US20070081910A1 - Compressor valve plate with spiral groove - Google Patents
Compressor valve plate with spiral groove Download PDFInfo
- Publication number
- US20070081910A1 US20070081910A1 US11/246,841 US24684105A US2007081910A1 US 20070081910 A1 US20070081910 A1 US 20070081910A1 US 24684105 A US24684105 A US 24684105A US 2007081910 A1 US2007081910 A1 US 2007081910A1
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- United States
- Prior art keywords
- valve
- cylinder
- suction
- discharge
- chamber
- 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.)
- Abandoned
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/10—Adaptations or arrangements of distribution members
- F04B39/1066—Valve plates
Definitions
- the subject invention generally pertains to reciprocating compressors and more specifically to valves and valve plates of such compressors.
- compressors To prevent backflow through a suction or discharge opening of a valve plate, compressors often use ring-type valves (similar in shape to washers) that can seal against the valve plate to cover the opening.
- the valves function as suction and discharge check valves that enable a reciprocating piston to compress the gas within a cylinder. The valves also determine which direction the gas flows through the compressor.
- valve seat The sealing surface of the valve plate against which the valve seals is known as a valve seat.
- the surface finish of both the valve and the valve seat are ground as smooth as possible to ensure a positive seal between the two.
- a smooth finish may provide a tight seal, such a surface finish can create several problems.
- adhesion of a fluid such as refrigerant or oil trapped between the valve and the valve seat can cause the valve to stick and delay its opening, which can reduce the operating efficiency of the compressor.
- the resulting delayed opening can make a compressor noisy.
- a smoothly ground surface can be costly to produce.
- Some compressors have something other than a smooth finish between the valve and the valve seat.
- the compressor disclosed in U.S. Pat. No. 1,718,350 for instance, has a series of concentric ridges on either the valve or its seat, thereby providing the valve with multiple seats for better sealing. Since the ridges are concentric, however, fluid can still be trapped within the concentric grooves that lie between the ridges. So even though such a design may provide better sealing, the design does not address the problem of liquid adhesion occurring between the valve and the valve seat.
- U.S. Pat. No. 5,078,582 discloses a compressor whose valve seats have a roughened surface to quiet the operation of the valve. It is not clear, however, how the surface is roughened. If the surface is created by a distribution of pits, the pits may provide pockets that trap fluid in a manner similar to that of the grooves disclosed in the '350 patent just described. If the surface, however, is roughened by a series of protrusions, fluid passageways winding around the protrusions may provide relatively short leakage paths across the valve. Although a compressor designed according to the '582 patent may be quieter, such a compressor is not necessarily more efficient.
- Another object of some embodiments is to provide a valve plate with a spiral groove so that when the valve is closed, the groove provides a minute fluid communication passageway between a cylinder and another chamber of the compressor.
- Another object of some embodiments is to create a valve seat with a spiral groove that provides the valve seat with a surface finish of between 10 and 250 microinches.
- Another object of some embodiments is to create a valve plate with an annular valve opening that is generally centered relative to a machined spiral groove in the valve seat.
- Another object of some embodiments is to incorporate both a suction valve seat and a discharge valve seat in a common valve plate, wherein both seats include a spiral groove.
- a compressor that includes a valve plate, wherein the valve plate has at least one valve seat with a spiral groove.
- FIG. 1 is a cross-sectional view of a compressor shown connected to a schematically illustrated refrigerant system.
- FIG. 2 is an enlarged view of the encircled portion of FIG. 1 .
- FIG. 3 is an enlarged view of the encircled portion of FIG. 2 .
- FIG. 4 is a view taken along line 4 - 4 of FIG. 3 but with the suction valve and piston omitted.
- FIG. 5 is a view taken along line 5 - 5 of FIG. 3 .
