MXPA97009515A - Circuit and configuration apparatus for refrigeration system - Google Patents

Abstract

The proposed refrigeration system includes an evaporator, which allows the inherent absorption of heat from the environment, a condenser that returns refrigerant to a liquid state, a compressor that sends refrigerant into the system but with the refrigerant flowing through a heat exchanger from the compressor to the receiver and flowing through that heat exchanger parallel to the flow of low pressure gas leaving the evaporator in a vertical configuration that prevents the flow of liquid from the evaporator to the compressor but maintains the constant pressures and the constant flow of refrigerant inside the heat exchanger to maximize system efficiency

Description

CIRCUIT APPARATUS AND CONFIGURATIONS FOR REFRIGERATION SYSTEMS. DESCRIPTION OF THE INVENTION: This invention refers to a conduit circuitry by which the refrigerant is carried inside a refrigeration system, specifically, the design refers to an apparatus, whose operation provides a parallel flow inside a heat exchanger in a vertical configuration to achieve greater efficiency in heat transfer, a non-traditional conduction pipe between various components of such a system, which eliminates the need for certain components, produces higher efficiency gains with reduced compressor motor failures, and reduces the potential for refrigerant exposure to the atmosphere, promoting the safety and environmental adaptability of desirable refrigerants on the other hand. Refrigeration is the cooling of a space or its content to a value lower than that of the environment. Until the advent of modern technology, natural ice was the only means of cooling. The ice acts as a coolant because the temperature of the melting ice is 0 *. Continuously absorbs heat from the hotter surroundings by cooling them until they are completely melted without heating. The demand for ice created a strong impulse in the inventors to develop artificial cooling methods.

Refrigeration takes place when the heat flows to a receiver cooler than its surroundings. In vapor compression systems, the heat sink is called an evaporator. The liquid refrigerant boils in it at a controlled temperature, absorbing heat to create the desired cooling. The heat heated from the evaporator is compressed and pumped out of the refrigerated space. When the pressure rises it is condensed and cold water or air takes away the excess heat. Then the refrigerant enters an expansion valve that causes the pressure to drop when evaporating in the evaporator, and the cycle repeats. There are two basic pressures, a low that sets the desired cooling temperature, and a high that sets a sufficiently high condensation temperature to dissipate the heat, adjusting the volumetric capacity of the compressor to adapt to the cooling needed in the evaporator, a wide margin of evaporator pressures (temperature) can be obtained. It should be noted that within all refrigeration and air conditioning systems, the superheat which is the temperature at which the refrigerant is above its saturation point at a given pressure is in the range of -13 to -11"C. The knowledge that the temperature at which evaporation occurs can be controlled by pressure and that a volatile liquid absorbs heat when evaporating, promoted the development of a circuitry that contains refrigerant to cool it around. the University of Glasgow where Williaa Cullen evaporated ethyl ether under a subatmospheric pressure to produce refrigeration in 1748. The procedure was successful, but it was not continuous and did not advance much more than laboratory status, a patent established in 1834 in London by Jacob Perkins established the first practical machine to make ice, a refrigerated with volatile liquid using a compressor in a closed cycle, the which retained the refrigerant to be reused. In 1844 John Genie developed the first successful refrigeration system using a liquid with a compression-expansion expansion process and received the US patent 8080 in 1851. The refrigeration principle was widely used during the 19th century and during the first years of the 20th century . Another type of refrigeration, refrigeration by absorption was developed by Ferdinand Carre in France by 1850. This process can only work by burning natural gas or other fuels, and was used before the use of electricity. The first machines of this type used water as a coolant and sulfuric acid as an absorbent, however in 1859 Carre switched to a water-ammonia system still in use in some applications.These examples of the prior art are simply mentioned instead of representing a discussion of the state of the art, since they do not indicate the subsequent development of the technique towards objectives of overcoming limitations. As indicated in the state of the art, previous attempts tried to reconcile limitations in the refrigeration mechanics, but only established that refrigeration could be presented and controlled at a fundamental level, the basic concepts of modern refrigeration were already established in 1860. However the problem continues to the present is more efficient systems and better refrigerants, and the modification of each one of the requirements for many new and different applications Ice making as a first aspect of the refrigeration industry, to which followed immediately the introduction of cold storage facilities, breweries and rail and ship transport. Starting at the beginning of 1900 but more quickly after 1910, air conditioning followed for comfort and industrial use. After the first world war, in 1920, the domestic refrigerator began to replace the ice box. The use of refrigeration for comfort shows no sign of diminishing and the market for its products is far from saturated when considering the world markets of the present. With the wider use of mechanical refrigeration in homes, the development of the frozen food industry became possible, this area continues to grow. As more products are developed for the frozen supply. the need for refrigeration continues to grow, the uses of industrial refrigeration are highest in food storage and distribution, the chemical industry also uses refrigeration in huge quantities such as in process control, chemical separation, petrochemical manufacturing and liquefaction of gases. A refrigeration system includes, essentially an evaporator that promotes the absorption of heat from an external medium by a cooling creating a cooling, an expansion device at the entrance to the evaporator, which reduces the pressure of the refrigerant by establishing the evaporation process, a condenser which allows the refrigerant to return to the liquid state so that it can be used to absorb heat and a compressor to pressurize the gas, and make it circulate. The system works by absorbing heat from the area to be cooled, and expelling heat to the outside, the media is selected from materials specially adapted for their molecular efficiencies under controlled conditions. With the increased efficiency of certain refrigerants it has become difficult to meet the ecological requirements using less efficient refrigerants. Materials such as ethyl alcohol and sulfur dioxide were first used, but after 1850 ammonia excelled. Although irritating and somewhat toxic it offered a great advantage and is still widely used industrially. The need for a secure compound for a compression system that was stable, incombustible, non-toxic and non-irritating became very important with the markets that were commercially and residentially expanded. Guided by Thomas Tidgley, a team of researchers discovered in 1930 that by placing chlorine and fluorine atoms in certain places in hydrocarbon compounds they hate to make suitable refrigerants. Thomas Tidgley, Albert R. Henne and Robert McNary received the US patent 1,833,847 for developing that refrigerant. These halogenated hydrocarbons were sold under the Du Pont Freon brand. Freon 12 and similar refrigerants are now known as refrigerant 12 and others as refrigerant 22. They are the most usual in the world. A fluorocarbon (an organic compound that has one or more fluorine atoms) and more than a hundred fluorocarbons can be replaced by a fluorine atom, the list of potential fluorocarbons has no end. Although certain such as the R-12 or the R-22 have high efficiency are not without limitations.

