MXPA03008601A - Heating and refrigeration systems using refrigerant mass flow. - Google Patents

Abstract

Vapor compression heat exchange systems are disclosed that are designed to allow for optimal mass flow of refrigerant there through. The systems of the present invention do not employ 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. The present invention may employ any conventional refrigerant including the newer HFC refrigerants, such as R-410A.

Description

HEATING AND REFRIGERATION SYSTEM USING REFRIGERANT MASS FLUID DESCRIPTION OF THE INVENTION A. The basic components of conventional systems of 4 heating and cooling: Conventional heating and cooling systems should include a motorized compressor, an evaporator, a condenser, and a series of ducts in communication with the compressor, evaporator and condenser. The conductors carry high pressure refrigerant gas from the compressor to the condenser, where the gas is condensing a liquid for the latent heat dissipation of the condenser. The coolant is then carried by a measuring device to the evaporator, where the latent heat is absorbed to vaporize the coolant. The result of the low pressure refrigerant gas is then sucked into the compressor where it is compressed once again into high pressure gas, and the cycle is repeated. The refrigerant measuring device allows the refrigerant to flow from the high pressure condenser to the low pressure evaporator and also functions to maintain this differential pressure while the compressor is operating. In the evaporator, the refrigerant liquid, under a reduced pressure, absorbs the heat and is rapidly vaporized, and the evaporator is cooled. The compressor creates a low pressure by sucking the refrigerant gas from the evaporator and then comprises the gas residue at a high pressure. Generally the refrigerating measuring apparatus includes expansion valves (e.g., automatic expansion, thermostatic expansion and thermoelectric expansion) and capillary tubes. To regulate the refrigerant fluid, the expansion valves use feedback on conditions in the suction line and / or evaporator. Expansion valves are the most common type of measuring devices and are provided for operation over a wide range of temperature conditions. The expansion valves are also used in these systems to support or restrict the refrigerant fluid to prevent the flooding of the compressor, the credible thing is that such a flood will include the operation of the majority of the compressor and ultimately causes damage to the entire system. The capillary tube, on the other hand, has a fixed restriction diameter which serves as a constant backup in the coolant fluid. The width, diameter, and configuration of the capillary tube as well as the operating temperature and differential pressure that crosses the capillary tube affecting the average refrigerant fluid. Thus, the uneven expansion valve, the capillary tube can not be adjusted and is only effective over a narrower range temperature for a given compressor. B. Refrigerants For years, the most common coolant of choice in hot pumps and air conditioning systems has been R-22, a hydrochlorofluorocarbon (HCFC). HCFC does not harm the ozone layer like chlorofluorocarbon (CFC), which has been completely realized since 1996; however, HCFC still contains chlorine that damages the ozone layer, according to the 1992 amendments to the Montreal Protocol [an international agreement on the global environment requiring CFC ozone depletion], has been an established schedule for the execution of HCFC. As a gradual result of the execution of refrigerants containing chlorine, the ozone layer does not decrease, alternate refrigerants have been introduced. A substitute deemed acceptable by the EPA is R-410A, a mixture of hydrofluorocarbon (HFC) that does not contribute to depletion of the ozone layer. R-410A, which will soon be required in all new heating and cooling systems installed, is also a very efficient refrigerant, has up to 30% more heating capacity. A disadvantage to the use of R-410A and similar refrigerants, however, is that the current R-22 hot pump and air conditioning systems using conventional measuring devices are designed to accommodate the high pressure characteristics of these refrigerants. In fact. , the use of R-410A in conventional hot pump and air conditioning systems often results from burning the compressor due to numerous factors, such as increasing the temperature and pressure of the system and the absorption of water inside the compressor due to the presence of oils synthetic lubricants which should be used with these high pressure refrigerants. Such redesigns of the current heating and cooling system will result in a huge financial expense in terms of re-assembly manufacturing as well as personnel training. In view of the foregoing difficulties with the refurbished HFC refrigerants, it is desirable to incorporate it as soon as possible, less costly modifications for existing systems that will allow the accommodation of these refrigerants without sacrificing heating or cooling efficiency and without damaging the system itself. The present invention will accommodate these new refrigerants as well as current HFC refrigerants such as R-22 with minimal modification to existing heating and cooling designs.

