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Heating and refrigeration systems and methods using refrigerant mass flow

a technology of refrigerant and mass flow, which is applied in the direction of compression machines with non-reversible cycles, compression machines with reversible cycles, lighting and heating apparatus, etc. it can solve the problems of reducing the efficiency of refrigerant mass flow, restricting the mass flow of refrigerant, and high water absorption rate, so as to achieve no frictional impedance and increase costs

Inactive Publication Date: 2005-08-04
SMOLINSKY DAVID
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  • Summary
  • Abstract
  • Description
  • Claims
  • Application Information

AI Technical Summary

Benefits of technology

"The present invention is a method of heating or cooling air and liquids in confined spaces using vapor compression heat exchange systems. These systems are designed to increase mass flow of refrigerant throughout the system by replacing conventional refrigerant metering devices with a fixedly open orifice. This results in faster refrigerant flow and better heat absorption and dissipation, leading to improved efficiency and performance. The method can be easily incorporated into existing vapor compression heat exchange designs, allowing for the use of conventional refrigerants and reducing the need for costly redesigns."

Problems solved by technology

Unlike conventional heating and cooling systems, however, the vapor compression systems employed do not include conventional metering devices, such as capillary tubes, expansion valves, and the like, which restrict mass flow of refrigerant.
A problem with POE, in addition to its relative high monetary cost, is that it has a high tendency to absorb water, which is detrimental to the compressor.
This is significant since current teaching in the industry is to extensively redesign current systems, resulting in increased costs due to factory re-tooling and the re-training of service personnel.

Method used

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  • Heating and refrigeration systems and methods using refrigerant mass flow
  • Heating and refrigeration systems and methods using refrigerant mass flow
  • Heating and refrigeration systems and methods using refrigerant mass flow

Examples

Experimental program
Comparison scheme
Effect test

example 1

[0041] In September 1999, performance tests were performed by Intertek Testing Services (Cortland, N.Y.) on a Model HTS 120A-1B heat pump pool heater charged with R-22 refrigerant. The pool heater included a thermostatic expansion valve as the refrigerant metering device. The system included a ZR 67 Copeland brand compressor. Table 4 lists the conditions and results of the test. The tests were conducted in

TABLE 4LowSpaStandardTemperatureConditionsRating TestTestTestAir SideAmbient Temperatures, ° F.Dry Bulb80.6050.2080.80Wet Bulb70.9544.3571.00Pool SideWater Temperatures, ° F.Entering80.1579.95104.90Leaving84.1582.85108.70Water Flow, gpm40.0540.0540.00Electrical CharacteristicsVoltage, volts230230230Current, amps24.922.831.4Power Input, watts5,4154,9306,850Refrigerant CircuitTemperatures, ° F.Discharge at compressor171.5162.5198.5Liquid at TXV102.595.0124.5Vapor at Evaporator69.534.571.0Suction at Compressor69.536.071.0Refrigerant CircuitPressures, PSIGDischarge at compressor23821...

example 2

[0042] In August 2000, performance tests were performed by Intertek Testing Services (Cortland, N.Y.) on a Model HTS 120A-1D heat pump pool heater charged with R-410A refrigerant. The pool heater included an orifice coupler disposed between the evaporator and condenser to maintain the pressure differential between the condenser side and evaporator side of the heater. The orifice size was 0.136 inch (29 drill size). The system included a ZR 67 Copeland brand compressor. Table 5 lists the conditions and results of the test.

TABLE 5LowSpaStandardTemperatureConditionsRating TestTestTestAir SideAmbient Temperatures, ° F.Dry Bulb80.6050.1080.50Wet Bulb71.0044.2071.15Pool SideWater Temperatures, ° F.Entering80.2580.00103.75Leaving86.2583.60109.15Water Flow, gpm44.9045.0545.05Electrical CharacteristicsVoltage, volts230230230Current, amps39.132.446.7Power Input, watts8,5907,12010,200Refrigerant CircuitTemperatures, ° F.Discharge at compressor144.5122.5163.0Liquid at TXV88.591.5110.0Vapor at...

example 3

[0043] In October 2000, performance tests were performed by Intertek Testing Services (Cortland, N.Y.) on a Model HT 115A-1B heat pump pool heater charged with R-22 refrigerant. The pool heater included an orifice coupler disposed between the evaporator and condenser to maintain the pressure differential between the condenser side and evaporator side of the heater. The orifice size was 0.128 inch (30 drill size). The system included a ZR 67 Copeland brand compressor. Table 6 lists the conditions and results of the test.

TABLE 6LowSpaStandardTemperatureConditionsRating TestTestTestAir SideAmbient Temperatures, ° F.Dry Bulb80.6050.0580.50Wet Bulb71.0544.3071.15Pool SideWater Temperatures, ° F.Entering79.9080.00103.95Leaving84.6082.85108.25Water Flow, gpm45.0045.0044.95Electrical CharacteristicsVoltage, volts230230230Current, amps28.723.833.8Power Input, watts6,2505,1307,430Refrigerant CircuitTemperatures, ° F.Discharge at compressor136.5105.0157.0Liquid at TXV81.084.5100.5Vapor at Ev...

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PUM

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Abstract

Methods employing the use of vapor compression heat exchange systems are disclosed that allow for optimal mass flow of refrigerant there through. The systems employed in the present invention do not use conventional refrigerant metering devices, such as capillary tubs and expansion valves, which restrict mass flow, but rather incorporate an openly fixed orifice in-line with the conduits connecting the condenser to the evaporator, thereby maintaining the preferential differential between the high pressure condenser side and low pressure evaporator side of the system during operation. Provision of the fixed orifice allows for optimal refrigerant mass flow as measured by cooler compressor temperatures, cooler compressor discharge temperatures, increased heat of rejection, increased heat of absorption, and improved heating and cooling efficiency.

Description

[0001] This application is a continuation of U.S. Ser. No. 10 / 350,811, filed Jan. 24, 2003 (and which is incorporated by reference herein in its entirety), which is a continuation of U.S. Ser. No. 09 / 815,295, filed Mar. 22, 2001 (which is incorporated by reference herein in its entirety), and which in turn is a continuation-in-part of Ser. No. 09 / 426,780, filed Oct. 22, 1999, now U.S. Pat. No. 6,227,003 issuing on May 8, 2001.BACKGROUND OF THE INVENTION [0002] A. Basic Components of Conventional Heating and Cooling Systems: [0003] Most conventional heating and cooling systems comprise a motorized compressor, an evaporator, a condenser, and a series of conduits in communication with the compressor, evaporator, and condenser. The conduits carry high pressure refrigerant gas from the compressor to the condenser, where the gas is condensed to a liquid upon dissipation of latent heat from the condenser. The refrigerant liquid is then carried through a refrigerant metering device to the e...

Claims

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Application Information

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Patent Type & Authority Applications(United States)
IPC IPC(8): F25B9/00F25B13/00F25B31/00F25B41/06F25B43/00
CPCF25B9/008F25B13/00F25B31/002F25B2500/01F25B43/006F25B2309/06F25B41/067
Inventor SMOLINSKY, DAVID
Owner SMOLINSKY DAVID