|Publication number||USRE33082 E|
|Application number||US 06/775,661|
|Publication date||Oct 10, 1989|
|Filing date||Sep 13, 1985|
|Priority date||Sep 13, 1985|
|Publication number||06775661, 775661, US RE33082 E, US RE33082E, US-E-RE33082, USRE33082 E, USRE33082E|
|Inventors||Joseph Gerstmann, Andrew D. Vasilakis|
|Original Assignee||Advanced Mechanical Technology, Inc.|
|Export Citation||BiBTeX, EndNote, RefMan|
|Patent Citations (14), Non-Patent Citations (9), Referenced by (23), Classifications (13), Legal Events (9)|
|External Links: USPTO, USPTO Assignment, Espacenet|
This invention relates to water heaters. More particularly, it relates to water heaters in which vapor in the products of combustion is condensed to retrieve latent heat of vaporization.
With the increasing cost of fuel, methods for increasing in efficiency of heat exchanger assemblies for extracting heat from the products of combustion of fuel burners has become increasingly more cost effective. One means of increasing the efficiency of heat recovery has been to burn the fuel in small-volume, water-walled combustion chambers. Forced draft or pulsed combustion techniques are utilized to achieve high rates of heat transfer and to vent the products of combustion.
Recently, systems have been proposed to cool the products of combustion below the dew point temperature of those products, typically below 130° F., in order to condense some of the vapor and thereby extract the latent heat of vaporization of that vapor. To cool the products of combustion to that extent and to minimize the size, and thus the cost, of the heat exchanger assemblies, efficient heat exchangers must be designed.
An object of this invention is to provide an efficient water heating system in which heat is extracted from the products of combustion by condensing vapor in the products, the system having an acceptable size and cost.
The condensate from natural gas combustion products is mildly acidic, and the acidic nature of the condensate is expected to be a potential cause of corrosion. The acidic nature of the condensate may result from sulfuric acid, nitric acid, and carbon acid.
A further object of this invention is to provide a water heating system designed to withstand the corrosive effects of the condensate at a minimal cost.
In a heating assembly of this invention, primary and secondary heat exchangers and a combustion chamber are positioned within a single housing. The combustion chamber is defined by the primary heat exchanger. The combustion products flow through the primary heat exchanger at a sufficiently low velocity to keep the temperature of the heat exchanger walls at an acceptable level. The products of combustion are then directed into a secondary heat exchanger in which the velocity of the products of combustion is increased in order to increase the heat transfer coefficient of that heat exchanger. Cold water flows through the secondary heat exchanger in counter flow relationship with the combustion gases to cool those products to a temperature below the dew point temperature. Vapor in the products of combustion is thereby condensed. After being heated in the secondary heat exchanger, the water is mixed with hot water from the output of the primary heat exchanger and the water mixture is directed through the primary heat exchanger at a higher flow rate than in the secondary heat exchanger. The hot mixture of water entering the primary heat exchanger assures that no condensation of the products of combustion occurs at this heat exchanger.
In the preferred water heating assembly, the primary heat exchanger is a coil of tubing which defines the combustion chamber. Products of combustion flow radially through that coil. The secondary heat exchanger is a second coil of tubing coaxial with but lower than the first. Products of combustion flow through that coil axially at a higher velocity. Prior to combustion, the combustion air and fuel may be preheated by combustion products in a tertiary heat exchanger which receives those products from the secondary heat exchanger.
In a system in which hot water is stored in an insulated storage tank, cool water is taken from the bottom of the tank and introduced into the burner and heat exchanger assembly, and the heated water is returned to an upper section of the storage vessel in such a manner as to avoid of the heated water with the cooler water in the bottom of the vessel.
The preferred system utilizes a blower downstream of the burner and heat exchanger assembly for inducing a draft to propel the products of combustion.
The foregoing and other objects, features and advantages of the invention will be apparent from the following more particular description of preferred embodiments of the invention, as illustrated in the accompanying drawings in which like reference characters refer to the same parts throughout the different views. The drawings are not necessarily to scale, emphasis instead being placed upon illustrating the principles of the invention.
FIG. 1 is a block diagram of the water circuit of a preferred system embodying this invention;
FIG. 2 is an elevational cross sectional view of a preferred embodiment of the burner and heat exchanger assembly embodying this invention;
FIG. 3 is an elevational cross sectional view of a possible storage tank configuration for use with this invention;
FIG. 4 is an elevational cross sectional view of an insulated plastic lined storage tank for use in this invention.