DESCRIPTION OF THE INVENTION The present invention is directed, in certain aspects, to high temperature compression exchange systems comprising, in part, the common components for many current heating and cooling systems, called, a compressor, an evaporator, a condenser, a refrigerant, and a series of ducts to carry the refrigerant throughout the system. Similar heating and cooling systems, however, the present invention does not include conventional measuring devices, such as capillary tubes, expansion valves and the like, which restrict the refrigerant mass fluid. In spite of this, the present invention is designed to provide the increase of the refrigerant mass fluid through the heating and cooling system, in addition it replaces the conventional refrigerant mass fluid by restricting measuring devices with a fixed open orifice exposed in line with the ducts connected to the evaporator and condenser. The functions of the gap to maintain the necessary differential pressure between the high pressure condenser and the low pressure evaporator. The combination of a diameter hole of an optimum size, refrigerant charge, and large diameter ducts provide for the increase of the refrigerant mass fluid through the system that is almost four or five times faster than the refrigerant fluid that passed before by the system using conventional expansion valves or capillary tubes. Conversely to be believed by those skilled in the art, they say that the refrigerant mass fluid should be restricted in time to minimize the inundation of the condenser, the inventor has discovered that the refrigerant mass fluid increases providing numerous benefits without compromising life of the compressor. Some of these advantages are the following: (1) to increase the mass fluid (ie by moving a greater volume of refrigerant per unit of time through the system), a larger volume of refrigerant per unit of time is presented to the respective heat exchangers (ie evaporator and condenser) , with that optimizes the ability of the refrigerant to absorb and dissipate the heat through the evaporator and condenser, respectively. Stated otherwise, the larger refrigerant mass fluid increases the heat absorption in the evaporator, thereby making use of the present invention for both cooling and heating applications. In a pool by applying a heating pump, for example, the inventor managed to close 100% heat exchange from the condenser in the condenser to the water coil (typical efficiencies in the systems shown above in a range of 50% at 85%). (2) Increase the reduced mass fluid by operating the pressure of R-410A and another HFC refrigerant, allowing the substitution of non-synthetic lubricating oils, such as mineral oils, for expensive synthetic oils, such as polyester (POE) (POE) is recommended for use with R-410A since there is no brake to high temperatures such as mineral oil). A problem with POE, in addition to its high relative monetary cost is that it has a high tendency to absorb water, which is detrimental to the compressor. The present invention allows the use of more economical and less hygroscopic oils, such as mineral oil, when R-410A, for example, is employed without fear that it will break during the operation of the system. (3) The refrigerants drag the lubricating oil to give ample lubrication of the compressor, even for oils that are not mixed with the refrigerant. (4) The compressor is properly frozen by suction of high frozen fluid, for this reason the life of the compressor is extended. While compressors in conventional systems are warm to contact during operation (up to 200 ° F), the compressor in the present invention is discreetly frozen (approximately 65 ° F). (5) The result of the high mass fluid allows the compressor to discharge temperatures to keep away the low temperatures reached using conventional industrial methods. It should be noted that while a capillary tube also provides for a narrow fixed diameter through which the cooling fluids between high and low pressure of the system, the coolant mass fluid is much more restricted through capillary tubes due to friction within the length of the capillary tube. A fixed open hole, on the other side, maintains a differential pressure between the high and low pressure sides, but allows the coolant to flow with less restriction - hence, there is no additional length of the narrow tube to retard the lower coolant. In other words, it takes more time for the refrigerant to flow through the length of the capillary tube compared to the orifice, which is essentially not wide (less than one inch), and without friction impediment. A key characteristic of the present invention is that it can easily be incorporated into the existing high compression vapor of exchanged designs for use with conventional refrigerants, such as HCFC's as well as HFC's, and as R-410A. This is significant since the current sample in the industry is to extensively redesign current systems, resulting in increased costs due to the manufacture of tools- and re-training of the personnel service. Simply to replace there are refrigerant measuring devices with a fixed opening having a diameter that provides for optimum refrigerant mass fluid, as a measure of the compressor for temperature discharge, temperature compressor, and achieved efficiency of heating and cooling, for example, systems Current heat exchangers may be able to effectively handle all refrigerants on the market, including HFCs.

BRIEF DESCRIPTION OF THE FIGURES Fig. 1 is a schematic representation of the main components of the heat exchange system.

Fig. 2 is a broad exploratory view of an adapter hole positioned between the two conduits.

Fig. 2A is a cross section taken along the lines 2A -2A of Fig. 2 showing the hole.

Fig. 2B is a cross-section of a conduit taken along the lines 2B-2B of Fig. 2.

Fig. 3 is a schematic representation of the main components of an alternate incorporation of the heat exchange system.

Fig. 3A is an enlarged view of a cross-section taken along lines 3A-3A of Fig. 3 showing the hole within the conduit.

Fig. 4 is a cross-sectional view taken of a third embodiment of the orifice provided by a layer located within the conduit.

