KR20020054315A - Nonflammable mixed refrigerants (mr) for use with very low temperature throttle-cycle refrigeration systems - Google Patents

Abstract

By using R-236fa and R-125, or R-125 and R-245fa, or R-236ea, or R-134a and R-236fa instead of HCFC, the refrigerant containing HCFC is replaced with a new mixture. There is no need to change the hardware or oil composition to keep the temperature, pressure and capacity of the cooling system substantially unchanged.

Description

NONFLAMMABLE MIXED REFRIGERANTS (MR) FOR USE WITH VERY LOW TEMPERATURE THROTTLE-CYCLE REFRIGERATION SYSTEMS}

Cooling systems have existed since the early 1900s when reliable sealed cooling systems were developed. From this point on, improvements in cooling technology have proved useful in both residential and industrial environments. In particular, low temperature cooling systems now play a key role in the industry in biomedical applications, low temperature electronics, coating processing and semiconductor manufacturing applications.

Cooling to temperatures below 223 K (-50 ° C.) is particularly important for manufacturing and test applications. The present invention relates to a cooling system for cooling to temperatures between 223K and 73K (-50 ° C and -200 ° C). Temperatures in this range are referred to variously as low temperature, cryogenic temperature and cryogenic temperature. As used herein, the term "very low" or "very low temperature" means a temperature range of 223K to 73K (-50 ° C to -200 ° C). In many manufacturing processes performed under vacuum and integrated with very low temperature cooling systems, rapid heating is required for some components. This heating process is a defrost cycle. This heating raises the evaporator and connecting refrigerant lines to room temperature. These parts can then be vented through the atmosphere without moisture from the air condensing on these parts of the cooling system. The more time it takes to rebuild the entire defrost cycle, and subsequently a very low temperature, the throughput of the manufacturing system decreases. It is advantageous to increase the throughput of the vacuum process to enable rapid defrosting and the rapid resumption of cooling of the low temperature surface (evaporator) in the vacuum chamber.

There are many vacuum processes that require cooling to such very low temperatures. Its main use is to cold pump water vapor into a vacuum system. Surfaces with very low temperatures capture and fix water vapor molecules much faster than they are released. As a result, the partial pressure of water vapor in the vacuum chamber is rapidly and significantly lowered. This steam low temperature pumping process is very useful in many physical deposition processes in the vacuum coating industry for electronic storage media, optical reflectors, metallizations, semiconductor devices and the like. This process is also used to remove moisture from foods during the freeze drying process.

Another use is to block heat radiation. In this application, large panels are cooled to very low temperatures. This cooled panel blocks the radiant heat from the vacuum chamber surface and the heater. This will reduce the heat load on the surface to cool to lower temperatures than the panel. Another use is to remove heat from manufactured objects. Depending on the application, the object to be manufactured is an aluminum disk for a computer hard drive, a silicon wafer for manufacturing a semiconductor device, or a material for a flat panel display such as glass or plastic. In this case, the very low temperature provides a means to remove heat more quickly from the object, even if the final temperature of the object is higher than room temperature at the end of the process step. In addition, some applications, including hard disk drive media, silicon wafers, flat panel display materials, or other substrates, include depositing materials onto the object of manufacture. In such a case, heat is released from the object due to the deposition, so it is necessary to remove the heat released while maintaining the temperature of the object within a predetermined range. Cooling a surface, such as a platen, is a typical means of removing heat from an object of manufacture. In both of these cases, the interaction between the cooling system and the cooling object proceeds in an evaporator where the refrigerant removes heat from the cooling object at very low temperatures.

Another use at very low temperatures is the storage of biological fluids and tissues and the control of reaction rates in chemical and pharmaceutical processes.