A preferred system embodying this invention is shown schematically in FIG. 1. A storage tank 12 is connected to an external gas-fired water heater 14 by supply and return pipes 16 and 18. The water heater 14 comprises a primary, fired heat exchanger assembly 20 and a economizer 22 which is a secondary heat exchanger operating in the condensing mode. A circulating pump 24 placed between the economizer and the primary heat exchanger draws water from the return line 18 and from the economizer 22 and drives that mixture through the primary heat exchanger 20.
The storage tank is designed to maximize stratification between a small volume 32 of relatively cool water in the bottom of the tank and a larger volume 34 of stored hot water. In this case, the two volumes are separated by baffles 33. Typically the cool volume 32 is about 20 percent of the total tank volume. If hot water is taken from the outlet 38 of the storage tank while the heater 14 is in the standby mode, cold water is introduced into the lower volume 32 through a diffuser from a cold water inlet 31 and pipe 35.
When the heater assembly 14 is turned on, water is drawn from the lower volume 32 through pipe 16 if no water is being extracted through outlet 38; or a mix of water from the cold water inlet 31 and the lower volume 32 is drawn through pipe 16 if water is being extracted from the outlet 38. Water heated in the heater assembly 14 is returned through pipe 18 to the upper volume 34 in the storage tank 12. The baffles 33 inhibit mixing of the hot water from pipe 18 with the cooler water in the volume 32.
The cool water introduced into the economizer 22 through pipe 16 passes in counter flow heat exchange relationship with products of combustion which have already been cooled somewhat in the primary heat exchanger 20. The products of combustion and the water are sufficiently cool when introduced into the economizer 22 that the temperature of the products of combustion within the economizer is below the dew point temperature. This results in condensation of vapor in the products of combustion, and the latent heat of vaporization is transferred to the water in the economizer.
Water which has been preheated in the economizer 22 is introduced into the primary heat exchanger 20 which defines a combustion chamber. There the water is heated to the high temperature necessary for heating the water in the storage tank 12.
The purpose of the cold volume 32 should now be apparent. It provides a sufficiently large reservoir of cool water to enable the economizer to operate in the condensing mode throughout the on-cycle even when no cold water is drawn through the inlet 31 during the heating cycle. The volume of cool water should be minimized to reduce standby losses from and to limit the size of the storage. To that end, the cool water is rationed to the heater 14 at a low flow rate to condense vapor in the exhaust gas with a minimal amount of water.
The percentage of the storage tank which must be devoted to the volume of cooler water 32 can be determined from the following equation: ##EQU1## Where VH and VC are the respective hot and cool volumes 34 and 32, TR is the temperature of the water in return line 18, Tcut-in is the temperature of water in the storage tank at which the water heater is fired, and TDiff is the differential between the thermostat cut-in and cut-off temperatures. Typically, TR -Tcut-in is in the range of 40° to 50° F. To minimize standby losses and total tank volume, the volume VC should be less than 20 percent of the total tank volume. Thus, the thermostat differential temperature must be less than about 10° F. A temperature differential of 5° to 10° F. and a cool volume of 10 to 20 percent of the total tank volume are reasonable. For a given burner input, the flow rate through the heater can be controlled by a thermostatic valve 37 to maintain the desired return temperature. Alternatively, the flow rate might be held constant and the burner input .[.vaired.]. .Iadd.varied .Iaddend.to maintain the steady return temperature.
Placement of pump 24 between primary heat exchanger 20 and the secondary heat exchanger 22 is important for the following reason. Hot water from the outlet 28 of the primary heat exchanger is recirculated back to the inlet 30 to raise the water inlet temperature of that heat exchanger above the dew point temperature of the products of combustion. This is done to prevent condensation in the primary heat exchanger. To minimize the cost of the system, the primary heat exchanger is not protected against corrosion by flue gas condensate.
A further advantage of recirculating water through the primary exchanger is that it increases water flow rate and thus establishes high water-side heat transfer coefficients. This minimizes liming of the main heat exchanger coil. This is unnecessary in the economizer due to the significantly low heat fluxes and water temperatures in the economizer section.