DETAILED DESCRIPTION OF THE PREFERRED INCORPORATIONS Now referring to the figures, the present invention, in certain aspects, is directed to the systems of heat exchange and vapor compression (10, 100) designed to allow an increase in the mass fluid of the refrigerant there is. through optimum efficiency in the low operation of pressures and temperatures. The inventiveness of vapor compression in heat exchange systems includes, but is not limited to, air-for-air and liquid-for-air heating or cooling systems for heating or cooling, respectively, air in restricted spaces (eg interiors of the built) and air for - liquid and liquid - for - liquid in heating and cooling systems for cooling or heating respectively, liquids in restricted spaces (eg industrial liquids, swimming pool / spas water, water in fish tanks, etc). The vapor compression in heat exchange systems of the present invention can be one of the applicable systems (i.e. only in heating systems or only in cooling systems) or in reverse cycles of the system. The samples and dimensions of the orifice described in this are from 4 tons to 6 tons of heat exchange systems; however, the present invention can be applied in smaller systems (e.g., home or commercial refrigerators) as well as larger ones (e.g. from 12 tons to 500 tons or larger), as will be seen below. Conventional heating and cooling systems, the present invention comprises a condenser (12,120), an evaporator (13,130) and a compressor (11, 110). Depending on the size of the system, more than an evaporator and / or condenser can be used. A series of conduits (30,300) is also used by the system to carry refrigerants from the compressor (11, 110) to the respective heat exchangers (i.e. evaporator and condenser). Not equal to the vapor compression of heating and cooling systems, however, the systems of the present invention do not include any conventional refrigerant measuring apparatus, such as expansion valves and capillary tubes, which restrict the refrigerant mass fluid . Contrary to popular industrial thinking, it has been discovered by the inventor that the refrigerant mass fluid is not detrimental to the compressor and, in fact, increases the total life of the compressor while at the same time providing for the increased heat of rejection (from the condenser), the heat increasing in absorption (from the evaporator), and improved heat (or cooling) efficiently. To achieve an optimum refrigerant mass fluid, thereby resulting in improved heat (for heating systems) or cooling (for refrigeration systems) as well as a freezing compressor and temperature discharge compressor, the present invention incorporates a fixed orifice open (40,400) located on-line with one or more conduits (31, 310) connecting to the evaporator (13, 130) and condenser (12,120). The function of the fixedly open orifice (40,400) is to allow the optimum increase of the mass fluid while maintaining the required differential pressure between the high pressure condenser (12a, 120a) and low pressure of the evaporator (13a, 130a) of the system. As used herein, the term "open-ended" refers to the state of the orifice diameter (d) during the operation of the heat exchange system, named that, the orifice (40,400), recalls the fully-opened opening during the operation of the system. In other words, the diameter of the orifice (d) not adjusted during the operation of the system as an expansion valve but is fixed in an open position. Also, there are no valves, pistons or anything that covers or blocks the hole during the operation. Those, the hole is fixed, open position while the system is operating. On the other hand, the term "orifice" refers to an individual opening through which the refrigerant can flow and which for the most part has a negligible length relative to the measurement of the heat exchange system (less than one inch, for example, from 4 tons to 6 tons in the systems). The "orifice" is distinguished from a "tube", like the capillary tube, which is not an individual opening but preferably comprises an inner channel in communication with the two openings at opposite ends. As shown in Fig. 2, an apparatus for providing the orifice of the present invention is in an adapted hole (50). The adapter (50) has two open ends (51), generally cylindrical and preferably threaded, meshed with the respective ends (31a) of the conduits (31) connecting the evaporator (13) and condenser (12). The adapter (50) may be designed to be removed from the system or permanently welded to the conduits. The adapter (50) has an inner channel (41) slightly narrower in diameter than the channel (42) of the connected conduits (31) and a centrally located hole (40) having a negligible length (less than one inch) and a internal diameter with an average of 0. 20 inches to 0.250 inches (from 4 tons to 6 in heat exchange systems). The diameter of the orifice (and / or a conduit hole for multiple conduits running in parallel between the condenser and the evaporator) are required by larger systems. While an adapter will be appreciated by those skilled in the art that other means of providing the orifice may be provided, including, but not limited to, the provision of one or more rings-or within the same conduit. The conduit can also be provided with a thick internal wall or cutout (311) to form a suitable hole (400) in (see Fig. 3A). Alternatively, a layer (55) can be fitted inside the conduit (310) and supported therein resting on the internal walls (312) of the conduit as shown in Fig. 4. The layer (55) can have perforated there through an orifice properly measured (401). A removable adapter hole (50) as shown and described this, however, preferably when the diameter of the orifice is being adjusted by a given system. While the orifice is fixedly open as discussed above, it will be taken into account by skilled artisans that an orifice adapter, for example, may be designed such that the orifice diameter measurement may be adjusted by a particular prior system for operation (not shown). ). However, even the orifice of an adjusted orifice will remain fixedly open at the selected diameter during the operation of the system - therefore, it will not be wider or narrower due to established feedback conditions while the system is operating. For the optimum coolant mass fluid, a hole diameter measurement is selected which provides a cooling compressor head, a suitable temperature discharge compressor (usually 180 ° F or less), increasing the heat of rejection in BTU (from the condenser) and / or increasing the heat of absorption in BTU (from the evaporator), and optimal heating efficiency and cooling (approximately 25% increasing efficiency over previous systems). Several conditions will affect the size of the selected orifice, such as the refrigerant used, the refrigerant charge, and the type of compressor. Table 1 provides optimal measurements of the orifice diameter given by a compressor, refrigerant, and refrigerant charge. It will be recognized by those skilled in the art, however, the size of the holes (generally within 0.120 to 0.25 inches average for systems up to 6 tons) can be adjusted by other compressors, refrigerants and temperatures to obtain an optimum refrigerant mass fluid , resulting in increased heat rejection (condenser), increased heat absorption (evaporator) and maximum efficiency while maintaining the compressor freezer and temperature discharge compressor. In general, heating and cooling systems have larger duct systems and will require larger orifice sizes to obtain optimum mass fluid. Larger compressors and all systems also require larger hole sizes. Table 1 provides a good starting point guide in hole measurements for systems comprising different compressors and refrigerants. As mentioned above, the optical hole diameter selected is based on a balance between optimal cooling (or heating) efficiency, increasing the heat of rejection in BTU and / or increasing heat absorption in BTU, head of the cooling compressor (cold to contact), and the freezer compressor discharges temperatures (preferably less than 180 ° F).