Conventional cooling systems have used chlorinated refrigerants for some time, which have been found to be harmful to the environment and are known to contribute to ozone destruction. Thus, increasingly stringent environmental regulations have led the cooling industry to use hydrogen chloride fluorocarbons (HCFCs) instead of carbon chloride fluorocarbons (CFCs). The Montreal Convention calls for a step outside the HCFC, and European Union law has banned the use of HCFCs in cooling systems since January 1, 2001. Thus, there is a need for the development of alternative refrigerant mixtures. Fluorinated hydrocarbon (HFC) refrigerants are nonflammable, low toxicity and good candidates on the market. The use of HFCs for commercial and residential purposes is not well known. However, these applications do not require the use of typical HFC refrigerants at very low temperatures. Thus, their performance and behavior in very low temperature mixtures is unknown.

When selecting an alternative refrigerant, it is desirable to use a nonflammable non-toxic refrigerant (the acceptable exposure limit is greater than 400 ppm).

Conventional very low temperature systems used flammable components to handle oil. The oil used in a system having a very low temperature using a chlorinated refrigerant has good miscibility with high temperature boiling components that can be liquefied at room temperature when pressurized. Low temperature boiling HFC refrigerants such as R-23 are not miscible with these oils and are not easily liquefied until they reach the low temperature part of the cooling process. This immiscibility causes compressor oil to separate and freeze, resulting in system failure due to blockage of pipes, strainers, valves or throttling devices. Ethane was added to the refrigerant mixture to give miscibility at such low temperatures. Unfortunately, ethane is flammable, can limit the consumer's level of satisfaction, and can add system control requirements, facility requirements and costs. Therefore, it is desirable to remove all combustible components.

In addition, the use of toxic refrigerants may limit the consumer's satisfaction range and add additional system control requirements, equipment requirements and costs. The acceptable exposure limit (PEL) is the maximum or maximum concentration of chemical that an operator can be exposed to under OSHA regulations. In the case of mixed refrigerants, a PEL of less than 400 ppm of any component is considered toxic and threatens the health of individuals who may be exposed to the refrigerant, such as work technicians. Therefore, it is advantageous to use a refrigerant with a PEL of components greater than 400 ppm.

Another requirement is to develop a mixture of refrigerants that do not freeze from the refrigerant mixture. A “freeze” state in a cooling system is when the viscosity becomes very high to the extent that one or more refrigerant components or compressor oil do not solidify or flow. In normal operation of the cooling system, the suction pressure decreases with decreasing temperature. When a freezing condition occurs, the suction pressure drops further, creating positive feedback and further decreasing the temperature, which intensifies the freezing state. What is needed is a method of preventing freezing in mixed refrigerant cooling systems. The usable HFC refrigerant has a higher freezing point temperature than the HCFC and CFC refrigerants to be replaced. Since these refrigerants are rather new and it is not uncommon to use them at very low temperatures, no one has the information to predict the freezing behavior of a mixture of these new refrigerants.

Another problem with the use of fluorinated hydrocarbons (HFC) is that polyolesters (POE) (1998 ASHRAE Refrigeration Handbook, Chapter 7, p. 7.4) can be used with HFC refrigerants because these refrigerants are not miscible in alkylbenzene oils. , American Society of Heating, Refrigeration and Air Conditioning Engineers. Proper oil selection is essential for systems with very low temperatures, because the oil not only lubricates the compressor well, but also does not freeze from the refrigerant at very low temperatures.

Typically, changes in refrigerants in the cooling industry require changes in hardware elements such as compressors or valves. As a result, changes in the refrigerant can result in expensive equipment modifications and consequent shutdowns. What is needed is a method of using existing cooling installations with recently developed HFC mixed refrigerants that can be used with existing hardware and materials. This is further complicated by the fact that very low temperature systems must operate in several different modes. In such a system the starting process is also not simple because many refrigerants are liquid in steady state operation, but gaseous when the system is at room temperature. In addition, in the case of severe changes in operation, such as rapid defrosting, the refrigerant must be properly mixed in order to allow the system to operate without exceeding operating temperature or pressure limits. Each mixture developed in accordance with the present invention is shown in Table 1 (FIG. 1) and is indicated as mixture A, mixture B and the like. The table also shows the model numbers of commercial products developed by IGC Polycold Systems, Inc., San Rafael, CA, using these mixtures.