The operating principle is best illustrated by the following example: Consider a 100 gallon tank with a thermostat that operates over a 10° F. differential and is located one fifth of the way from the bottom of the tank. Assume that the lower section 32 of the tank contains 20 gallons of water at an average temperature of 80° F, and that the average storage temperature is 140° F.
In the proposed concept, the water heater would use the 20 gallons of cooler water to heat 80 gallons of stored water from 135° F. to 145° F. During this process, the cooler water would be displaced by 135° F. water. A heat balance indicates that the total energy required is 15,700 Btu. If the heat output of the water heater is 157,000 Btu/hr, then the burner-on time is 6 minutes. In this case, the circulating pump 24 would draw water at the rate of 3.33 GPM from the bottom section and would return it to the top section at a temperature of 175° F. At the end of the on-cycle, the mixed temperature of the upper section will have reached 145° F., and the bottom section will contain water at 135° F. The flow control is preferably accomplished by thermostatic control of the return temperature to the tank by a valve 37 .[.at.]. .Iadd.as .Iaddend.this will prevent excessive temperatures if the bottom temperature, and thus the heater inlet temperature, gets too high. Alternatively, the desired flow rate may be set by a constant flow regulator or by a fixed orifice.
A variation of the concept might include the use of a separate, smaller preheat tank instead of the integral volume 32.
A preferred design of the water heater 14 is shown in FIG. 2. The primary heat exchanger consists of an integrally finned copper tube coil 42 surrounding the combustion chamber 44. This arrangement provides an efficient "water-wall" combustion chamber, which minimizes combustion chamber heat losses and requires a minimal amount of refractory insulation 46 and 48. Moreover, with radial flow through the coil, the large area of the coil facing the combustion chamber provides relatively low gas velocities. Such low gas velocities are necessary to prevent excessive wall temperatures due to the high temperature of the combustion products.
A mixture of natural gas and air is burned at a burner 50 within the combustion chamber. In a pipe 56 combustion air from an exterior inlet 52 is mixed with natural gas from a pipe 53 and nozzle 54. The desired air flow rate is established by fixed orifice 55. The mixture is drawn into the combustion chamber by a blower 58 positioned in the flue gas outlet. Alternatively, the mixture can be propelled by a blower placed upstream of the burner.
Combustion gases are collected in an exhaust annulus 60 before passing through the economizer coil. The gas temperature at the annulus is in the range of 250° to 400° F.
The combustion products are cooled further in the economizer coil 62 which is designed for condensing operation. Because of the corrosive properties of the condensate, the economizer is made of a corrosion-resistant material, such as 70/30 cupronickel. The economizer is designed for cross-counterflow of the combustion products. With axial flow of gasses through this coil, the combustion products flow at high velocities in order to achieve high heat transfer coefficients. Here, high gas-side transfer coefficients can be utilized without fear of excessive wall temperatures because both the gas and water temperature are much lower than in the main heat exchanger. Most of the system product of combustion pressure drop will occur in this section.
FIG. 2 also illustrates a third heat exchanger section 64. This is a counterflow pre-heater which uses the latent and sensible heat of the exhaust products to preheat the incoming gas/air mixture. The preheater 64 is a compact arrangement positioned concentrically within the economizer coil 62. Exhaust gas which has passed through the economizer is directed up through a first annulus 66 and then back down through a second annular 68. The annuli are separated by a cylinder 69 Gas in the annular 68 is in counter flow heat exchange relationship with the incoming mixture of natural gas and air. Any liquid which condenses from the exhaust gases in the preheater is collected in a reservoir 70. Also, any condensed liquid from the economizer 62 flows through holes 72 in the cylinder 69 into that same reservoir. The collected liquid is taken off through an anit-syphon tube 74 to the drain pipe 40. The anti-syphon tube insures that exhaust gas can not leak into the surrounding area but allows condensate to be drained from the heater.
With sufficiently low incoming water temperatures, the preheater 64 is probably unnecessary, since it will add less than 1% to the recovery efficiency. However, when incoming water temperatures are high, as may occur in a hot water booster, the air preheater may product worthwhile savings. The heat that can be recovered in this type of preheater is limited by the heat capacity of the incoming mixture. Typically, preheating the inlet mixture by 100° F. would increase efficiency by approximately 2.5%.