Generally, only one hole is required to be located inside the evaporator / condenser connecting the conduit (31,310). However, where two or more conduits are employed, in parallel, to connect multiple evaporators to multiply condensers (not shown), an adapter hole, for example, through conduit may be installed.

This is generally the case for larger systems using many larger compressors and multiple evaporators. Conventional heating and cooling systems are charged with refrigerant according to weight. For example, a 6-ton system would be loaded with approximately 4 pounds of R-22 refrigerant. For the present invention, however, the inventor has discovered that the optimum results, charging the system with a selected refrigerant to obtain a certain pressure condenser for a given liquid or air temperature to be heated or cooled as it preferably is. The list in Table 2 preferably pressures charged for a water or air temperature granted to be heated.

Table 1 Compressor measurement Refrigerant Total heat load measurement of nominal rejection coolant hole 5, 000 BTU R-410A 0.120 inches See table2 92,000 BTU (hole measurement 31) 55,000 BTU R-410A 0.120 inches See table 2 99,000 BTU 63,000 BTU R-410A 0.120 inches See table 2 123,000 BTU (hole measurement 31) 67,000 BTU R-410A 0.136 inches See table 2 136.0D0 BTU (hole measurement 29) Table 2 Pressure of the diagram of the charging systems in relation to the water or air temperature R-410A The pushing temperature of the water or air for the condenser (° F) Loading for the high-pressure side 50 242.9 PSl 60 270.3 PSl 70 301.2 PSl 80 335.9 PSl 90 374.5 PSl 100 417.5 PSl For a water or air temperature, a sufficient amount of refrigerant added to achieve the pressure shown in the table.

Table 3 Pressure diagram of charging systems in relation to water or air temperature R-22 Water or air temperature High pressure side charging For condenser (° F) 50 165 PSl 60 185 PSl 70 210 PSl 80 235 PSI 90 275 PSI 100 320 PSI For an air or water temperature, a sufficient amount of refrigerant is added to achieve the pressure shown in the table. Conventional heating and cooling systems comprise conduits of different internal diameters, depending on their respective location within the system. For example, even for 6-ton systems, the conduit between the evaporator and compressor has an internal diameter averaging from 3/4 to 7/8 inches. For the same systems, the conduit between the condenser and the refrigerant measuring device has an average internal diameter from 1/2 to 5/8 inches. And the conduit between the evaporator and the refrigerant measuring apparatus has an average internal diameter from 3/8 to 1/2 inches. For the optimum mass fluid in the present invention, the conduits used would be on the larger side of the diameter by a particular conduit location. In addition, while any evaporator and condenser can be used in the present invention, it is important for the mass fluid of the refrigerant and the efficiency that the evaporator and the condenser select to be suitable partners for the system based and giving the measure of the compressor and conditions . While the objective in the present invention is to achieve the optimum mass fluid of the refrigerant, which compared to conventional heating and cooling systems in the prior art is a substantially increase in the velocity of the mass fluid, it is important to note that "optimum "Mass fluid is not necessarily equal to" as fast "as possible of the mass fluid. Therefore, if there is too much mass fluid, too much refrigerant freezing, then resulting in the compressor suspending since there is no heat to pump the compressor to start recycling. Too much mass fluid is obviously decreasing the heating or cooling efficiency.

