A METHOD FOR ANALYSING AND CONTROLLING A COOLING PROCESS

Abstract: A method for determining the values of such refrigeration process parameters as those by means of which the efficiency of the process can be established. The refrigerating process is carried out with the aid of a refrigerant which is circulated through a closed circuit which incorporates a compressor, a condenser, an expansion device, and an evaporator. Mutually corresponding measurement values of the refrigerant pressure and temperature upstream and downstream of the compressor and downstream of the condenser are collected in a computer, it being assumed that the pressure of the medium downstream of the condenser is the same as that downstream of the compressor. These values are utilized to determine, with the aid of information stored in the computer defining the refrigerant diagram for the refrigerant used, three key points K1, K2 and K3 on the refrigerant diagram. Process parameters required for assessing the efficiency of the refrigerating process, such as vapourization temperature, condensing temperature, overheating, undercooling and the ideal coefficient of performance of the process are then determined on the basis of these key points, while using the information defining the refrigerant diagram stored in the computer. The true or prevailing coefficient of performance of the process is then calculated as the product of the ideal coefficient of performance and a correction factor which, inter alia, compensates for losses in the process.

Description: A method for analysing and controlling a cooling process. The present invention relates to a method for determining the values of such cooling or refrigeration process para¬ meters as those by means of which the efficiency of the process can be established, said process being carried out with the aid of a refrigerant, or coolant, which is circulated through a closed circuit which incorporates a compressor, a condenser, an expansion device, and an evaporator. The term refrigeration process as used here shall be understood to include, in accordance with accepted practice, all types of compressor-driven evaporation or vapourization processes, irrespective of whether such processes are applied in heat pump systems, air conditio- ning systems, refrigerating systems or cooling systems, and irrespective of whether the apparatus used in con¬ junction therewith are stationary or mobile. The inven¬ tion is described in the following primarily with referen¬ ce to a heat pump cycle. It will be understood by all thos of normal skill inthis art, however, that when reference ' is made in the following description and claims to the coefficient of performance, heating power (heat emission) etc. analogous conditions and methods of calculation with regard to cooling efficiency factor, cooling power, etc. are to be found in the aforesaid cooling and refrigera¬ tion systems. There are many instances when it is desirable to know the working efficiency of a heat pump system. Such is the case, for instance, when installing and finely adjust¬ ing or tuning heat pump systems, when carrying out functional checks, or when servicing such systems. The measuring methods most used today utilize a combination of flow and temperature measurements. This normally involves measuring the flow rate of the heat carrier and/or the cold carrier (brine) and the temperature difference across the condenser and evaporator respec¬ tively, so as to establish thereby the heat emitted or the cold absorbed, and comparing the measuring results with the amount of electrical energy consumed. This method, however, is encumbered with several serious draw¬ backs. Among other things the accuracy to which the working efficiency of a heat pump system can be deter¬ mined by measuring the rate of flow of the heat carrier and the aforesaid temperature difference, when said difference is small, is very low. The most serious drawbacks encountered with the aforesaid method are caused by the fact that in order to measure the flow rate of the circulating medium it is necessary to install flow meters in the various circuits concerned, which is both expensive and time consuming. Thus, in order to connect-up the flow meters it is necessary first to shut down and drain the system and then to cut the pipes in a manner which will enable the flow meters to be installed. The system must then be started up and allowed to run until substantially stable temperature conditions are reached. The measuring process will normally take a full working day to complete. Because the rate of flow and temperature are not read- off simultaneously, it cannot be certain that the result obtained is accurate, since the measurement values read- off do not correspond exactly with one another. This further impairs the overall accuracy of the measuring result, since processes of this k _nd are normally rela¬ tively unstable with constantly varying parameters. It can be said in summary that although the methods applied today may be suitable ,or determining yearly average values, or corresponding values, they are not suitable for measuring the efficiency of a system when tuning the system, inspecting the