In 1988 due to the ozone layer, the Dupont company and Dow Chemical agreed with EPOA and 100 other countries to put the CFC refrigerants under the Montreal Protocol ACT. In doing so, alternative mixtures emerged in the market, including for example the SUVA brand of Du Pont, although offering a healthy compound both non-toxic and ecological, the blends have experienced an unfortunate reduction in efficiency. It is indicated that the reduced capacity of an operation of a system with a strong increase in capacity in calories as well as a decrease in energy consumption ranges from 16 to 30%. Thus the needs of the refrigeration system are met rather than accepted as a commitment in a world that continually demands a maximum work for the energy consumed. The current state of the art requires additional components that offer certain functions to keep the operation under design imperfections, this is required the inclusion of a suction accumulator that stops the refrigerant before the evaporator, to maintain the level of liquid, an exchanger of heat to have a source of heat to heat the refrigerant leaving the evaporator, a receiver to accumulate the liquid that leaves the condenser, when the demand is reduced, and a thermal expansion device, a mechanical control and another control to adjust the amount of liquid that is introduced to the evaporator. The problem of the liquid entering the compressor has a basic importance, which results in the ruin of the compressor. It is common practice in refrigeration systems to protect the compressor from the refrigerant liquid by placing a suction accumulator and / or heat exchanger in the suction line of the compressor. These devices are joined by pipe in the common form of Figure 1. Additionally there are inefficiencies in the magnitude of several components, coupled with an inconsistent demand, creates the need for a non-continuous mechanism. This mechanism maintains the maximum efficiency of a high level of liquid, in the evaporator without allowing the evaporator to flood, because if a higher level is allowed, there is the risk of hitting when liquid enters the compressor. During operation, the liquid refrigerant returning from the compressor is stored in the receiver. When liquid is needed, the thermal expansion valve opens and flows to the evaporator, through the heat exchanger which can also serve as a suction accumulator for the low pressure side of the system, and then to the evaporator. A method to combine the transfer of heat with the accumulation of liquid at low pressure before entering the compressor and put a coil inside the suction accumulator as shown in Figure 2. Inside the exchanger place the hot liquid of the condenser transfers its heat through the exchanger to the suction gas, vaporizing any remaining liquid in the suction vapor. This serves to guarantee against liquid, that has not evaporated and that now flows to the compressor. It is common in the art to use a single exchanger, an accumulator, with or without an internal coil or a combination of both devices depending on the circumstances of the passage of the liquid. These components refer to two problems one that the compressor may not accept liquid refrigerant, and thus refrigerant must be prevented from arriving in a non-gaseous state, and second that the evaporator operates more efficiently with a high level of liquid, since thus the absorption of heat is maximized. There is a conflict between the two problems, since raising the liquid level increases the risk that the liquid will reach the compressor, and vice versa. Thus the previous technique has made a continuous balancing. A distinction is made between making ice and cooling. Although the previous cooling process serves to cool air for cooling and comfort under the same principle as ice making, this last one introduces water to the evaporator which adheres to the cooling surface. Chilled water and air can be easily moved by a fan or gravity. The ice must be "harvested" by melting the cooled surface to initiate melting. This can be done by other heating means, the most common is using hot gas, or hot liquid that leaves the condenser. This is simpler since two functions can be provided at the same time. US Pat. 2, 121, 253, presents a circuit in which the refrigerant flows from the compressor to the condenser to a receiver to a heat exchange that also serves as an accumulator and then to the compressor. This was a development of a heat exchanger, whose The first component stabilized the cooling process. This is different from what is proposed because the high pressure liquid that leaves the condenser flows directly to the receiver without heat exchange. This primitive type did not have the advantage that a heat exchanger previously heated the refrigerant thus reducing the need for excessive evaporation coils, no mention was made of defrosting with hot gas. This type needed an inefficient amount of liquid in the evaporator, and the energy is spent in part in moving the refrigerant without absorbing heat.