- a refrigerant system 10 shown in FIG. 1 , includes a compressor 12 for compressing refrigerant gas and for forcing the refrigerant sequentially through a discharge outlet 14 of compressor 12 , through a condenser 16 that releases heat for condensing the refrigerant, through an expansion device 18 (e.g., expansion valve, capillary tube, orifice, etc.) for cooling the refrigerant by expansion, and through an evaporator 20 for absorbing heat from an outside source or heat load. From evaporator 20 , the refrigerant returns to compressor 12 via a suction inlet 22 to repeat the cycle.
- an expansion device 18 e.g., expansion valve, capillary tube, orifice, etc.
- compressor 12 comprises a compressor housing assembly 24 , which in this example includes a number of components including, but not necessarily limited to, a cylinder block 26 , a cylinder head 28 , a hermetically sealed shell 30 , a discharge muffler 32 , and other components of the compressor.
- a compressor housing assembly 24 which in this example includes a number of components including, but not necessarily limited to, a cylinder block 26 , a cylinder head 28 , a hermetically sealed shell 30 , a discharge muffler 32 , and other components of the compressor.
- an electric motor 34 drives a piston 36 in reciprocating motion within a cylinder 38 .
- a valve plate 40 provides a discharge valve seat 42 for a discharge valve 44 and a suction valve seat 46 for a suction valve 48 .
- Additional components of the discharge valve assembly include a spider 50 attached to the face of valve plate 40 , a center plug 52 attached to spider 50 , and a spring 54 (e.g., a wave spring) that urges valve 44 against discharge valve seat 42 .
- suction valve seat 46 comprises an inner seat 46 a and an outer seat 46 b that define an annular suction opening 56 between the two.
- Suction opening 56 provides a gas passageway that runs past valve seat 46 .
- Suction valve 48 is a generally annular spring steel washer that is of a shape and size to overlie and cover suction opening 56 .
- suction valve 48 includes two outwardly protruding tabs 58 that engage a curved upper edge of cylinder block 26 .
- valve 48 moves to its open position to uncover suction opening 56 .
- the surface finish of suction valve seat 46 is produced by machining, turning or otherwise producing a spiral groove 64 on the face of valve plate 40 .
- Groove 64 is laid out along a spiral pattern similar to that of a phonograph record, and the center of the spiral 66 is generally in line with the center of valve seat 46 .
- Groove 64 preferably has an axial depth and a radial pitch that provides the face of the valve plate with a surface finish of about 10 to 250 microinches when measured along a radial path perpendicular to the groove.
- groove 64 provides a spiral path that extends multiple revolutions on both the inner and outer seats of valve seat 46 , whereby any minute backflow gas leakage along groove 64 when valve 48 is closed must make multiple passes or laps around each seating surface. To reduce fluid adhesion between valve 48 and seat 46 , groove 64 maintains at least some minute fluid communication across valve seat 46 when valve 48 is closed.
- discharge valve seat 42 comprises an inner seat 42 a on center plug 52 and an outer seat 42 b on valve plate 40 .
- the inner and outer seats define an annular discharge opening 68 between the two.
- Discharge opening 68 provides a gas passageway that runs past valve seat 42 .
- Discharge valve 44 is a generally annular spring steel washer that is of a shape and size to overlie and cover discharge opening 68 .
- Valve 44 is radially contained between a central post 70 and several peripheral posts 72 of spider 50 .
- a back surface 74 of spider 50 limits the axial movement of discharge valve 44 .
- Spring 54 interposed between valve 44 and surface 74 urges valve 44 to its closed position against discharge valve seat 42 .
- discharge valve 44 lifts away from valve seat 42 to an open position where valve 44 uncovers discharge opening 68 .
- the surface finish of discharge valve seat 42 is produced by machining, turning or otherwise producing a spiral groove 80 on the face of valve plate 40 and plug 52 .
- Groove 80 preferably has an axial depth and a radial pitch that provides the face of valve plate 40 and plug 52 with a surface finish of about 10 to 250 microinches when measured along a radial path perpendicular to the groove.
