial orifice 35 extending entirely therethrough providing communication between the discharge pipe 29 and the counterbore 33.
- a closure plug 36 is threadedly received within the counterbore 33 to prevent the passage of refrigerant to the exterior of the body 31.
- the orifice 35 is of a size to permit a predetermined quantity of liquid refrigerant to pass therethrough at a desired pressure.
- a wire insert 37 having outwardly bent ends 38 is inserted within the orifice 35 with such wire insert being slightly longer than the length of the metering plug 34. Liquid refrigerant passing through the orifice causes the wire insert 37 to jiggle or move in a haphazard manner to keep the orifice clean of all materials.
- the wire insert is of a specific diameter relative to the diameter of the orifice to permit a predetermined quantity of refrigerant to pass through the orifice.
- the flow of refrigerant can be either increased or further restricted. It is apparent that the metering plug 34 can be easily removed from the body 31 to repair or replace the wire insert 37 or to replace the metering plug 34 with another plug having a different size orifice or wire insert.
- the body 31 is provided with an enlargement or boss 39 at one side and such boss has a bore 40 providing communication between the counterbore 33 and the exterior of the body.
- a heat exchange pipe 41 of the evaporator E is connected to each of the metering valves 30 in communication with the outlet bore 40 and such pipes are situated in a generally parallel relationship and disposed generally perpendicular to the supply header 28.
- the heat exchange pipes 41 are equally spaced along the length of the supply header at intervals determined by the effective heat exchange areas required with a spacing of approximately four inches having been found satisfactory for an ice rink. Vapor and unevaporated refrigerant are discharged from the heat exchange pipes into a return or discharge header 42 disposed generally perpendicular to such pipes and generally parallel to the supply header 28.
- the return header is of stepped eccentric construction having sections 43, 44 and 45 of progressively larger diameters respectively. These sections are situated along a common upper grade line 46 which runs across the top of each of the sections 43, 44 and 45 and therefore has a stepped increasing lower grade line 47 defined by the bottom of each pipe.
- This configuration allows for the necessary increase in capacity without pressure increase as the flow is increased as each successive heat .exchange pipe discharges into the return header.
- the stepped lower grade line 47 permits the refrigerant to flow by gravity from sections 43-45 while allowing the heat exchange pipes to enter the return header 42 at a common elevation.
- the lower grade line 47 could have a constant slope from end to end.
- the evaporated and unevaporated refrigerant which is received by the return header 42 is discharged through a line 48 into a vapor-liquid lift assembly 49.
- the discharge line 48 is located diametrically opposite the inlet end 27 of the supply header 28 so that all of the refrigerant flow paths are substantially equal in resistance and the pressures within the heat exchange pipes 41 are substantially constant.
- the lift assembly 49 FIG. 5, includes a vertically positioned elongated generally cylindrical side wall 50 with a bottom wall 51 at one end and a top wall 52 at the other end forming a receptacle for vaporized and unevaporated refrigerant.
- the return line 48 enters the side wall at a point below the top wall 52.
- a pair of vertically disposed discharge pipes 53 and 54 extend through the top wall 52 and are welded or otherwise connected thereto.
- the vertical discharge pipes 53 and 54 are positioned so that their intakes 55 and 56 respectively are below the discharge line 48.
- the intake 56 of the vertical discharge pipe is positioned below the intake 55 of the discharge pipe 53 with the spacing between such intakes depending upon the quantity of evaporated and unevaporated refrigerant being introduced to the lift assembly 49 from the return header 42.
- the vertical discharge pipe 53 normally is smaller in diameter than the pipe 54 and is ofa diameter such that when the compressors are operating at minimum capacity, the suction through line 53 withdraws a mixture of vapor having liquid entrained therein at a velocity of not less than 1,000 feet per minute. Such velocity is necessary to insure that the liquid remains entrained in the evaporated refrigerant and does not collect along the inner wall of the vertical discharge pipe and run back into the lift assembly.