US Patent 2, 198 258 to Money 1937 shows a circuit in which the refrigerant flows from the compressor through the condenser to a flotation mechanism through the evaporator and back to the compressor. This technique demonstrates that the need for a receiver for the smooth operation of the system was recognized, however, the receptor function is performed inside the compressor not allowing liquid accumulation before entering the evaporator. while the reception did not limit the introduction of liquid to the compressor, no control of the level of liquid in the evaporator was offered, since only the flow of refrigerant was stopped, but it could not reduce the quantity, due to its nature this system had an efficiency limited, a perennial trend in current techniques. Additionally, it included the use of a flotation mechanism that allowed an excess flow of refrigerant to the evaporator, and allowing sub-cooling of the environmental conditions to cause more condensation of the refrigerant at high pressure. The technique aimed at correcting refrigerant imperfections in US Patent 2, 472, 729 to Sideli, 1940 shows a refrigeration circuit in which the refrigerant of a compressor flows to a condenser and to an accumulator exchanger and then to the exchanger returning to the compressor. The refrigerant tube and the return were in a heat exchange relationship in front of the condenser. The tubular arrangement serves as a means of heat exchange, but also provides a minimum location to receive liquid and thus a separate receiver is not used. This tubular arrangement demonstrates that the pattern, still prevalent at present, that the liquid leaving the condenser is carried by a counterflow tube to the suction gas to establish heat exchange. This attempt also provides some heat exchange, but has the disadvantage of a very short exchange time that can not respond to variable loads. Thus, with variable loads, in the system or in the environment, the system must have a low rather than optimum efficiency to compensate for an incomplete or excessive exchange. This design also shows an early use of a capillary tube to provide an intermediate between the flow of the liquid to the evaporator. This technique differs from the proposed design because the liquid that leaves the condenser immediately enters a capillary tube that acts as an expansion device, there is no receiver to store hot liquid under high pressure, and provide a source of hot gas to defrost or harvest the ice , the nature of the capillary tube design and the large capacity of an oversized condenser but no idea of diverting hot gas directly to the evaporator for defrosting. For purposes of its ability to thaw the system, this disadvantage need an external heat source which would make it more complex but reducing efficiency, since when added heat this should be expelled from the system apart from the normal expulsion of heat absorbed by the cooling process. This technique is unable to vary the superheat level in the evaporator and must therefore allow a reduced level of liquid. US Pat. No. 2, 500, 778 to Tobey 1947, is to move the condenser from the condenser to a heat exchanger against the flow of return refrigerant from the compressor. This feature appears similar to the suction heat exchanger of the present design, but differs significantly because no retainer was provided for storing high pressure liquid refrigerant, which requires an excessive evaporator size to maintain a low level of liquid. In essence, the capacitor provides the reception function and must therefore have a large size to accommodate the condensing function with the storage function, here the lack of a receiver is inherent and there is also no provision to use hot gas to defrost. Although this technique shows that refrigeration can occur without a separate receiver, the use of the condenser to store liquid, limits the efficiency to expel the heat. The primary object of this technique seemed to be the use of control and the jump to limit the liquid inside the evaporator, and an inefficiency allowing the evaporation from the heat source that was intended. It should be noted that this technique uses a volatile refrigerant, an unacceptable risk at present. Finally use a bellows that allows a pressure drop, bellows that serves as a Venturi vessel. U.S. Patent 2,521,040 to Casette 1945, shows the placement of the condenser downstream of the compressor, so that the refrigerant from the compressor goes to a heat exchanger against the refrigerant of the evaporator before flowing to the receiver. Although this feature may appear similar to the current heat exchanger, it differs because the compressor discharge gas, instead of the condenser liquid, is brought into direct contact with the suction line. Unlike the proposed technique, this excessively heats the suction gas, causing the capacity of the compressor to be used to recirculate heat into the system instead of expelling it into the environment. This premature technique limits the condition of subsequent heat absorption. Additionally, it does not provide the supply of hot gas for defrosting. He needed a minimum amount of liquid level in the evaporator to prevent the hit and thus has a low efficiency. U.S. Patent 2, 549, 747 discloses the use of water in the heat exchanger as well as refrigerant-to-refrigerant heat exchanger within the evaporator. This technique shows that the conventional arrangement in which the liquid leaving the receiver feeds through a suction heat exchanger driving liquid against the suction gas. The gas leaving the compressor is condensed and stored in a condenser-receiver combination, requiring an inefficient condenser size to fulfill the additional function. An arrangement like the one proposed, to move the receiver downstream from the place of heat exchange, with the benefit of keeping the heat exchange constant regardless of the demand in the evaporator, is not possible when the capacitor and receiver are combined in a single unit. It also has the disadvantage that there are risks of varying water temperatures that affect the rate of superheating. Additionally, the use of a condenser as a receiver allows sub-cooling when the ambient temperature drops (winter). U.S. Patent 2, 637, 983 shows the separation of part of the refrigerant conduit downstream of the compressor through a heat exchanger against part of the return duct from the evaporator. This technique differs from the present because most of the liquid with high pressure flows directly from the condenser to the receiver, with no provision for exchanging heat between the liquid leaving the condenser and the suction line. The hot gas for defrosting is taken directly from the compressor discharge, instead of the receiver as in the proposed system. This technique suffers from the disadvantage of the common use of an oversized heat exchanger, while the system is operating at less than the maximum, introducing the heat exchanger in the system in another way. This technique also suffers from attempts to mix hot gas and condensed liquid to perform moderation with varying pressure and temperature combinations. US Patent 2, 691, 276, shows the current portion of the refrigerant conduit downstream of the condenser through a heat exchanger against part of the refrigerant conduit from the evaporator to the compressor. This technique differs from the one presented because there is no receiver, and the supply of hot gas to defrost is not prevented. It also has as a disadvantage the use of non condensed hot coolant which offers less heat expelling. In order to compensate this and the risk of blows to the compressor, a low level of liquid is needed in the evaporator and thus inherently less efficiency. This invention also allows by means of a throttling function, to limit the flow of liquid to the evaporator, a method that reduces heat exchange. The US patent to Whitsel 1955 is similar to 2,691,276 where the condenser refrigerant and the return refrigerant are in heat exchange. Although this seems similar to what is proposed here, there is no receiver and there is no provision for supplying hot gas for defrosting, since a capillary system is used immediately at the outlet of the condenser, a receiver can not be placed in the system. Additionally the essence of using a capillary tube is not suitable for extreme temperatures or changing load conditions and should be planned to operate less efficiently to reduce the risk of knocking on the compressor as the evaporator leaves the liquid. This technique maintains limited efficiency to minimize cooling in the cooling section.