system, or carrying out corresponding system procedures, since when applying the known method it is not possible to obtain continuous¬ ly information that relates to the functioning of the system. Furthermore, the known method will only provide data concerning the overall function of the system and will not provide detailed information relating to process data and the condition of the various system components. When tuning a system it is necessary, for instance, to obtain simultaneously information relating to a number of parameters that are determinative of the coefficient of performance and the heating power, or heat emission, of the system, where, for instance, a certain control procedure can result in a higher heat emission with a lower coefficient of performance, and vice versa. The main objective of the present invention is therefore to provide a method for measuring the values of refrige¬ ration process parameters which can be carried out very rapidly and at low cost and which will provide continuous documentation of essential process parameters. Another objective of the invention is to enable such a method to be applied for the purpose of automatically regulating or controlling a refrigeration process. A further objective is to provide regulating apparatus for controlling a refrigeration or cooling process on the basis of process data obtained by the inventive measuring method. In order to achieve these objectives it is important to provide a measuring method which does not require the rate of flow to be measured. The present invention is based on the realization that this can be avoided and the aforesaid objectives achieved when the information contained in the refrigerant diagram of the refrigerant used is utilized rationally. In this respect it suffices to determine at a given moment the pressure and tempera- ture simultaneously at three points in the closed refrigerant cycle, and to use these measurement values to determine three key points on the refrigerant diagram. The values of essential basic parameters of the refrige¬ ration process, such as evaporation temperature, conden¬ sation temperature, overheating, undercooling,and the ideal coefficient of process performance, can then be determined with a starting point from the aforesaid three key points on the diagram. One of the problems instrumental in the failure of earlier methods of this kind was that when utilizing information obtained from a refrigerant diagram, it was considered necessary to obtain a value of the mass flow in order to establish the true, or prevailing, coefficient of process performance. Consequently, it has been conside¬ red hitherto necessary either to measure the rate of flow, which is an excessively expensive and highly complicated procedure, or to acquire sufficient compressor data to enable the mass flow to be calculated, which has not been found possible in practice. The problem of determining the mass flow can be resolved in accordance with the invention by calculating or empiri- cally determining instead a correction factor which, inter alia, compensates for process losses, whereafter the true coefficient of performance can be calculated as the product of the ideal coefficient of performance and the aforesaid correction factor, without using the mass flow. The most important losses can be referred to thermal losses in the compressor, and practical tests have sur¬ prisingly shown that the true or prevailing coefficient of performance can be determined very accurately by using as said correction factor, with which the ideal coefficient of performance is multiplied, a calculated or empirical value of the thermal efficiency η_ of the compressor. The thermal efficiency n_ of the compressor is therewith defined as the relationship between the total energy input to the refrigerant from the compres¬ sor and the total driving energy supplied to the com- pressor, normally electrical energy. In this regard, test runs have shown that in the case of conventional systems which include hermetical or semi- hermetical compressors a satisfactorily accurate result can be obtained when using a value within the range of about 90% to about 97% as an empirical value of η . A lower value applies in the case of open compressors. Thus, the invention enables expensive and time consuming mass flow calculations to be avoided and, in the majority of cases in conjunction with the calculation of the true coefficient of performance, to be replaced with the use of a pre-determined correction factor. Subsequent to calculating the prevailing or true co- efficient of performance, the heating power generated by the process can be calculated, in accordance with the invention, as the product of the coefficient of perfor¬ mance and the drive energy supplied to the compressor. Other characteristic features of the method according to the invention are set forth in the following Claims. A refrigeration or cooling process can be automatically controlled with extreme accuracy when applying the aforedescribed method, wherewith the adjustable expansion device used to steer the process can be regulated, inter alia, on the basis of the coefficient of performance and/or heat emission