- groove 80 provides a spiral path that extends multiple revolutions on both the inner and outer seats of valve seat 42 , whereby any minute backflow gas leakage along groove 80 when valve 44 is closed must make multiple passes or laps around each seating surface. To reduce fluid adhesion between valve 44 and seat 42 , groove 80 maintains at least some minute fluid communication across valve seat 42 when valve 44 is closed.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
Abstract
Description
- 1. Field of the Invention
- The subject invention generally pertains to reciprocating compressors and more specifically to valves and valve plates of such compressors.
- 2. Description of Related Art
- To prevent backflow through a suction or discharge opening of a valve plate, compressors often use ring-type valves (similar in shape to washers) that can seal against the valve plate to cover the opening. In reciprocating compressors, the valves function as suction and discharge check valves that enable a reciprocating piston to compress the gas within a cylinder. The valves also determine which direction the gas flows through the compressor.
- The sealing surface of the valve plate against which the valve seals is known as a valve seat. Typically, the surface finish of both the valve and the valve seat are ground as smooth as possible to ensure a positive seal between the two. Although a smooth finish may provide a tight seal, such a surface finish can create several problems. One, adhesion of a fluid such as refrigerant or oil trapped between the valve and the valve seat can cause the valve to stick and delay its opening, which can reduce the operating efficiency of the compressor. Two, the resulting delayed opening can make a compressor noisy. Also, a smoothly ground surface can be costly to produce.
- Some compressors have something other than a smooth finish between the valve and the valve seat. The compressor disclosed in U.S. Pat. No. 1,718,350, for instance, has a series of concentric ridges on either the valve or its seat, thereby providing the valve with multiple seats for better sealing. Since the ridges are concentric, however, fluid can still be trapped within the concentric grooves that lie between the ridges. So even though such a design may provide better sealing, the design does not address the problem of liquid adhesion occurring between the valve and the valve seat.
- U.S. Pat. No. 5,078,582 discloses a compressor whose valve seats have a roughened surface to quiet the operation of the valve. It is not clear, however, how the surface is roughened. If the surface is created by a distribution of pits, the pits may provide pockets that trap fluid in a manner similar to that of the grooves disclosed in the '350 patent just described. If the surface, however, is roughened by a series of protrusions, fluid passageways winding around the protrusions may provide relatively short leakage paths across the valve. Although a compressor designed according to the '582 patent may be quieter, such a compressor is not necessarily more efficient.
- Consequently, a need exists for a compressor valve arrangement that is quieter, more efficient and less expensive than current valve arrangements.
- It is an object of the present invention to provide a reciprocating compressor with a valve plate that includes a valve seat with a spiral groove to reduce the noise, reduce the manufacturing cost, and/or increase the efficiency of the compressor.
- Another object of some embodiments is to provide a valve plate with a spiral groove so that when the valve is closed, the groove provides a minute fluid communication passageway between a cylinder and another chamber of the compressor.
- Another object of some embodiments is to create a valve seat with a spiral groove that provides the valve seat with a surface finish of between 10 and 250 microinches.
- Another object of some embodiments is to create a valve plate with an annular valve opening that is generally centered relative to a machined spiral groove in the valve seat.
- Another object of some embodiments is to incorporate both a suction valve seat and a discharge valve seat in a common valve plate, wherein both seats include a spiral groove.
- One or more of these and/or other objects of the invention are provided by a compressor that includes a valve plate, wherein the valve plate has at least one valve seat with a spiral groove.