For example, the prior art cooling unit used a mixture containing R-123, R-22, R-23, R-170, R-14 and argon, which was replaced by mixture A (Table 1). Thus, the goal of providing equivalent cooling performance without the use of HCFCs and without the use of flammable or toxic refrigerants has been successfully achieved.

In addition, according to the present invention, other components can be added to the above-described composition, assuming that the ratio of the listed components (Table 1) is maintained at a constant ratio with respect to each other.

US Pat. No. 6,041,612, entitled "Single Circuit Cryogenic Liquefaction of Industrial Gases," assigned to Praxair Technology, Inc., discloses a method for more efficiently liquefying industrial gases, where cooling for liquefaction is defined as a multiple component. Generated by using refrigerant fluid and provided by a single flow circuit over a wide temperature range from ambient temperature to cryogenic temperatures.

U.S. Patent No. 5,702,632 entitled "Non-CFC Refrigerant Mixtures", assigned to General Signal Corporation, Stamford, Conn., Discloses a section of cooling heat exchangers useful for circulating a substantially non-CFC refrigerant mixture. This section comprises a compressor means, an auxiliary condenser, a first condenser, a second condenser, a third condenser, a supercooler and a liquid / gas separator, wherein the supercooled refrigerant fluid mixture withdrawn as a bottom component from the liquid / gas separator is Distributed and inflated by the first expansion means and the second expansion means to form a first expanded flow and a second expanded flow, respectively, and the first expanded flow is directed to the auxiliary condenser and compressor to avoid overheating of the compressor. To return.

U.S. Patent No. 5,408,848 entitled "Non-CFC auto-cascade cooling system" assigned to General Singal Corporation (Stampford, Connecticut) describes cooling useful for circulating a substantially non-CFC refrigerant mixture. A heat exchanger section is disclosed which comprises a compressor means, an auxiliary condenser, a first condenser, a second condenser, a third condenser, a supercooler and a liquid / gas separator, which is withdrawn as a bottom component from the liquid / gas separator. The supercooled refrigerant fluid mixture is dispensed and expanded by the first expansion means and the second expansion means to form a first expanded flow and a second expanded flow, respectively, and the first expanded to avoid overheating of the compressor. The flow returns to the auxiliary condenser and the compressor.

The present invention relates to the use of nonflammable, nontoxic chlorine free refrigerant mixtures used in very low temperature cooling systems.

1 is a schematic diagram of a very low temperature cooling system that can operate without modification of hardware when using the refrigerant mixture according to the present invention, employs an automatic cooling cascade process, and has defrost capability.

FIG. 2 is a partial schematic view of another cooling process and a single phase separator automatic cooling cascade for use in the cooling system of FIG. 1 in accordance with the present invention. FIG.

3 is a partial schematic view of another cooling process for use in the cooling system of FIG. 1 in accordance with the present invention.

4 is Table 1 of the refrigerant mixture composition according to the present invention.

5 is a table 2. for comparison of cooling system performance with the mixture according to the invention.

6 shows Table 3 of a refrigerant mixture which may be used to cool to 105 K without freezing of the refrigerant according to the invention.

7 shows Table 4 of a refrigerant mixture which may be used to cool down to 118 K without freezing the refrigerant according to the invention.

8 is a table 5 of refrigerant mixtures that may be used to cool to 130 K without freezing the refrigerant according to the present invention.

9 shows Table 6 of a refrigerant mixture that may be used to cool down to 140 K without freezing the refrigerant in accordance with the present invention.

10 shows Table 3 of a refrigerant mixture which may be used to cool down to 155 K without freezing the refrigerant according to the present invention.