calculated in accordance with the aforegoing. The inventive method can also be used as a basis for the construction of control apparatus for controlling a refrigeration process, said apparatus being characterized in that it includes means for calculating the true coefficient of performance of the process and/or the heating power generated by the process, in accordance with the aforegoing, and in that process control means are actuated thereby. The invention will now be descri¬ bed in more detail with reference to the accompanying drawings, in which Figure 1 is a principle diagram of a single stage refri- geration process; Figure 2 illustrates a refrigerant diagram of a refrige¬ rant, chosen by way of example, incorporating a refrige¬ ration process characteristic; Figure 3 is a block schematic of apparatus used when carrying out the method according to the invention. The compressor-driven refrigeration process illustrated in Figure 1 , which process is assumed here to be applied in a heat pump, represents an evaporation process which passes eyelicly through four stages. The process requires a refrigerant, or coolant, which is circulated around a closed circuit incorporating a compressor 1 , a condenser 2, an expansion valve 3, and an evaporator 4. Ammonia and chloro-fluoro-hydrocarbons (FREON) are those refri- gerants most used today. The physical properties of these refrigerants are relatively well known and are presented in the literature in both diagram form and in the form of mathematical for uli. Since it is normally the energy differences which are of interest, the refri- gerants are most often presented in so-called _i log £ diagrams, where _i stands for enthalpy and £ stands for. pressure. These diagrams are.-designated refrigerant diagrams, and an example of one such diagram is given in Figure 2. The process illustrated in Figure 1 can be divided into the following four stages: 1 ) Refrigerant in gas phase and at low pressure is drawn by suction into the compressor 1 and is compressed therein. Gas under high pressure has a high boiling point. 2) The gaseous refrigerant of high pressure flows into the condenser 2, in which the refrigerant is cooled by a heat carrier which flows through the conduit 5 and which absorbs heat from the refrigerant. Cooling of the refrigerant continues to a temperature beneath the boiling point of the refrigerant, thereby conden- sing the vapour. 3) The condensed refrigerant flows to the expansion valve 3, in which the refrigerant is expanded so that the pressure falls. The boiling point of the refrigerant is low at this low pressure. 4) The low pressure liquid refrigerant is lead into the evaporator 4, in which the refrigerant is heated and vapourized by a cold carrier flowing in through the con- duit 6, whereafter the gaseous refrigerant is again drawn in¬ to the compressor 1 and the cycle is repeated. Thus, the principle of a heat pump system is to transfer heat from a cold carrier in the conduit 6, which may have a relatively low temperature, to a heat carrier in the conduit 5, which has a relatively high temperature. The cold carrier and heat carrier may comprise any desired medium, and are most often water or air. 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Although it is possible to calculate the thermal efficiency of the compressor, it has been found very surprisingly that a very high degree of accuracy can be reached when using an empirical value for η_ of between 90 - 95% in the case of conventional systems. This method of utilizing the thermal efficiency of the compressor erables the true coefficient of performance of the process to be calculated extremely accurately by means of the aforedescribed novel method, which has been recei- ved with great surprise by those skilled in this art. This calculation is based on the realization that all energy supplied to the compressor is utilized by the process with the exception of the thermal energy lost in the compressor. The coefficient of process performance calculated above can be utilized to determine the heating power generated • by the process in a novel and simple manner, by multi¬ plying said coefficient with the value of the electrical energy supplied to the compressor, this energy being detected by means of the data logger 7. In order to determine the condition of the compressor, which is highly significant to the performance of the heat pump, the enthalpy H7 is determined at the point K7 which represents the point of intersection between the isentrope passing through the point K1 and the pressure at the point K2. A quality factor Q„ for the compressor can then be calculated as H7 - H1 . H2 - H1 In addition to earlier mentioned basic parameters for the refrigerating process a highly representative founda¬ tion for determining the efficiency of the refrigerating process and its performance, and for optimizing the same, can be obtained by complementing with a coeffi¬ cient of performance, heating power and compressor func¬ tion, since the aforesaid values can be determined at short intervals in conjunction with tuning or testing the system. In order to provide ' a complete definition of the operat¬ ing condition of the system