-
FIG. 1 is a cross-sectional view of a compressor shown connected to a schematically illustrated refrigerant system. -
FIG. 2 is an enlarged view of the encircled portion ofFIG. 1 . -
FIG. 3 is an enlarged view of the encircled portion ofFIG. 2 . -
FIG. 4 is a view taken along line 4-4 ofFIG. 3 but with the suction valve and piston omitted. -
FIG. 5 is a view taken along line 5-5 ofFIG. 3 . - A
refrigerant system 10, shown inFIG. 1 , includes acompressor 12 for compressing refrigerant gas and for forcing the refrigerant sequentially through adischarge outlet 14 ofcompressor 12, through acondenser 16 that releases heat for condensing the refrigerant, through an expansion device 18 (e.g., expansion valve, capillary tube, orifice, etc.) for cooling the refrigerant by expansion, and through anevaporator 20 for absorbing heat from an outside source or heat load. Fromevaporator 20, the refrigerant returns tocompressor 12 via asuction inlet 22 to repeat the cycle. - Referring further to
FIGS. 2 and 3 ,compressor 12 comprises acompressor housing assembly 24, which in this example includes a number of components including, but not necessarily limited to, acylinder block 26, acylinder head 28, a hermetically sealedshell 30, adischarge muffler 32, and other components of the compressor. - To compress the refrigerant, an
electric motor 34 drives apiston 36 in reciprocating motion within acylinder 38. Avalve plate 40 provides adischarge valve seat 42 for adischarge valve 44 and asuction valve seat 46 for asuction valve 48. Additional components of the discharge valve assembly include aspider 50 attached to the face ofvalve plate 40, acenter plug 52 attached tospider 50, and a spring 54 (e.g., a wave spring) that urgesvalve 44 againstdischarge valve seat 42. - Referring to
FIG. 4 ,suction valve seat 46 comprises aninner seat 46 a and anouter seat 46 b that define an annular suction opening 56 between the two.Suction opening 56 provides a gas passageway that runs pastvalve seat 46.Suction valve 48 is a generally annular spring steel washer that is of a shape and size to overlie and cover suction opening 56. To holdvalve 48 in place yet allow the valve to resiliently flex between a closed position againstvalve seat 46 and an open position spaced apart fromseat 46,suction valve 48 includes two outwardly protrudingtabs 58 that engage a curved upper edge ofcylinder block 26. When the gas pressure differential between asuction chamber 60 andcylinder 38 is sufficient to forcevalve 48 away from valve seat 46 (as a result ofpiston 36 retracting or moving in areturn stroke 62 within cylinder 38),valve 48 moves to its open position to uncoversuction opening 56. - To minimize valve noise, to increase compressor efficiency, and/or to minimize the manufacturing cost of producing
valve plate 40, the surface finish ofsuction valve seat 46 is produced by machining, turning or otherwise producing aspiral groove 64 on the face ofvalve plate 40. Groove 64 is laid out along a spiral pattern similar to that of a phonograph record, and the center of thespiral 66 is generally in line with the center ofvalve seat 46.Groove 64 preferably has an axial depth and a radial pitch that provides the face of the valve plate with a surface finish of about 10 to 250 microinches when measured along a radial path perpendicular to the groove. To avoid creating a short, direct leak path betweensuction chamber 60 andcylinder 38,groove 64 provides a spiral path that extends multiple revolutions on both the inner and outer seats ofvalve seat 46, whereby any minute backflow gas leakage alonggroove 64 whenvalve 48 is closed must make multiple passes or laps around each seating surface. To reduce fluid adhesion betweenvalve 48 andseat 46,groove 64 maintains at least some minute fluid communication acrossvalve seat 46 whenvalve 48 is closed. - Referring to