The present invention will work with any refrigerant known to those skilled in the art using vapor compression in heat exchange systems, including, but not limited to, hydrochlorofluorocarbon (HCFC), hydrofluorocarbons (HFC), chlorofluorocarbons, and working with natural fluids. such as carbon dioxide, hydrocarbons (eg propane) and ammonium, and mix them (eg HFC / hydrocarbon bonds, such as R-407C). Exemplifying HFC including R-410A, R-410B, R-134a, R-152a, R-32, R-125. However, as mentioned above, the present invention is in advantage over the conventional system in which it works well with the newer, as soon as required, the HFC refrigerants, such as R-410A, which operates at high pressures and temperatures. in conventional heating and cooling systems. For example, generally high pressure ends for R-410A average from 600 to 800 PSI in conventional systems. In the present invention, high pressure ends for R-410A drop to 450 PSI. Similar low pressure with R-22, which generally runs about 100 PSI less than R410A at the high pressure end. Another aspect of the present invention is a simple method of modifying existing heating and cooling systems by replacing the conventional measuring device with an adapter orifice or providing a hole within the system conduit as described herein to maintain differential pressure. required between the high and low pressure ends of the system as well as removing all the restrictions of the other refrigerant fluid while allowing the optimum refrigerant mass fluid. Another feature of the present invention is that the compressor that lubricates oils can be used (both mixtures and not mixable with the refrigerant). In conventional heat exchange systems, POE is recommended if it is not required for use with HFC high pressure refrigerants, such as R-410A, since it does not interrupt high temperatures like some of the non-synthetic oils, such as mineral oil. The present invention, however, will work well with mineral oil and other non-synthetic oils, such as alkylbenzene, for example, even when high pressure HFC refrigerants are used.

The following samples do not propose the scope limit of the invention, but proposed to illustrate various aspects of the invention.

Sample 1 In September 1999, the tests shown were taught by Intertek Testing Services (Cortland, New York) on a Model HTS 120 A-B hot pump heater tank loaded with R-22 refrigerant. The heating tank includes a thermostatic expansion valve as the refrigerant measuring device. The system included a ZR 67 Copeland brand of the compressor. The lists in Table 4 show the conditions and results of the test. Table 4 Standard average of the low temperature of the test conditions SPA test the test end of the air Ambient temperatures, ° F Dry bulb 80.60 50.20 80.80 Wet bulb 70.95 44.35 71.00 Tanaue side Water temperatures, ° F Input 80.15 79.95 104.90 Output 84.15 82.85 108.70 Water fluid, gpm 40.05 40.05 40.00 Electrical characteristics Voltage, volts 230 230 230 Current, amps 24.9 22.8 31.4 Input power, watts 5,415 4,930 6,850 Refrigerant circuit TemDeraturas. ° F Compressor discharge 171.5 162.5. 198.5 Liquid in TXV 102.5 95.0 124.5 Steam in evaporator .69.5 34.5 71.0 Suction in compressor 69.5 36.0 71.0 Refrigerant circuit Pressures. PSIG Compressor discharge 238 215 311 Compressor suction 82 53 88 Barometric Pressure in (Ha.) 28.71 28.76 28.77 Test Conditions Heat capacity (BTU / hr) 80,350 58,500 Sample Coefficient 4.34 3.47 (COP) Sample 2 In August 2000, the tests shown were performed by Intertek Testing Services (Cortland, New York) on a Model HTS 120A-1D heating pump for tank heater charged with R-410A refrigerant. The tank heater included an orifice adapter located between the evaporator and the condenser to maintain the differential pressure between the condenser and the heater evaporator. The orifice measurement was 0.136 inches (hole measurement 29). The system included a compressor ZR 67 Copeland brand. List the table 5 the conditions and results of the test.