U.S. Patent 2, 871, 679 to Zearfoss 1955, presents for bringing an accumulator to the compressor refrigerant to the condenser before placing the heat exchanger. This evaporator return line flows against the accumulator to provide the heat exchange ratio. An attempt is made to combine the receiver function with the accumulator. This technique differs from that which occurs because the liquid leaving the condenser flows through an important length of capillary tube before being placed in exchange relation with the suction line. This reduces the temperature and pressure of the liquid creating an unacceptable level of subcooling when the ambient conditions are low but also making the liquid useless as a possible source of hot gas for thawing, there is no receiver to store a hot gas mass, no it is supposed to use hot gas to defrost. U.S. Patent 2,895, 306 to Latter 1957, presents a portion of the condenser coolant conduit in exchange against a portion of the evaporator coolant return conduit for the purpose of heating the portion of the return conduit that is exposed to the ambient air on the evaporator. dew point to prevent suction of the suction line. This technique differs from the one we present because a capillary tube is used instead of a receiver, there is no hot gas source. since a capillary placed immediately at the condenser outlet is used, a receiver can not be placed in the system. US Patent 2, 907, 181 to Nomomaque 1957, presents the conduit in a different way than in the previous patent, but preserves the use of the capillary tube placed immediately at the outlet of the condenser, preventing the placing of a receiver in the system or the Use refrigerant to defrost or collect ice. This technique should be considered inefficient in the same way as others that use a capillary tube. It can generally be said that the technique suffers from attempts to introduce components to solve an inherent inefficiency of the refrigerant but to minimize the failure of the compressor. However, compressor failures are a reality. In view of the failures, the gains have been modest, gains that are threatened as a result of the use of mixed or substituted refrigerants of inferior chemical properties, which are less efficient than CFC, HCFC refrigerants. There are several inherent disadvantages in the conventional equipment available. The most critical risk of the liquid entering the compressor, which is solved by the sacrifice of efficiency. The level of the liquid in the evaporator is kept below the flood level to prevent spillage from the evaporator. Also the function of the suction accumulator is required by adding coils to the suction accumulator as an additional heat exchange surface or by introducing a separate heat exchanger or the three things, each of which is a source of inefficiency either due to the Pressure reduction or natural resistance increase the work the compressor must do. The traditional use of a heat exchanger provides a necessary source of superheating to the liquid that is introduced to the evaporator but variants in the load or demand allow an excessive superheat that limits the amount of heat that has to be absorbed by the liquid refrigerant in the evaporator. The process of harvesting and thawing itself is a balancing of the need for heat to clean the outside of the evaporator as well as the desire to minimize the unnecessary introduction of heat. In addition, the defrosting cycle or removal of the ice, creates a period in which the system must recycle and have heat exchange, while traditionally no refrigerant is flowing to the heat exchanger. Thus, in a period where there is a great risk that the liquid reaches the compressor, the heat exchanger is not working (part of the process to clean the suction line). This risk continues even when the system returns to the normal cycle since the liquid remaining in the evaporator limits the flow of the high pressure liquid through the exchanger mounted upstream. Additionally, it should be noted that the use of mixed gas from the receiver limits the efficiency of the evaporator more without continuing the heat exchange. Two methods are used to produce a bottleneck or intermittency of the cycle, in addition to the on and off controls, each suffers its drawbacks. The capillary tubes are used to stop the liquid refrigerants which delays the system when the level of evaporation falls. The capillary tube design offers simplicity over mechanical intermittence devices because they have less efficiency and a limited capacity to handle very different loads. Also the design can not offer a supply of hot liquid for defrosting, for this you must use either a hot gas fed directly from the compressor, which gives a higher load to the evaporator and therefore a longer recovery period or use some external heat source, which is inherently inefficient. thermal expansion devices have been implemented in large systems where complexity is less important, but the prevailing planning of placing the heat exchanger directly upstream of the thermal expansion device prevents continuous expansion at a constant rate when the system is choked . Thus, the heat exchanger must be too large to change the heat during intermittent periods. This allows a super heating of the liquid refrigerant and makes it not very efficient. The cooling system of the preferred embodiment uses "IPFX" inverted parallel flow crossing pipe to have an unexpected efficiency in the cooling system, the preferred embodiment includes an evaporator, for example of the ice-making type, which freezes or cools an space or its contents at a value less than the surrounding space, a condenser, either by air or water, which removes the heat absorbed by the refrigerant inside the evaporator, a refrigerant receiver that provides a selective operation of the refrigerant evaporator either in freezing, cooling or defrosting cycle, a refrigerant thermal expansion device, a refrigerant suction heat exchanger, a refrigerant compressor to compress the vapor. The preferred embodiment of the refrigeration system of the present invention includes a compressor that provides refrigerant under pressure to a condenser wherein the heat contained within the refrigerant is expelled into the environment. A first refrigerant conduit provides the refrigerant with the flow from the high pressure side of the compressor to the condenser.