FIG. 5 ,discharge valve seat 42 comprises aninner seat 42 a oncenter plug 52 and anouter seat 42 b onvalve plate 40. The inner and outer seats define an annular discharge opening 68 between the two.Discharge opening 68 provides a gas passageway that runs pastvalve seat 42.Discharge valve 44 is a generally annular spring steel washer that is of a shape and size to overlie andcover discharge opening 68. Valve 44 is radially contained between acentral post 70 and severalperipheral posts 72 ofspider 50. Aback surface 74 ofspider 50 limits the axial movement ofdischarge valve 44.Spring 54 interposed betweenvalve 44 andsurface 74urges valve 44 to its closed position againstdischarge valve seat 42. When the gas pressure differential betweencylinder 38 and adischarge chamber 76 overcomes the closing force of spring 54 (as a result ofpiston 36 extending or moving in acompression stroke 78 within cylinder 38),discharge valve 44 lifts away fromvalve seat 42 to an open position wherevalve 44 uncoversdischarge opening 68. - Again, to minimize valve noise, to increase compressor efficiency, and/or to minimize the manufacturing cost of producing
valve plate 40 and plug 52, the surface finish ofdischarge valve seat 42 is produced by machining, turning or otherwise producing aspiral groove 80 on the face ofvalve plate 40 and plug 52.Groove 80 preferably has an axial depth and a radial pitch that provides the face ofvalve plate 40 and plug 52 with a surface finish of about 10 to 250 microinches when measured along a radial path perpendicular to the groove. To avoid creating a short, direct leak path betweendischarge chamber 76 andcylinder 38,groove 80 provides a spiral path that extends multiple revolutions on both the inner and outer seats ofvalve seat 42, whereby any minute backflow gas leakage alonggroove 80 whenvalve 44 is closed must make multiple passes or laps around each seating surface. To reduce fluid adhesion betweenvalve 44 andseat 42,groove 80 maintains at least some minute fluid communication acrossvalve seat 42 whenvalve 44 is closed. - To provide additional information on the structure and function of
compressor 12, U.S. Pat. Nos. 4,811,757; 6,254,354; and 6,358,026 are hereby incorporated by reference herein. - Although the invention is described with respect to a preferred embodiment, modifications thereto will be apparent to those of ordinary skill in the art. Therefore, the scope of the invention is to be determined by reference to the following claims:
Claims (20)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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US11/246,841 US20070081910A1 (en) | 2005-10-07 | 2005-10-07 | Compressor valve plate with spiral groove |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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US11/246,841 US20070081910A1 (en) | 2005-10-07 | 2005-10-07 | Compressor valve plate with spiral groove |
Publications (1)
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US20070081910A1 true US20070081910A1 (en) | 2007-04-12 |
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ID=37911217
Family Applications (1)
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US11/246,841 Abandoned US20070081910A1 (en) | 2005-10-07 | 2005-10-07 | Compressor valve plate with spiral groove |
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Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2009124659A2 (en) * | 2008-04-11 | 2009-10-15 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Valve plate for a compressor, and method for cooling compressed air in a valve plate of a compressor |
Citations (13)
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US1718350A (en) * | 1929-06-25 | Valve fob pump assemblies | ||
US2151746A (en) * | 1936-07-14 | 1939-03-28 | Westinghouse Electric & Mfg Co | Compressor valve structure |
US2302447A (en) * | 1941-08-30 | 1942-11-17 | Gen Electric | Compressor valve |
US3628564A (en) * | 1969-10-02 | 1971-12-21 | Ford Motor Co | Fluid flow control valve assembly |
US4027853A (en) * | 1976-05-03 | 1977-06-07 | The Trane Company | Valve plate having improved suction gas flow path |
US4425836A (en) * | 1981-02-20 | 1984-01-17 | Government Innovators, Inc. | Fluid pressure motor |
US4723572A (en) * | 1987-07-20 | 1988-02-09 | Hoerbiger Corporation Of America, Inc. | Compressor valve |