- the purpose of the lift assembly 49 is to raise excess liquid which is not evaporated, with a minimum of pressure penalty, from the rink floor level into the accumulator-separator which usually is much higher because of the structure of the building. Therefore, it is necessary to provide a velocity of flow in one or more of the vertical pipes 53 and 54 under any of the several capacity steps of the compressors such that the velocity in any vertical pipe is not less than 1,000 feet per minute thus providing a vertical movement of unevaporated liquid as an entrainment in the vapor stream.
- the weight of the unevaporated liquid is equal to approximately 50% of the weight of the vapor, but the volume of the liquid is very small when compared to the vapor volume.
- the unevaporated liquid refrigerant returned to the accumulator-separator is inversely proportional to the load on the evaporator but is readily moved with the vapor, providing vapor velocity is never less than 1,000 feet per minute.
- liquid refrigerant is pumped at a constant volume from the accumulatorseparator to the supply header 28 under all load conditions. From the supply header the liquid refrigerant is fed to the plurality of heat exchange pipes 41 through the metering valves 30.
- the orifice 35 of each metering valve and the wire insert therethrough permit a specific quantity of liquid to be fed to each heat exchange pipe at a desired pressure.
- the wire insert 37 being free to move with the orifice, also functions to prevent the buildup of any material which would tend to restrict the flow through the valves.
- the progressively larger diameters of the stepped eccentric return header allows for the necessary increase in capacity without pressure increase as the flow increases due to the discharge from successive heat exchange pipes.
- the unevaporated and evaporated reflgerant is discharged from the return header into the vapor-liquid lift apparatus 49.
- the discharge from the return header is located diametrically opposite the inlet to the supply header so that refrigerant flow paths through the headers and each heat exchange pipe are substantially equal, thereby aiding in maintaining a more uniform heat exchange rate in the evaporator.
- the refrigerant discharged into the vapor-liquid lift apparatus is returned through discharge lines 54 and/or 53, in which suction is created by the compressors 15, to the accumulator-separator as a mixture of unevaporated refrigerant entrained in evaportated refrigerant.
- the vertical line 54 is uncovered and vapor and unevaporated refrigerant flows vertically through both lines 53 and 54 but the sizes have been proportioned so that the velocity in each line is not less than 1,000 feet per minute. At full capacity the liquid level is further lowered because of the increased flow in both of the vertical pipes.
- a direct liquid refrigerant supply and return apparatus including an evaporator for use with a refrigeration system having an accumulator-separator, said apparatus comprising a supply header having an inlet at one end for receiving pressurized liquid refrigerant from the accumulator-separator, a plurality of heat exchange pipes located substantially parallel with each other and generally perpendicular to the supply header, each of said heat exchange pipes being connected at one end to said supply header, a return header in spaced generally parallel relationship to said supply header, the opposite end of each of said heat exchange pipes communicating with said return header, said return header having discharge means at one end for discharging vaporized and unevaporated refrigerant therefrom, said discharge means being diametrically opposite said inlet to said supply header so that the refrigerant flow paths from the inlet of said supply header through said heat exchange pipes and said return header are substantially of equal resistance, a vaporliquid lift apparatus including a receptacle for receiving vaporized and unevaporated refrigerant from the discharge means of said return header
- each of said metering means having a body with a bore and a counterbore concentric with said bore, plug means having a metering orifice removably mounted in said bore, said body having inlet means providing communication between said supply header and said orifice and oulet means providing communication between said counterbore and said heat exchange pipes, and closure means removably mounted in said counterbore, whereby said plug means may be selectively removed from said body when said closure means is removed from said counterbore.
- said return header includes a plurality of sections of progressively increasing diameters eccentrically connected together along a common substantially horizontal upper grade line and a stepped lower grade line, said discharge means being adjacent the larger end of said return header.
- said receptacle includes a vertically disposed generally cylindrical side wall having a top wall and a bottom wall fixed thereto.