Losses in the system are minimized through the use of several design features. The combustion chamber is small and does not have a large inactive surface exposed to flame temperatures. The first stage heat exchanger is small with little water inventory. The bottom surface of the combustion chamber forms the top of the air preheater, so that heat losses in this direction will reenter the exhaust stream and increase the heat recovered in the preheater. Insulation is shown on this surface only for the protection of the metal surface which forms the bottom of the combustion chamber. This insulation may be eliminated if the exhaust gas can be utilized to cool this surface. The main "radiation" heat loss occurs through the top of the combustion chamber and along the outside shroud which contain the exhaust gas. Both these surfaces are insulated with insulation 78 to minimize these losses. The exhaust gas is relatively cool by the time it reaches the bottom of the unit and this surface need not be insulated.
Other significant features include the use of an induced draft blower which causes the unit to operate under negative craft conditions; thus, sealing the heater is not as critical as it would be if the unit were pressurized. Also since the exhaust gas is cool at this point, a plastic blower may be used to reduce costs and improved performance over a sheet metal blower.
The unit is shown using sealed combustion; that is, combustion air is drawn directly from the building exterior and exhaust gas is blown directly to the exterior. A natural convection stack is not feasible because of the low exhaust temperature. An alternative is the use of a conventional air intake plus exhaust through plastic pipe installed as a roof vent or through an unused chimney.
Alternative storage tanks are illustrated in FIGS. 3 and 4. The tank of FIG. 3 is conventional, with the exception of the provisions for stratification described above. This tank is a glass lined steel tank 80 surrounded by insulation 82 and a metal housing 84. The hot return pipe 18 .[.eenters.]. .Iadd.enters .Iaddend.through the side of the tank and directs the hot water upwardly into the upper volume 34. The baffle 33 is positioned below the hot return pipe 18 to assist in the natural stratification of the hot and cool water within the tank. Holes 86 in the baffle allow for displacement of water through the baffle as necessary. A diffuser 88 is positioned over the inlet pipe 35 so that flow between the volumes 32 and 34 is not induced by introduction of cold water into the tank. A thermostat 36 controls the operation of the heater.
An alternative version of the tank is illustrated in FIG. 4. This preferred tank structure includes a plastic lining 90 surrounded by insulation 92, such as foam insulation, and an outer steel tank 94. All connections to the interior of the tank are through a bottom plate 96. This arrangement includes the baffle 33 and the diffuser 88 as in the embodiment of FIG. 3. The thermostat 36 is also connected through the bottom plate 96 to a remote sensing bulb 98.
It should be noted that the baffle 33 is not absolutely necessary. It may be sufficient to have the hot return pipe outlet positioned sufficiently high within the tank that a lower volume of cool water remains. Also, flow directors may be mounted directly to the outlet of pipe 18 to avoid the need for a baffle 33 fabricated within the storage tank.
While this invention has been particularly shown and described within references to preferred embodiments thereof, it will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the spirit and scope of the invention as defined by the appended claims.
|Cited Patent||Filing date||Publication date||Applicant||Title|