FIG. 11 is a table 8. of the refrigerant mixtures tested to determine the limits used in Tables 3-7 without freezing of the refrigerant in accordance with the present invention.

Figure 12 is a table 9. of the temperature at which each refrigerant and refrigerant mixture can be combined with the compressor oil without freezing the refrigerant or oil in accordance with the present invention.

The present invention relates to a nonflammable, non-toxic chlorine free mixed refrigerant (MR) used in throttle cycle cooling systems with very low temperatures of various structures.

The nonflammable, nontoxic chlorine free mixed refrigerant of the present invention is intended for use in very low temperature cooling systems or processes such as mixed refrigerant systems, automatic cooling cascade cycles, Kleemenko cycles or single expansion device systems. The cooling system comprises at least one compressor and an throttling cycle of a single stage (no phase separator) or multiple stage (at least one phase separator) structure. Multistage throttling cycles, also called automatic cooling cascade cycles, are characterized by the use of a vapor-liquid phase separator of at least one refrigerant during the cooling process.

The nonflammable, nontoxic, chlorine free mixed refrigerant mixture of the present invention is useful for cooling systems with long defrost cycles.

An advantage of the present invention is that a nonflammable, non-toxic chlorine free refrigerant mixture is provided for use in very low temperature cooling systems.

Another advantage of the present invention is that a suitable compressor oil is provided for use with HFC refrigerants used in very low temperature cooling systems.

Another advantage of the present invention is that the nonflammable, non-toxic, chlorine free refrigerant mixture of the present invention can be used at temperatures below the freezing point of the hot freezing component by identifying the limitations of the hot freezing refrigerant.

Therefore, the object of the present invention can be used without changing the compressor, liquid-vapor phase separator, throttling unit and heat exchanger of the refrigerant, to provide the same cooling performance as the previous mixture containing HCFC and does not include HCFC. To develop an improved refrigerant mixture.

Accordingly, the present invention includes refrigerant mixtures and suitable compressor oils having the features, properties and relationships of the components exemplified through the mixtures described below, the scope of the invention being indicated by the appended claims.

Other objects and advantages of the present invention will become apparent from the following description.

Accordingly, the present invention includes features of the structure, combinations of elements, and arrangement of components illustrated through the structures described below, the scope of the invention being indicated by the claims that follow.

To better understand the present invention, reference is made to the following description in conjunction with the accompanying drawings.

In the first embodiment, FIG. 1 shows a cooling system 100 having a very low temperature using a mixed refrigerant according to the present invention. This cooling system 100 is a very low temperature cooling system including a compressor 102 which feeds the feed to an optional oil separator 124 which feeds the feed through the discharge line 106 to the condenser 104. . The second outlet of oil separator 124 feeds feed back to compressor suction line 122 via oil return line 130 at the node between cooling process 108 and compressor 102. Condenser 104 feeds the feed through liquid line 110 to the feed inlet of cooling process 108. The feed outlet of the cooling process 108 feeds the feed through the refrigerant supply line 114 to the inlet of the evaporator 112. In the line between the cooling process 108 and the evaporator 112 of the refrigerant supply line 114 is a flow measurement device (FMD) 116 that supplies the feed to the solenoid valve 118. The outlet of the evaporator 112 feeds the feed through the refrigerant return line 120 to the return inlet of the cooling process 108. The return outlet of the cooling process 108 closes the loop by returning the feed through the compressor suction line 122 to the compressor 102. According to another configuration, solenoid valve 118 is located between the outlet of cooling process 108 and flow measurement device 116.

The cooling system 100 further includes a defrost supply line 128 that feeds the feed to the solenoid valve 160 which transfers the refrigerant to the node between the solenoid valve 118 and the evaporator 112.

The oil separator 124 is not necessary if an oil free compressor is used. Also, in some cases, the oil concentration in the discharge line exiting the compressor is so low that no oil separator is needed. In another variant, an oil separator is installed in the defrost supply line 128.