- the structure of claim 1 including a plurality of discharge pipes having ends terminating at different elevations within said receptacle to provide for varying capacities of flow to the accumulator-separator.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
Claims (8)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US467318A US3919858A (en) | 1973-04-19 | 1974-05-06 | Direct liquid refrigerant supply and return system |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US35281473A | 1973-04-19 | 1973-04-19 | |
US467318A US3919858A (en) | 1973-04-19 | 1974-05-06 | Direct liquid refrigerant supply and return system |
Publications (1)
Publication Number | Publication Date |
---|---|
US3919858A true US3919858A (en) | 1975-11-18 |
Family
ID=26997664
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US467318A Expired - Lifetime US3919858A (en) | 1973-04-19 | 1974-05-06 | Direct liquid refrigerant supply and return system |
Country Status (1)
Country | Link |
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US (1) | US3919858A (en) |
Cited By (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4216764A (en) * | 1978-09-14 | 1980-08-12 | Sunworks, Inc. | Solar energy collector system including apparatus for balancing heat-exchange fluid flow |
US4287945A (en) * | 1979-07-03 | 1981-09-08 | The A.P.V. Company Limited | Plate heat exchanger |
US4370868A (en) * | 1981-01-05 | 1983-02-01 | Borg-Warner Corporation | Distributor for plate fin evaporator |
US5765393A (en) * | 1997-05-28 | 1998-06-16 | White Consolidated Industries, Inc. | Capillary tube incorporated into last pass of condenser |
WO1999058910A1 (en) * | 1998-05-11 | 1999-11-18 | Scholl Klaus Dieter | Method and device for preserving snow |
US20050066683A1 (en) * | 2003-09-25 | 2005-03-31 | Delaware Capital Formation, Inc. | Refrigerated worksurface |
WO2006083484A1 (en) * | 2005-02-02 | 2006-08-10 | Carrier Corporation | Parallel flow heat exchanger for heat pump applications |
US20100263397A1 (en) * | 2009-04-16 | 2010-10-21 | Fujikoki Corporation | Motor-operated valve and refrigeration cycle using the same |
ITLE20100006A1 (en) * | 2010-05-07 | 2011-11-08 | Uni Del Salento Dipartime Nto Di Ingegne | PLAN SOLAR PANEL WITH RAKED MANIFOLDS FOR APPLICATIONS WITH TRADITIONAL THERMOVIC FLUID AND INSEMINATED WITH PARTICLES AND WITH NANOFLUIDI |
US20130036758A1 (en) * | 2010-11-15 | 2013-02-14 | Guangjing Li | Refrigeration equipment with sleeve-type collection pipe for artificial skating rink |
JP2014020737A (en) * | 2012-07-23 | 2014-02-03 | Toyo Eng Works Ltd | Refrigerant circulation cooling system |
US20180010857A1 (en) * | 2015-03-31 | 2018-01-11 | Gd Midea Heating & Ventilating Equipment Co., Ltd. | Heat exchanger and multi-split system having same |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1883958A (en) * | 1929-04-25 | 1932-10-25 | Koeniger Walther | Ice skating pink |
US2032286A (en) * | 1935-04-30 | 1936-02-25 | Frick Co | Refrigerant liquid return system |
US2158792A (en) * | 1934-12-07 | 1939-05-16 | Gen Refrigeration Corp | Header feed evaporator |
US2265282A (en) * | 1937-02-13 | 1941-12-09 | Masch Und Metallwaren Handels | Regulating device |
US2270745A (en) * | 1940-07-24 | 1942-01-20 | Todd Newton Taylor | Skating rink |
US2354497A (en) * | 1943-06-12 | 1944-07-25 | Robert T Brizzolara | Refrigeration apparatus |
-
1974
- 1974-05-06 US US467318A patent/US3919858A/en not_active Expired - Lifetime
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1883958A (en) * | 1929-04-25 | 1932-10-25 | Koeniger Walther | Ice skating pink |
US2158792A (en) * | 1934-12-07 | 1939-05-16 | Gen Refrigeration Corp | Header feed evaporator |
US2032286A (en) * | 1935-04-30 | 1936-02-25 | Frick Co | Refrigerant liquid return system |