A heat exchanger, which is a vessel constructed with an internal pipe mounted vertically in a straight or coil contiguous within a vertically oriented outer vessel allows controlled heat exchange in the interface area located between the first conduit and the second conduit. refrigerant and the sixth and seventh conduit. The heat exchanger is built to allow vertical installation so that the inputs for both the high and low pressure conduits (second and seventh which are at the bottom of the heat exchanger) and the outputs for the high and low pressures ( third and eighth) are on top of the heat exchanger so that the flow of refrigerant for both low and high pressure is upward. A second conduit provides the flow of refrigerant from the condenser to the bottom inlet of the heat exchanger. A refrigerant receiver provides a container for the accumulation of hot liquid under high pressure. A third conduit provides the flow of refrigerant from the upper outlet of the exchanger to the receiver. An evaporator with an expansion valve is provided to start the evaporation of the refrigerant. A thermal expansion valve serves as a throttling means to control the flow of refrigerant to the evaporator. a fourth conduit provides the flow from the refrigerant receiver to the expansion device. A fifth conduit provides the flow from the expansion device to the high pressure side of the evaporator. A suction accumulator defines a container for accumulating low pressure gaseous refrigerant. A sixth coolant conduit provides the low pressure side of the evaporator to the suction accumulator, a seventh conduit provides flow from the accumulator to the lower inlet to the suction heat exchanger. Finally an eighth refrigerant pipe allows the flow from the upper outlet of the suction heat exchanger to the low pressure side of the compressor. In addition, a heat exchanger device is located in the coolant flow in the conduit of the seventh to the eighth heat exchange conduit, constructed to cause vertical flow and heat exchange of the inner conduit in parallel flow with the second conduit of the heat exchanger. refrigerant. The implementation of the design is an innovative route through a novel planning of a heat exchanger and a method to use it. Starting with the compressor, the refrigerant under pressure and in a gaseous form flows to a condenser where it loses heat and becomes liquid, under pressure. From the condenser the liquid refrigerant is directed through the exchanger built and oriented so that the refrigerant penetrates to the bottom and travels upwards, under pressure where it absorbs heat from the low pressure refrigerant that leaves the evaporator to approach the temperature necessary for the evaporation. The refrigerant flows from the evaporator and enters the bottom of the heat exchanger so that the low pressure refrigerant and high condensed refrigerant travel in parallel to bring the constant level of lime exchange to a maximum. From the heat exchanger, the liquid refrigerant under pressure flows to the container where it maintains its heating and pressure, so that the evaporation does not condense, in order to keep the refrigerant at a constant level of liquid inside the evaporator. The evaporator operates at a high level of liquid compared to the previous one, which results in greater efficiency, since it will be the liquid refrigerant that absorbs the heat that causes cooling. The receiver allows the evaporator to run and rest for defrosting without affecting the flow of liquid from the compressor through the heat exchanger. The liquid inside the evaporator evaporates and for this process absorbs heat from the environment. The gaseous refrigerant flows out of the evaporator into the heat exchanger where the absorbed heat can partially be rejected to superheat the cooling liquid flowing from the compressor. The gaseous refrigerant enters the bottom of the exchanger where it flows upwards transferring heat but also allowing the liquid droplets to fall backwards and collect at the bottom of the heat exchanger. Additionally, the liquid oil collected on the surface of the coolant accumulation at the bottom of the heat exchanger and the minimum liquid and the oil introduced for the lubrication are evaporated by the incoming flow of the gaseous refrigerant, causing all the refrigerant to remain gaseous. The flow from the upper part of the heat exchanger can be carried to a suction accumulator before the exchanger of or optionally the exchanger can serve as an accumulator In any embodiment the liquid can not flow upwards from the exchanger to the compressor to a minimum possibility of compressor failure. Although the principle of refrigeration is straight, the evolution of the previous techniques show that the nature of inefficiencies and difficulties within the principle of refrigeration and now with the application of modern refrigerants. Therefore, the main objectives of the present invention are the development of a system that maximizes the absorption of heat for a given energy expenditure, and that minimizes the risk of introducing liquid into the compressor, which causes its failure and that allows refrigerant leakage (safety). the previous techniques reflect attempts at balance and commitment of these two objectives. With the understanding of the risk of compressor failure due to the liquid, previous techniques have reduced efficiency as a saving weapon. Given the potential for the liquid that escapes from the evaporator, the attempts have reduced the level of liquid in the evaporator and practiced the strangulation or intermittency that maintains that level reduced. This attempt fails in the modern era of limited energy resources. The advantages of the proposed design include the capacity for maximum efficiency when using novel planning to avoid compressor failure.