US4834631A (en) * | 1988-04-04 | 1989-05-30 | Carrier Corporation | Separator and biasing plate |
USH974H (en) * | 1983-07-06 | 1991-11-05 | Thrust bearing and method of manufacturing thereof | |
US5078582A (en) * | 1990-01-16 | 1992-01-07 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Reciprocatory piston type compressor having a noise and vibration suppressed discharge valve mechanism |
US5452994A (en) * | 1994-02-16 | 1995-09-26 | Thermo King Corporation | Refrigerant compressor |
US5722818A (en) * | 1995-09-05 | 1998-03-03 | Sanyo Electric Co., Ltd. | Suction valve arrangement for a hermetic compressor |
US20020170604A1 (en) * | 2001-05-15 | 2002-11-21 | An Kwang Hyup | Valve plate structure |
-
2005
- 2005-10-07 US US11/246,841 patent/US20070081910A1/en not_active Abandoned
Patent Citations (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1718350A (en) * | 1929-06-25 | Valve fob pump assemblies | ||
US2151746A (en) * | 1936-07-14 | 1939-03-28 | Westinghouse Electric & Mfg Co | Compressor valve structure |
US2302447A (en) * | 1941-08-30 | 1942-11-17 | Gen Electric | Compressor valve |
US3628564A (en) * | 1969-10-02 | 1971-12-21 | Ford Motor Co | Fluid flow control valve assembly |
US4027853A (en) * | 1976-05-03 | 1977-06-07 | The Trane Company | Valve plate having improved suction gas flow path |
US4425836A (en) * | 1981-02-20 | 1984-01-17 | Government Innovators, Inc. | Fluid pressure motor |
USH974H (en) * | 1983-07-06 | 1991-11-05 | Thrust bearing and method of manufacturing thereof | |
US4723572A (en) * | 1987-07-20 | 1988-02-09 | Hoerbiger Corporation Of America, Inc. | Compressor valve |
US4834631A (en) * | 1988-04-04 | 1989-05-30 | Carrier Corporation | Separator and biasing plate |
US5078582A (en) * | 1990-01-16 | 1992-01-07 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Reciprocatory piston type compressor having a noise and vibration suppressed discharge valve mechanism |
US5452994A (en) * | 1994-02-16 | 1995-09-26 | Thermo King Corporation | Refrigerant compressor |
US5722818A (en) * | 1995-09-05 | 1998-03-03 | Sanyo Electric Co., Ltd. | Suction valve arrangement for a hermetic compressor |
US20020170604A1 (en) * | 2001-05-15 | 2002-11-21 | An Kwang Hyup | Valve plate structure |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2009124659A2 (en) * | 2008-04-11 | 2009-10-15 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Valve plate for a compressor, and method for cooling compressed air in a valve plate of a compressor |
WO2009124659A3 (en) * | 2008-04-11 | 2009-12-03 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Valve plate for a compressor, and method for cooling compressed air in a valve plate of a compressor |
US20110070101A1 (en) * | 2008-04-11 | 2011-03-24 | Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh | Valve Plate for a Compressor, and Method for Cooling Compressed Air in a Valve Plate of a Compressor |
US8337177B2 (en) * | 2008-04-11 | 2012-12-25 | Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh | Valve plate for a compressor, and method for cooling compressed air in a valve plate of a compressor |
CN101952591B (en) * | 2008-04-11 | 2013-06-12 | 克诺尔商用车制动系统有限公司 | Valve plate for a compressor, and method for cooling compressed air in a valve plate of a compressor |
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Owner name: AMERICAN STANDARD INTERNATIONAL INC., NEW YORK Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:BUTLER, ROY MICHAEL;BRANDT, GEORGE W.;PALMORE, THOMAS LEE;AND OTHERS;REEL/FRAME:017084/0166 Effective date: 20050926 |
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Owner name: TRANE INTERNATIONAL INC., NEW YORK Free format text: CHANGE OF NAME;ASSIGNOR:AMERICAN STANDARD INTERNATIONAL INC.;REEL/FRAME:020733/0970 Effective date: 20071128 Owner name: TRANE INTERNATIONAL INC.,NEW YORK Free format text: CHANGE OF NAME;ASSIGNOR:AMERICAN STANDARD INTERNATIONAL INC.;REEL/FRAME:020733/0970 Effective date: 20071128 |
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STCB | Information on status: application discontinuation |
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