Table 5 Standard average Low temperature of the SPA conditions of the test test test End of air Ambient temperatures, ° F Dry bulb 80.60 50.10 80.50 Wet bulb 71.00 44.20 71.15 Tank end Water temperatures, ° F Input 80.25 80.00 103.75 Output 86.25 83.60 109.15 Water flow, gpm 44.90 45.05 45.05 Electrical characteristics Voltage, volts 230 230 230 Current, amps 39.1 32.4 46.7 Input power, watts 8,590 7,120 10,200 Refrigerant circuit Temperatures, ° F Discharge in the compressor 144.5 122.5 163.0 Liquid in TXV 88.5 91.5 110.0 Vapor in evaporator 51.0 27.5 55.0 Suction in compressor 50.0 27.0 54.0 Refrigerant circuit PSIG pressures Compressor discharge 383 324 474 Compressor suction 131 84 151 Barometric pressure (in. Ha.) 28.86 28.86 28.86 Test conditions Heating capacity (BTU / hr) 135,060 81, 570 122,010 Sample coefficient ( COP) 4.60 3.35 3.50 Sample 3 In October 2000, the test shows that it was performed by Intertek Testing Services (Cotland, New York) on a Model HT 115A -1 B heating pump for tank heater loaded with R-22 refrigerant. The tank heater included an adapter hole located between the evaporator and condenser to maintain the differential pressure between the condenser and the heater evaporator. The side of the hole was 0.128 inches (measure 30 from the hole). The system included a compressor ZR 67 Copeland brand. The list in Table 6 shows the conditions and results of the test.

Table 6 Standard average Low temperature of the SPA conditions of the test test test End of air Ambient temperatures, ° F Dry bulb 80.60 50.05 80.50 Wet bulb 71.05 44.30 71.15 Tanaue end Water temperatures, ° F Input 79.90 80.00 103.95 Output 84.60 82.85 108.25 Water flow, gpm 45.00 45.00 44.95 Electrical characteristics Voltage, volts 230 230 230 Current, amps 28.7 23.8 33.8 Input power, watts 6.250 5,130 7.430 Refrigerant circuit Temperatures, ° F Discharge in the compressor 136.5 105.0 157.0 Liquid in TXV 81.0 84.5 100.5 Vapor evaporator NA NA NA Compressor suction 55.0 31.5 57.0 Refrigerant circuit PSIG pressures Compressor discharge 266 216 352 Compressor suction 92 59 96 Barometric pressure (in. HgJ 28.98 28.98 28.98 Test conditions Heating capacity 106,310 63,520 96,950 Sample coefficient (COP) 4.98 3.62 3.82 Sample 4 An HTS 120A-1D heating pump in the tank heater was charged with CO2 refrigerant. The system included a compressor ZR 67 Copeland brand and an adapter hole was placed in line with the ducts connected to the evaporator and the condenser. No other measuring device was used. The heating pump was used to heat the water satisfactorily.

Sample 5 A cooler was loaded with R-22. The system included a nominal compressor 67,000 BTU and an adapter hole located in-line with the conduits connecting the evaporator and the condenser. No other measuring device was used. The system was used to freeze water satisfactorily (92,000 BTU's was achieved).

Claims (1)