It is the proposed configuration which for the first v 2 provides a reliable method to prevent the flow of the liquid to the compressor. This planning reaches the object even though the flow through the evaporator has been reduced either due to throttling or defrost cycling since the liquid recedes into the receiver but the high pressure liquid continues to flow to the upstream heat exchanger. A particular object during defrosting or ice removal is the use of a heated refrigerator within the system without subcooling caused by the gas mixture of the receiver (the gas formed in the receiver is directly vented to the hot liquid for the evaporator). An additional object of the planning is to provide a source of heat to defrost the evaporator without the need for an independent heat source. Another object of the planning is to allow efficiency under different loads and demands while keeping efficiency commitments to a minimum without sacrificing safety. Another object is to provide a simpler use and placement of the components to help both cost reduction and design flexibility. Other objects of planning will be manifested when considering the drawings and applications of the invention. BRIEF DESCRIPTION OF THE DRAWINGS In the drawings the similar parts have equal reference figures and the description is made with reference to the drawings in which it is shown: FIGURE 1 a prior art embodiment schematizing the method used in the prior art for bringing the refrigerant from the compressor 12 to the condenser 14 where the liquid is collected in the receiver 16. When the system is working, the liquid flows from the receiver 16 through the heat exchanger 18 to the evaporator 20 passing a thermal expansion valve, where the gas absorbs heat when it becomes gaseous. The gas now at low pressure flows from the evaporator 20 to the suction accumulator 22 which stops the droplets contained in the suction gas returning to the compressor. The suction gas flows from the accumulator 22 through the heat exchanger 18 where it transfers heat to the high pressure liquid. This drawing includes a throttle mechanism 24 which limits the liquid introduced into the evaporator 20.

Figure 2 presents a second heat exchange function contained within the suction accumulator 20 but is similar to Figure 1. This second heat exchanger allows a more controlled level of heat introduced to the refrigerant flow upon entering the evaporator 22 since such superheating promotes evaporation. Figure 3 shows the planning of inverted cross-flow parallel pipe where the refrigerant flows from the compressor 12 to the condenser 14 where the liquid first flows through the heat exchanger 18 before being collected in the receiver 16. The liquid heated flows from the container 16 directly to the evaporator 20 by passing a thermal expansion valve where it absorbs heat. The gas now at low pressure flows from the evaporator (El through the accumulator 22) to the heat exchanger 18 before returning to the compressor. This drawing presents the layout of the proposed design and suggests a vertical configuration of heat exchanger paths that are parallel to the opposite of previous techniques. Figure 4 introduces a second heat exchange function contained within the suction accumulator 20 in the same way that this alternate attempt (as a secondary heat exchange) is found in the present technique and is presented in Figure 2. Figure 5 presents a design in which the heat exchanger provides the function in another case made by the suction accumulator and therefore a separate suction accumulator is not necessary; Figure 6 shows an ice making unit using the planning of inverted parallel cross pipe; Figure 7 shows the upper part of the evaporator with tubes where ice is formed; Figure 8 shows the bottom of the evaporator where the ice cubes are cut into segments; Figure 9 illustrates a flow chart showing the flow of refrigerant starting at the compressor discharge for a cross-flow piping system; Figure 10 shows a bar chart for a horse compressor comparing the conventional evaporation temperature with several coolers compared to the cross-flow reversal piping system; Figure 11 shows a bar chart for a horse compressor comparing the conventional evaporation temperature with several chillers compared to an inverted flow cross pipe system. The proposed design is that the pipeline circuit that controls and directs the flow of refrigerant inside the apparatus constituting a cooling system as shown in Figures 3-5 uses inverted parallel flow "IPFX" pipe to have an efficiency unexpected in the refrigerant system. The preferred embodiment includes a compressor that sends refrigerant under pressure and a condenser where the heat contained in the refrigerant is expelled into the environment. A first refrigerant conduit provides the refrigerant flow from the high pressure outlet side of the compressor to the condenser, a heat exchanger, which is a vessel constructed with internal pipe vertically mounted in a straight or coil configuration inside an external vessel Vertically oriented allows heat transfer in an interface area located between the first to the second refrigerant conduit and the sixth to the seventh conduit. The heat exchanger is built to allow vertical installation so that the inlets for both high-pressure and low-pressure ducts (second and seventh are at the bottom of the exchanger) and outlets for high-pressure and low-pressure ducts (third and eighth respectively) are in the upper part of the heat exchanger so that the flow of refrigerant for all high or low conduits is upward. A second refrigerant conduit takes it from the condenser to the bottom inlet of the heat exchanger, a refrigerant receiver provides a container for the accumulation of hot liquid under high pressure. A third conduit provides the flow of refrigerant from the upper outlet of the heat exchanger to the refrigerant receiver. An evaporator with an expansion or vented valve at its inlet is provided to start the evaporation of the refrigerant. the valve serves as a throttling means to control the flow of refrigerant to the evaporator. a fourth refrigerant allows the flow of refrigerant from the receiver to the thermal expansion device, a fifth conduit provides the flow from the expansion device to the high pressure (inlet) side of the evaporator. A suction accumulator defines a container for accumulating the gas at low pressure. A sixth conduit allows the flow of refrigerant from the low pressure side [outlet] of the evaporator to the suction accumulator. A seventh conduit allows the flow from the suction accumulator to the bottom inlet of the suction heat exchanger. Finally an eighth conduit for refrigerant allows the flow from the upper outlet of the suction heat exchanger to the low pressure inlet of the compressor. Further, a heat exchanger device is provided for a heat exchange with the refrigerant flowing in the seventh through eighth conduit, constructed to cause vertical flow and heat exchange of the inner conduit in parallel flow with the second refrigerant conduit. An alternate modality of the refrigeration system includes a suction accumulator which contains coils so that the refrigerant flow of the fourth conduit is placed in a secondary heat exchange relationship with the refrigerant flow of the sixth conduit within the suction accumulator. This planning allows the installation of a suction accumulator with or without a coil of the pressurized liquid inside the fourth coolant duct. The preferred embodiment of the refrigerant system may also include a place of passage of a suction accumulator so that the flow of the sixth evaporator conduit flows directly into the heat exchanger allowing operation without suction accumulator because the heat exchanger installed in the Proposed way serves to perform the same function as the suction accumulator. The refrigerant system can use any type of condenser for air or evaporative water and any evaporator for freezing or cooling. The refrigerant systems can also provide the parallel flow of refrigerants from the receiver to the evaporator and from the evaporator to the compressor in a vertical embodiment for the exchange of heat in a manner that causes the accumulation of liquid present in the low pressure conduit eliminating any need to collect the liquid before or inside the compressor. Where a cooling system requires ice removal or defrosting with hot gas, the described systems may include a secondary conduit for pulling hot liquid to defrost directly from the receiver instead of using compressor hot gas without sacrificing the integrity of the proposed design. The implementation of the planning is a novel route of the circuit together with a novel design of the heat exchanger and method to use it. Starting with the compressor, the refrigerant under pressure and in gaseous state * flows to a condenser where it expels heat and condenses even liquid, still under pressure. From the condenser the liquid goes to a heat exchanger built and oriented so that the refrigerant penetrates to the bottom and travels upwards, under pressure where it absorbs heat from the low pressure refrigerant that leaves the evaporator to approach the temperature necessary for evaporation. The refrigerant flows from the evaporator and enters the bottom of the heat exchanger so that the low pressure refrigerant and high condensed refrigerant travel in parallel to bring the constant level of lime exchange to a maximum. From the heat exchanger, the liquid refrigerant under pressure flows to the container where it maintains its heating and pressure, so that the evaporation does not condense, in order to keep the refrigerant at a constant level of liquid inside the evaporator. The evaporator operates at a high level of the liquid in comparison to the previous one, which gives as a result or greater efficiency, since it will be the liquid refrigerant that absorbs the heat that causes the cooling. The receiver allows the evaporator to run and rest for defrosting without affecting the flow of liquid from the compressor through the heat exchanger. The liquid inside the evaporator evaporates and by this process absorbs heat from the environment. The gaseous refrigerant flows out of the evaporator to the heat exchanger where the absorbed heat can be partially rejected to superheat the cooling liquid flowing from the compressor. The gaseous refrigerant enters the bottom of the exchanger where it flows upwards transferring heat but also allowing the liquid droplets to fall backwards and collect at the bottom of the heat exchanger. Additionally, the liquid oil collected on the surface of the coolant accumulation at the bottom of the heat exchanger and the minimum liquid and the oil introduced for the lubrication are evaporated by the incoming flow of the gaseous refrigerant, causing all the refrigerant to remain gaseous. The flow from the top of the heat exchanger can be carried to a suction accumulator before the exchange, optionally the exchanger can serve as an accumulator. In any embodiment, the liquid can not flow upwards from the exchanger to the compressor, minimizing the possibility of compressor failure.