US2265282A (en) * | 1937-02-13 | 1941-12-09 | Masch Und Metallwaren Handels | Regulating device |
US2270745A (en) * | 1940-07-24 | 1942-01-20 | Todd Newton Taylor | Skating rink |
US2354497A (en) * | 1943-06-12 | 1944-07-25 | Robert T Brizzolara | Refrigeration apparatus |
Cited By (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4216764A (en) * | 1978-09-14 | 1980-08-12 | Sunworks, Inc. | Solar energy collector system including apparatus for balancing heat-exchange fluid flow |
US4287945A (en) * | 1979-07-03 | 1981-09-08 | The A.P.V. Company Limited | Plate heat exchanger |
US4370868A (en) * | 1981-01-05 | 1983-02-01 | Borg-Warner Corporation | Distributor for plate fin evaporator |
US5765393A (en) * | 1997-05-28 | 1998-06-16 | White Consolidated Industries, Inc. | Capillary tube incorporated into last pass of condenser |
WO1999058910A1 (en) * | 1998-05-11 | 1999-11-18 | Scholl Klaus Dieter | Method and device for preserving snow |
US6418733B1 (en) | 1998-05-11 | 2002-07-16 | Ralf Morent | Method and device for preserving snow |
US7216500B2 (en) * | 2003-09-25 | 2007-05-15 | Dover Systems, Inc. | Refrigerated worksurface |
US20050066683A1 (en) * | 2003-09-25 | 2005-03-31 | Delaware Capital Formation, Inc. | Refrigerated worksurface |
WO2006083484A1 (en) * | 2005-02-02 | 2006-08-10 | Carrier Corporation | Parallel flow heat exchanger for heat pump applications |
US20100263397A1 (en) * | 2009-04-16 | 2010-10-21 | Fujikoki Corporation | Motor-operated valve and refrigeration cycle using the same |
US8763419B2 (en) * | 2009-04-16 | 2014-07-01 | Fujikoki Corporation | Motor-operated valve and refrigeration cycle using the same |
ITLE20100006A1 (en) * | 2010-05-07 | 2011-11-08 | Uni Del Salento Dipartime Nto Di Ingegne | PLAN SOLAR PANEL WITH RAKED MANIFOLDS FOR APPLICATIONS WITH TRADITIONAL THERMOVIC FLUID AND INSEMINATED WITH PARTICLES AND WITH NANOFLUIDI |
WO2011138752A1 (en) * | 2010-05-07 | 2011-11-10 | Università Del Salento - Dipartimento Di Ingegneria Dell'innovazione | Thermal solar collector with tapered tubes |
US20130036758A1 (en) * | 2010-11-15 | 2013-02-14 | Guangjing Li | Refrigeration equipment with sleeve-type collection pipe for artificial skating rink |
US8919141B2 (en) * | 2010-11-15 | 2014-12-30 | Guangjing Li | Refrigeration equipment with sleeve-type collection pipe for artificial skating rink |
JP2014020737A (en) * | 2012-07-23 | 2014-02-03 | Toyo Eng Works Ltd | Refrigerant circulation cooling system |
US20180010857A1 (en) * | 2015-03-31 | 2018-01-11 | Gd Midea Heating & Ventilating Equipment Co., Ltd. | Heat exchanger and multi-split system having same |
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Legal Events
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AS | Assignment |
Owner name: CANADIAN IMPERIAL BANK OF COMMERCE Free format text: SECURITY INTEREST;ASSIGNOR:YORK INTERNATIONAL CORPORATION;REEL/FRAME:005156/0705 Effective date: 19881215 |
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STCF | Information on status: patent grant |
Free format text: PATENTED FILE - (OLD CASE ADDED FOR FILE TRACKING PURPOSES) |
|
AS | Assignment |
Owner name: CANADIAN IMPERIAL BANK OF COMMERCE Free format text: SECURITY INTEREST;ASSIGNOR:YORK OPERATING COMPANY, F/K/A YORK INTERNATIONAL CORPORATION A DE CORP.;REEL/FRAME:005994/0916 Effective date: 19911009 |
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Owner name: CANADIAN IMPERIAL BANK OF COMMERCE Free format text: SECURITY INTEREST;ASSIGNOR:YORK INTERNATIONAL CORPORATION (F/K/A YORK OPERATING COMPANY);REEL/FRAME:006007/0123 Effective date: 19911231 |
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Owner name: CANADIAN IMPERIAL BANK OF COMMERCE Free format text: RELEASED BY SECURED PARTY;ASSIGNOR:YORK INTERNATIONAL CORPORATION, A DE CORP.;REEL/FRAME:006194/0182 Effective date: 19920630 |