1. CLAIMS 1. A heat exchange system of vapor compression comprises: a. a compressor, an evaporator, and a condenser; b. a refrigerant charge; c. a series of conduits in communication with said compressor, said condenser, and evaporator, wherein the conduits are adapted to transport the refrigerant through the compressor, the aforementioned condenser, and evaporator of said heat exchange system. d. Series of ducts including at least one duct connected to the condenser and evaporator and by which the refrigerant is transported from the condenser to the evaporator, at least one duct has an internal diameter; and e. An adapter securely fixes at least one conduit, by which defines an evaporator and a condenser, said adapter has an individual internal channel in communication with at least one conduit and an open orifice fixedly located within, and integral with, the internal channel of said adapter, the orifice has an internal diameter smaller than the diameter of at least one conduit creating a differential pressure between said condenser and evaporator of said system during the operation, and furthermore where the orifice has a negligible relative length to the other lengths of the series of conduits. 2. The heat exchange system with respect to claim, wherein the internal diameter of the orifice is from about 0.120 inches to 0.25 inches, and wherein the length is less than one inch. 3. The heat exchange system with respect to claim 1, wherein said system is designed to heat the air or liquid in a limited space. c 4. The heat exchange system with respect to claim 1, wherein the system is designed to cool air or liquid. in a limited space. 5. The heat exchange system with respect to claim 1, wherein the refrigerant is selected from the group of hydrochlorofluorocarbons, hydrochlorofluorocarbons, and carbon dioxide. The heat exchange system with respect to claim 5, wherein the internal diameter of the orifice is from about 0.120 to 0.25 inches, and where the length is less than one inch. 7. The heat exchange system with respect to claim 6, wherein the system is designed to heat air or liquid in a limited space. 8. The heat exchange system with respect to claim 6, wherein the system is designed to cool air or liquid in a limited space. 9. The heat exchange system with respect to the claim, wherein the refrigerant is R-22. The heat exchange system with respect to claim 9, wherein the internal diameter of such an orifice is from about 0.120 inches to 0.25 inches, wherein the length is less than one inch. 11. A pump suitable for heating swimming pools and SPAS 20 comprises: a. a compressor, an evaporator, and a condenser; b. a refrigerant charge; c. a series of ducts in communication with the compressor, condenser, evaporator, where the ducts are adapted 25 to transport refrigerant to the compressor, condenser and evaporator of the mentioned heat exchange system. d. The series of ducts including at least one duct connecting the condenser and evaporator and by which the refrigerant is taken from the condenser to the evaporator, at least one duct 30 has an internal diameter; and e. An adapter securely fixed in at least one duct, defining an evaporator and a condenser, the aforementioned adapter having an individual inner channel in communication with said duct and the fixed hole located inside and an integral with, the internal channel of said adapter, the Orifice has an internal diameter smaller than the diameter of a conduit to create differential pressure between the condenser and the evaporator of the system mentioned during the operation, and where the orifice has an insignificant length with respect to the total length of the series of conduits. 12 The heat pump with respect to claim 11, wherein said internal diameter of the orifice is from about 0.120 inches to 0.25 inches, and wherein the length is less than one inch. The heat pump with respect to claim 1, wherein the refrigerant is selected from the group of hydrofluorocarbons, hydrochlorofluorocarbons, and carbon dioxide. The heat pump with respect to claim 1, wherein the refrigerant is R-4 0A. A method of modifying a vapor compression in the heat exchange system to increase the mass fluid during the next operation of said system, this method comprises: a. by removing the existing refrigerant measuring device from the exchange system, said system comprises: i. a compressor, an evaporator and a condenser; ii. a series of conduits in communication with the compressor, condenser and evaporator where the conduits are adapted to carry the refrigerant through the compressor, condenser, and evaporator of the mentioned system; and iü. the series of conduits including at least one conduit connected to the condenser and evaporator and by which the refrigerant is carried from the condenser to the evaporator, at least one conduit has an internal diameter; and b. introducing a fixed adapter fixed at least to a conduit, by this same defining an evaporator and a condenser, having an adapter a single internal channel in communication with at least one conduit and a fixed open hole located inside, and an integral with the inner channel of said adapter, said hole has an internal diameter smaller than the diameter of a conduit to create a differential pressure between the condenser and the evaporator of said system during operation, and then where the orifice has an insignificant length with respect to the total length of the series of conduits. The method of claim 15, wherein the internal diameter of the hole is from about 0.125 inches to 0.25 inches, and wherein the length is less than one inch. 17. The method of claim 15, wherein the refrigerant is R-410A. 18. The method of claim 17, wherein the internal diameter of the hole is from about 0.125 inches to 0.25 inches, and wherein the length is less than one inch. 19. The method of claim 15, wherein the refrigerant is replaced with a carbon dioxide. 20. The method of claim 19, wherein the internal diameter of said orifice is from about 0.125 inches to 0.25 inches, and wherein the length is less than one inch. 21. The heat exchange system with respect to claim 8 includes a non-synthetic lubricating oil within the compressor. 22. The heat exchange system with respect to claim 1, wherein the refrigerant is R-22. 23. The heat exchange system with respect to claim 22, comprises a secured adapter for a conduit, said adapter has an internal channel in communication with at least one conduit, and inside the open orifice is internally located the internal channel of the adapter mentioned. 24. The heat exchange system with respect to claim 23, wherein the internal diameter of the orifice is from about 0.120 inches to 0.25 inches. 25. The heat exchange system with respect to claim 22, wherein the orifice located within a conduit. 26. The heat exchange system with respect to claim 25, wherein the internal diameter of the orifice is from about 0.120 inches to 0.25 inches. 