The use of the proposed design allows maximum levels of liquid inside the evaporator, which in turn gives a maximum of heat absorption. This is a direct function of the refrigerant available inside the evaporator. the absorption is also an indirect function of the superheating of the refrigerant since the superheating of the refrigerant reduces the capacity thereof to absorb additional heat from the environment. The efficiency can be seen as a direct function of the maximum liquid inside the evaporator and an indirect function of the superheat ported to the evaporator for a given energy expenditure by the compressors to maintain the cycle, therefore the proposed design to bring a maximum of liquid and to a minimum of superheating, it provides a refrigeration method that uses refrigerants available both for ecological purposes and for unfavorable environmental conditions. Applying the exchange ratio in a vertical arrangement of the proposed design, rather than in a traditional horizontal design, the escape of the residual liquid, ordinarily present in the vapor from the evaporator, to the compressor is eliminated. This eliminates the need for a suction accumulator which is a reduction of the necessary components. Applying the heat exchange ratio in a vertical arrangement the need for a separate suction accumulator, which is a container in the system that causes a point of pressure reduction which gives inefficiency by reducing the amount of compressed refrigerant in each movement of the compressor, for each compression cycle of the compressor there will be a reduction in density which will be a reduction in the refrigerant mass sent to the evaporator where R eventually absorbs heat as the ultimate goal of the system. Applying the heat exchange ratio in a parallel flow arrangement allows a longer and more gradual exchange than in the traditional system of counter flow of suction gas and condensed liquid. The above method requires the size of the heat exchanger medium to compensate for the less efficient arrangement, while the invention allows to reduce the size of the components. This allows greater flexibility and a reduced production cost. Applying the heat exchange ratio in a parallel flow arrangement coupled with a receiver placed downstream, a more consistent heat exchange relationship is obtained regardless of the throttle function required to vary the loads and demands of the system. This constant heat change allows better evaporator sizes since the risk of subcooling is minimal. The use of the invention allows greater density of the outlet of the suction gas from the evaporator because the reduced pressure changes are of reduced volume in the compressor duct. This in turn allows greater compression per cycle or more efficient use of the energy expended in causing that cycle. The use of the present invention, by minimizing the possibility of introducing liquid into the compressor, almost completely eliminates the risks of knocking on the compressor, a major cause of failure. In addition to an obvious reduction in maintenance costs, the reduction of compressor failures reduces the possibility of refrigerant reaching the environment. Where refrigerants have been considered hazardous to the environment, the risks of leakage failure are very important. The flow of hot liquid through the heat exchanger or suction accumulator is established immediately after the system switches from harvesting ice to defrosting, when flowing hot liquid that is 10 to 20 degrees hotter than the liquid stored in it. recipient at that time. The maximum protection of the compressor is maintained using a hot liquid source for suction cleaning or it is of the highest quality and the highest temperature available, the amount of washing gas from the receiver during the ice harvest is not affected adversely since the hot liquid is only subcooled by 1 to 5 degrees in the suction heat exchanger before it reaches the receiver.