|US2327339 *||Dec 24, 1940||Aug 24, 1943||Chandler Edward F||Heating system|
|US2937625 *||Apr 18, 1958||May 24, 1960||Robert L Meyers||Heating and hot water boiler|
|US3896992 *||Jul 18, 1974||Jul 29, 1975||Anton Borovina||Heat recovery system for space heating and for potable water heating|
|US4090474 *||Jun 4, 1976||May 23, 1978||Kauffmann Walter E||Hot water booster|
|US4136731 *||Aug 26, 1977||Jan 30, 1979||Deboer Richard J||Heat transfer apparatus|
|US4163430 *||Feb 8, 1978||Aug 7, 1979||Neumann Siegmar R||Heat recovery and filter system and process for furnace exhaust gases|
|US4222350 *||Jun 26, 1978||Sep 16, 1980||Boston Gas Products, Inc.||Efficient heating and domestic hot water apparatus|
|US4227647 *||May 22, 1978||Oct 14, 1980||Leif Eriksson||Device for cooling chimney gases|
|US4253446 *||Mar 20, 1978||Mar 3, 1981||Vama Vertrieb Von Anlagen Und Maschinen Gmbh & Co. Kg||Storage reservoirs for liquids heatable by solar energy|
|US4366778 *||Mar 26, 1981||Jan 4, 1983||Paquet Thermique, S.A.||Gas boiler able to operate in a sealed combustion circuit|
|US4401058 *||Aug 20, 1982||Aug 30, 1983||Paquet Thermique, S.A.||Gas boiler able to operate in a sealed combustion circuit|
|DE30162C *||Title not available|
|DE1907987A1 *||Feb 18, 1969||Sep 3, 1970||Wagner Geb||Zwangsdurchlauferhitzer fuer aus organischen Fluessigkeiten bestehende Waermetraeger|
|DE3041265A1 *||Nov 3, 1980||Sep 30, 1982||Wilhelm Kraemer||Boiler combustion gas heat-recovery method - uses granulate filling in combined heat exchanger and water-vapour absorber|
|1||Boston Gas Products, "Heat Maker Brochure", 1980.|
|2||*||Boston Gas Products, Heat Maker Brochure , 1980.|
|3||Hydro Therm, "Hydro Pulse Brochure", A1-379.|
|4||*||Hydro Therm, Hydro Pulse Brochure , A1 379.|
|5||*||Smay, V., High Efficiency Home Heating, Popular Science, Nov. 1979, pp. 60, 62, 158, 162, 164.|
|6||*||The Laars Type AF Heavy Duty Commercial Pool Heater, Laars Engineers, Catalog 3.1.001 4, 6/1/70.|
|7||The Laars Type AF Heavy Duty Commercial Pool Heater, Laars Engineers, Catalog 3.1.001-4, 6/1/70.|
|8||*||Water Supply Boiler/Heaters and Package Systems, Raypak, Catalog No. 3000 d, pp. 2 7, 8/1/78.|
|9||Water Supply Boiler/Heaters and Package Systems, Raypak, Catalog No. 3000-d, pp. 2-7, 8/1/78.|
|Citing Patent||Filing date||Publication date||Applicant||Title|
|US7428883 *||May 10, 2005||Sep 30, 2008||Noritz Corporation||Heat exchanger and water heater|
|US7634977||Aug 16, 2006||Dec 22, 2009||Aos Holding Company||Gas water heater|
|US8136485 *||Aug 11, 2006||Mar 20, 2012||Zenex Technologies Limited||Flue, and a boiler including such a flue|
|US8196386||Mar 19, 2008||Jun 12, 2012||Honeywell International Inc.||Position sensors, metering valve assemblies, and fuel delivery and control systems|
|US9273880 *||Aug 14, 2013||Mar 1, 2016||Elwha Llc||Heating device with condensing counter-flow heat exchanger|
|US9310113 *||Jan 4, 2013||Apr 12, 2016||Industrial Technology Research Institute||Thermoelectric heat pump apparatus|
|US9546798 *||Jul 31, 2012||Jan 17, 2017||Intellihot Green Technologies, Inc.||Combined gas-water tube hybrid heat exchanger|
|US9631808 *||Nov 21, 2014||Apr 25, 2017||Honeywell International Inc.||Fuel-air-flue gas burner|
|US20070221143 *||May 10, 2005||Sep 27, 2007||Noritz Corporation||Heat Exchanger and Water Heater|
|US20080066694 *||Aug 16, 2006||Mar 20, 2008||Aos Holding Company||Gas water heater|
|US20090126915 *||Jan 21, 2009||May 21, 2009||Zodiac Pool Systems, Inc.||Header for Heat Exchanger|
|US20090235665 *||Mar 19, 2008||Sep 24, 2009||Honeywell International, Inc.||Position sensors, metering valve assemblies, and fuel delivery and control systems|
|US20090272340 *||Aug 11, 2006||Nov 5, 2009||Zenex Technologies Limited||Flue, and a Boiler Including Such a Flue|