27. A hot pump for heating swimming pools and SPA's comprise: a. a compressor, an evaporator, and a condenser b. b. A refrigerant charge; c. a series of conduits in communication with the compressor, condenser, and evaporator, wherein the conduits are adapted to transport the refrigerant through the compressor, condenser and evaporator of the heat exchange system; d. the series of conduits include at least one conduit connected to the condenser and evaporator and by which the refrigerant is taken from the condenser to the evaporator, at least one conduit has an internal diameter; and e. a fixedly open orifice located in line with at least one conduit connected to the condenser and evaporator, defining an evaporator and a condenser of the mentioned system, the orifice has an internal diameter smaller than the diameter of a mentioned conduit to create a differential pressure between the condenser and evaporator mentioned in this system during the operation. 28. A hot pump with respect to claim 27, comprises an adapter secured to said conduit, the adapter has an internal channel in communication with at least one conduit, and wherein the orifice is located within the interior channel of said adapter. A hot pump with respect to claim 28, wherein the internal diameter of the orifice is from about 0.120 inches to 0.25 inches. 30. A hot pump with respect to claim 27, wherein the orifice is located within a conduit. 31. A hot pump with respect to claim 30, wherein the internal diameter of the orifice is from about 0.120 inches to 0.25 inches. 32. A hot pump with respect to claim 27, wherein the refrigerant is selected from the group of hydrofluorocarbons, hydrochlorofluorocarbons, and carbon dioxide. 33. A hot pump with respect to claim 32, further comprising an adapter secured to a conduit, the adapter having an internal channel in communication with a conduit, and wherein the open orifice is located within the interior channel of said adapter. 34. A hot pump with respect to claim 33, wherein the internal diameter of the orifice is from about 0.120 inches to 0.25 inches. 35. A hot pump with respect to claim 33, wherein the orifice is located within the conduit. 36. A hot pump with respect to claim 35, wherein the internal diameter of the aforementioned orifice is from about 0.120 inches to 0.25 inches. 37. A hot pump with respect to claim 32, wherein the refrigerant is R-410A. 38. A hot pump with respect to claim 32, further includes a non-synthetic lubricating oil within the compressor. 39. A hot pump with respect to claim 37, further includes a mineral oil within the compressor. 40. A hot pump with respect to claim 1, wherein the refrigerant is R-22. 41. The hot pump with respect to claim 40, comprising an adapter secured to such a conduit, the adapter has an inner channel in r communication with at least one conduit, and where the orifice is located inside the inner channel of the adapter. 42. The hot pump with respect to claim 41, wherein the internal diameter of the orifice is from about 0.120 inches to 0.25 inches. 43. The hot pump with respect to claim 40, wherein the orifice is located within a conduit. 44. The pump em with respect to claim 43, wherein the inner diameter of the aforementioned orifice is approximately 0.120 inches and 0.25 inches. 45. A vapor compression method modifying the heat exchange em to increase the mass fluid of the refrigerant during the subsequent operation of said em, such method comprises: a. by removing existing refrigerant measuring devices from the heat exchange em, the em mentioned includes: i. a compressor, an evaporator, and a condenser; ii. a series of conduits in communication with the compressor, condenser, evaporator, where the conduits are adapted to carry the refrigerant by means of the compressor, condenser and evaporator of the mentioned em; and iii. the series of conduits mentioned including at least one conduit connecting the condenser and the evaporator and by which the refrigerant is taken from the condenser to the evaporator, in at least one conduit having an internal diameter; and b. introducing a hole openly in line with at least one conduit connecting the condenser to the evaporator, defining by this one side of the evaporator and one side of the condenser, the orifice has an internal diameter smaller than the diameter of at least one conduit to create a differential pressure between the condenser and the evaporator of said em during the operation. 46. The method with respect to claim 45, wherein introducing the hole comprises an adapter secured to at least one conduit, the adapter has an interior channel in communication with a conduit, and wherein the orifice is located within the inner channel of the adapter. mentioned. 47. The method with respect to claim 46, wherein the internal diameter of said orifice is from about 0.125 inches to 0.25 inches. 48. The method with respect to claim 45, wherein the hole is located within a conduit. 49. The method with respect to claim 48, wherein the internal diameter of said orifice is from about 0.125 inches to 0.25 inches. 50. The method with respect to claim 45, wherein the refrigerant is replaced with a hydrofluorocarbon. 51. The method with respect to claim 50, wherein the refrigerant is R-410A. 52. The method with respect to claim 51, wherein introducing the hole comprises an adapter secured to at least one conduit, the adapter has an inner channel in communication with a conduit, and wherein the orifice is located within the interior channel of the adapter mentioned. 53. The method with respect to claim 52, wherein the internal diameter of said orifice is from about 0.125 inches to 0.25 inches. 54. The method with respect to claim 51, wherein the hole is located within at least one conduit. 55. The method with respect to claim 54, wherein the internal diameter of the hole is from about 0.125 inches to 0.25 inches. 56. The method with respect to claim 45, wherein the refrigerant is replaced with a carbon dioxide. 57. The method with respect to claim 50, wherein the em includes a nonsynthetic lubricating oil within the compressor. 58. The method with respect to claim 57, wherein the lubricating oil is mineral oil. 59. The method with respect to claim 57, wherein said refrigerant is R-410A. 60. The method with respect to claim 58, wherein said refrigerant is R-410A. 61. The method with respect to claim 56, wherein introducing the hole comprises an adapter secured to at least one conduit, the adapter has an inner channel in communication with a conduit, and wherein the orifice is located within the interior channel of the adapter mentioned. 62. The method with respect to claim 61, wherein the internal diameter of the hole is from about 0.125 inches to 0.25 inches. 63. The method with respect to claim 56, wherein the hole is located within at least one conduit. 64. The method with respect to claim 63, wherein the internal diameter of said orifice is from about 0.125 inches to 0.25 inches.