apparatus, the temperatures of the incoming cold carrier and the departing heat carrier can also be collected with the aid of the data logger and presented together with the aforementioned para¬ meters. As will be understood by those skilled in this art, the Carnot efficiency, mass flow, and volume flow can also be determined without the aid of flow meters. The aforedescribed method is based on the assumption that the refrigerant will actually work as anticipated in theory, and that the system will only give off energy to the surroundings via heat emitting components, in this case the condenser, and as a result of the thermal losses in the compressor. The influence of the pressure drop across the condenser and evaporator has also been assumed to be negligible. The described process also represents a single stage process without internal heat exchange. It will be understood, however, that the principles also apply in the case of multi-stage systems. In the case of more complicated systems, additional pressure and tempera¬ ture measurements can be made to the extent necessary to define the process. Thus, one important advantage afforded by the method according to the invention-: " _s that unstable processes can also be measured with a high degree of accuracy, as can also changes in the course taken by the process, and that the method enables adjustments to be made to the process as measurements arc Jaeing _taken. This enables the method to be applied when wishing to control a refrigerating process automatically, in which case the expansion device suitably includes a control mechanism optionally of conventional kind. This mechanism is regulated in accordance with the invention on the basis of the coefficient of performance and/or the heat- ing power calculated in accordance with said method, depending upon whether one is primarily interested in an optimal function of the process or in obtaining the highest possible heat emission. When applied in this way the method will thus enable the whole process to be con- trolled verv accurately, since the result of each adjust¬ ment to the system can be detected immediately and compa¬ red with stored set point values or limit values. The actual control function can be carried out in a known manner and will not be described in detail here. Thus, the principle features ofthe invention can be utiliz to provide a novel, effective and highly accurate control apparatus for use with refrigerating processes. The parti¬ cular novelty of this apparatus is that it includes a data logger and a computer for collecting and processing the measuring values simultaneously, in accordance with the aforegoing, said computer being programmed with informa¬ tion defining the refrigerant diagram for the refrigerant used. The computer calculates, in the aforedescribed man- ner, the true coefficient of performance C^. and/or the generated heating power, heat emission, which values can be used for influencing the process control means, suit¬ ably arranged in the expansion device, in a manner known per se.

Claims: CLAIMS 1. A method for determining the values of such refri¬ gerating process parameters as those by means of which the efficiency of the refrigerating process can be established, said process being carried out with the aid 5 of a refrigerant which is circulated in a closed circuit which incorporates a compressor, a condenser, an expan¬ sion device, and an evaporator, characterized in that mutually corresponding measuring values of t e pressure and temperature of the refrigerant upstream and downstream 10 of the compressor and downstream of the condenser are collected with the aid of a computer, the pressure of the medium downstream of the condenser being assumed to be equal to that downstream of the compressor; in that these values are utilized to determine three key points, T5 K1 , K2 and K3, in the refrigerant diagram of the refrige¬ rant used with the aid of information defining said refrigerant diagram stored in the computer; in that the parameters required for assessing the efficiency of the refrigerating process, such as vapourization temperature, 20 condensing temperature, overheating, undercooling and the ideal coefficient of performance of the process, are determined on the basis of said key points and with the aid of the information defining said refrigerant diagram stored in the computer; and in that the true or prevailing 25 coefficient of performance of the process is calculated as the product of the ideal coefficient of performance and a correction factor which, inter alia, compensates for losses in the process. 30 2. A method according to Claim 1, characterized in that the correction factor comprises a calculated value or an empirical value of the thermal efficiency r\- of the compressor. 35 3. A method according to Claim 2, characterized in that the empirical value of η_, in the case of conventional compressors comprises a value between 90 - 97%. CO to t o o LΠ t_π TJ 0 £ CD H

Inventors: BACKMARK HANS, BERGLOEF KLAS, SANDSTROEM BENGT, BACKMARK, HANS, BERGLOEF, KLAS, SANDSTROEM, BENGT
Applicants: ETM MAETTEKNIK AB
Application year: 1987
Main classification: F25B49
IPC codes: F25B49, G01L3, G05D23