|US20100170452 *||Jul 4, 2008||Jul 8, 2010||Darren William Ford||Water heating apparatus, especially for pools|
|US20110303400 *||Jun 9, 2011||Dec 15, 2011||Pb Heat, Llc||Counterflow heat exchanger|
|US20130074786 *||Sep 26, 2011||Mar 28, 2013||Claude Lesage||Gas water heater with increased thermal efficiency and safety|
|US20130312426 *||Jan 4, 2013||Nov 28, 2013||Industrial Technology Research Institute||Drinking dispenser and thermoelectric heat pump apparatus thereof|
|US20140116657 *||Oct 26, 2012||May 1, 2014||Michael Charles Ritchie||Intercooler heat exchanger for evaporative air conditioner system|
|US20140326197 *||Jul 31, 2012||Nov 6, 2014||Sridhar Deivasigamani||Combined gas-water tube hybrid heat exchanger|
|US20150047812 *||Aug 14, 2013||Feb 19, 2015||Elwha Llc||Heating device with condensing counter-flow heat exchanger|
|US20160146455 *||Nov 21, 2014||May 26, 2016||Honeywell International Inc.||Fuel-air-flue gas burner|
|US20160146541 *||Dec 22, 2014||May 26, 2016||Fontecal S.P.A.||Double tubing condensation exchanger for heating water and/or for producing sanitary hot water|
|WO2010096858A1 *||Feb 12, 2010||Sep 2, 2010||Hydox Pty Ltd||Fluid heater|
|U.S. Classification||122/20.00B, 165/125, 122/33|
|Cooperative Classification||F24D11/005, Y02B30/102, F24H8/00, F24D11/004, F24H1/43|
|European Classification||F24H1/43, F24D11/00C4, F24H8/00, F24D11/00C3|
|Jan 30, 1989||AS||Assignment|
Owner name: AMTI HEATING PRODUCTS INC., A MASSACHUSETTS CORP.,
Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:ADVANCED MECHANICAL TECHNOLOGY, INC.,;REEL/FRAME:005014/0255
Effective date: 19890125
|Aug 7, 1998||AS||Assignment|
Owner name: JANDY INDUSTRIES, INC., PENNSYLVANIA
Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:TRIANCO HEATMAKER INC.;REEL/FRAME:009367/0406
Effective date: 19980731
|Dec 3, 1999||AS||Assignment|
Owner name: CHASE MANHATTAN BANK, THE, NEW YORK
Free format text: SECURITY INTEREST;ASSIGNOR:LAARS, INC.;REEL/FRAME:010444/0563
Effective date: 19991129
Owner name: CHASE MANHATTAN BANK, THE, NEW YORK
Free format text: SECURITY AGREEMENT;ASSIGNOR:JANDY INDUSTRIES, INC.;REEL/FRAME:010444/0585
Effective date: 19991129
|Jan 11, 2000||AS||Assignment|
Owner name: TRIANCO HEATMAKER INC., MASSACHUSETTS
Free format text: RELEASE OF INTEREST IN PATENTS;ASSIGNOR:ROYAL BANK OF SCOTLAND PLC, THE;REEL/FRAME:010499/0632
Effective date: 19991216
|Dec 26, 2000||AS||Assignment|
Owner name: WATER PIK TECHNOLOGIES, INC., CALIFORNIA
Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:TELEDYNE INDUSTRIES, INC.;REEL/FRAME:011379/0807
Effective date: 19991129
|Jan 22, 2001||AS||Assignment|
Owner name: LAARS, INC, CALIFORNIA
Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:WATER PIK TECHNOLOGIES, INC;REEL/FRAME:011449/0071
Effective date: 19991129
|Jul 1, 2005||AS||Assignment|
Owner name: JANDY INDUSTRIES, INC., CALIFORNIA
Free format text: RELEASE OF SECURITY INTEREST;ASSIGNOR:JPMORGAN CHASE BANK, N.A., FORMERLY THE CHASE MANHATTAN BANK;REEL/FRAME:016206/0837
Effective date: 20050628
Owner name: LAARS, INC., CALIFORNIA
Free format text: RELEASE OF SECURITY INTEREST;ASSIGNOR:JPMORGAN CHASE BANK, N.A., FORMERLY THE CHASE MANHATTAN BANK;REEL/FRAME:016206/0827
Effective date: 20050628
|Apr 24, 2006||AS||Assignment|
Owner name: JPMORGAN CHASE BANK, N.A. (F/K/A THE CHASE MANHATT
Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:JANDY POOL PRODUCTS, INC. (F/K/A LAARS, INC.);REEL/FRAME:017519/0021
Effective date: 20060412
|Apr 25, 2006||AS||Assignment|
Owner name: JPMORGAN CHASE BANK, N.A. (F/K/A THE CHASE MANHATT
Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:JANDY INDUSTRIES, INC.;REEL/FRAME:017519/0436
Effective date: 20060412