Figures 9-11 detail a basic refrigeration system with all the necessary components to control the pressure, the temperature and prevent the components from removing liquid refrigerant from the compressor. What is shown by the scheme and the graphs is that the mixed refrigerants (134a and MP -39) are less efficient than the refrigerant 12, noting that these mixtures are the replacement for the R-l2, which is a CFC and no longer It is manufactured by the Act of the Government of the United States and the Montreal Protocol. Figures 10 and 11 are graphs (in British thermal units) that demonstrate the capacity of various energy rates in 3 of the most usual temperatures in the evaporators using 3 of the most common refrigerants. These graphs are generated by data supplied by the compressor manufacturers, Figure 10 represents a cooling system of a horse and Figure 11 represents 1 quarter horsepower in the cooling system. The foregoing detailed description gives first for clarity and understanding and no limitation is to be understood as such, since modifications are obvious to the technicians after the teaching shown above.

Claims (6)

1. R E I V I N D I CA C I O NES 1. - a refrigeration system comprising a compressor that provides refrigerant under pressure; a condenser of refrigerant where the heat [energy] contained within the refrigerant is expelled to the environment; a first coolant conduit provides for the coolant flow from the high pressure side of the compressor to the condenser; A heat exchanger, which is a vessel constructed with an internal pipe vertically mounted in a straight or coil configuration within a vertically oriented outer vessel allows for controlled heat exchange in the interface area located between the first conduit and the second conduit. refrigerant and the sixth and seventh conduit, the heat exchanger is built to allow vertical installation so that the inputs for both the high and low pressure conduits (second and seventh which are at the bottom of the heat exchanger) and the outputs for the high and low pressures (third and eighth) are on the top of the heat exchanger so that the flow of refrigerant for both low and high pressure is rising, a second pipe provides the flow of refrigerant from the condenser At the bottom inlet of the heat exchanger, a refrigerant receiver provides a container for the accumulator hot liquid ulation under high pressure, a third conduit provides the flow of refrigerant from the upper outlet of the exchanger to the receiver an evaporator with an expansion valve is provided to start the evaporation of the refrigerant, a thermal expansion valve serves as a means of throttling to control the flow of refrigerant to the evaporator a fourth conduit provides the flow from the refrigerant receiver to the expansion device or a fifth conduit provides the flow from the expansion device to the high pressure side of the evaporator a suction accumulator defines a container To accumulate low pressure gaseous refrigerant, a sixth cooling pipe provides flow, the low pressure side of the evaporator to the suction accumulator, a seventh pipe provides flow from the accumulator to the lower input to the suction heat exchanger, and an eighth pipe of refrigerant allows The flow of from the upper outlet of the suction heat exchanger to the low pressure side of the compressor; in which a heat exchanger device is located in the coolant flow in the conduit of the seventh to the eighth heat exchange conduit, constructed to cause vertical flow and heat exchange of the inner conduit in parallel flow with the second conduit of the refrigerant.
2. 2. The refrigerant system according to claim 1, characterized in that it comprises a suction accumulator which contains a coil in such a way that the refrigerant flows through the refrigerant conduit which is placed in a heat exchange relation to the flow of the refrigerant. refrigerant of the sixth conduit inside the suction accumulator, where the design allows the installation of a suction accumulator with or without a high pressure liquid coil inside the fourth refrigerant conduit.
3. 3. The refrigerant system according to claim 1, characterized in that it further comprises a step or deflection or jump of a suction accumulator so that the flow of refrigerant of the sixth cooling conduit from the evaporator flows directly to the heat exchanger, allowing the design the operation without any suction accumulator, that function is drained inside the heat exchanger installed in the proposed way.
4. 4. The refrigerant system according to claim 1, 2 and 3, characterized in that it comprises the use of any type of condenser, air, water or evaporator, and any kind of evaporator, for cooling or freezing, known, but claiming the systems that incorporate such techniques in the designs of the invention.
5. 5. The refrigerant system according to claims 1, 2 and 3, characterized in that it comprises the creation of the parallel flow of refrigerants from the receiver to the evaporator and from the evaporator to the compressor in a vertical embodiment for a heat exchange in a manner that provides the accumulation of the liquid present in the low pressure refrigerant conduit rendering useless another collection of liquid before or inside the compressor.
6. 6. The refrigerant system according to claim 1, 2 and 3, characterized in that it comprises a secondary conduit for carrying hot liquid to defrost or remove ice directly from the receiver instead of using hot gas from the discharge of the compressor without sacrificing the integrity of the proposed design to operate a refrigerant system that requires hot gas to thaw or remove ice. RES UM EN The proposed refrigeration system includes an evaporator, which allows the inherent absorption of heat from the environment, a condenser that returns refrigerant to a liquid state, a compressor that sends refrigerant into the system but with the refrigerant flowing through a heat exchanger from the compressor to the receiver and flowing through that heat exchanger parallel to the flow of low pressure gas leaving the evaporator in a vertical configuration that prevents the flow of liquid from the evaporator to the compressor but maintains the constant pressures and the constant flow of refrigerant inside the heat exchanger to maximize the efficiency of the system.