Evaporator 112 is often integrated as part of a complete cooling system 110 as shown. According to another configuration, the evaporator 112 is provided by the purchaser or other third party and assembled at the time of installation of the complete cooling system 100. Fabrication of the evaporator 112 is often very simple and may consist of copper or stainless steel tubing. The main invention is embodied by the specifications of other parts of the cooling system 100.

Another element common to the structure of the present invention is a connecting line that allows the evaporator 112 to be located at a significant distance, typically 6 feet to 100 feet from other elements of the cooling system 100. This connecting line is not shown as a separate element.

The cooling process 108 shown as a copper cooling cascade system includes a heat exchanger 132, a phase separator 134, a heat exchanger 136, a phase separator 138, a heat exchanger 140, a phase separator 142, a heat exchanger. 144, a flow measurement device (FMD) 146, an FMD 148, and an FMD 150. The heat exchanger transfers heat from the high pressure refrigerant to the low pressure refrigerant. FMDs throttle high pressure refrigerant into low pressure refrigerant, creating a cooling effect as a result of the throttling process.

The path through which the supply refrigerant flows through the cooling process 108 is described. The feed inlet of the heat exchanger 132 receives the feed from the liquid line 110, and the feed outlet of the heat exchanger 132 supplies the feed to the feed inlet of the phase separator 134. The feed outlet of the phase separator 134 supplies the feed to the feed inlet of the heat exchanger 136, and the feed outlet of the heat exchanger 136 supplies the feed to the feed inlet of the phase separator 138. do. The feed outlet of the phase separator 138 supplies the feed to the feed inlet of the heat exchanger 140, and the feed outlet of the heat exchanger 140 supplies the feed to the feed inlet of the phase separator 142. do. The feed outlet of the phase separator 142 supplies the feed to the feed inlet of the heat exchanger 144, and the feed outlet of the heat exchanger 144 supplies the feed to the refrigerant supply line 114.

The path through which the return refrigerant flows through the cooling process 108 will be described. The return inlet of the heat exchanger 144 receives the feed from the refrigerant return line 120, and the return outlet of the heat exchanger 144 supplies the feed to the return inlet of the heat exchanger 140. The return outlet of the heat exchanger 140 supplies the feed to the return inlet of the heat exchanger 136. The return outlet of the heat exchanger 136 supplies the feed to the return inlet of the heat exchanger 132. The return outlet of the heat exchanger 132 feeds the feed to the suction line 122.

In addition, the second outlet of the phase separator 134 supplies the feed to the FMD 146 which feeds the feed into the refrigerant return path at the node between the heat exchanger 136 and the heat exchanger 140. The second outlet of the phase separator 138 supplies the feed to the FMD 148 which feeds the feed into the refrigerant return path at the node between the heat exchanger 140 and the heat exchanger 144. In a similar manner, the second outlet of the phase separator 142 supplies the feed to the FMD 150 which feeds the feed into the refrigerant return line 120 at the node between the heat exchanger 144 and the evaporator 112. .

In each case, phase separators 134, 138, and 142 serve to separate the liquid refrigerant from the vapor refrigerant. The separation efficiency varies from 40% to 100% (ie, any range of liquid refrigerant from 60% to 0% can escape the first outlet). The first outlet is preferentially steam. The second outlet is optionally liquid. The liquid from each phase separator is expanded by a throttling device, typically a capillary tube, represented by a flow measurement device (FMD). More specifically, the liquid from the phase separator 134 is supplied to the FMD 146, the liquid from the phase separator 138 is supplied to the FMD 148, and the liquid from the phase separator 143 is supplied to the FMD ( 150). Thus, the liquid is at high pressure when exiting the phase separators 134, 138, 142 and at low pressure when mixed with the returning low pressure refrigerant.

The cooling system 100 further includes a solenoid valve 152 that receives feed from a branch of the first outlet of the phase separator 134. The outlet of this solenoid valve 152 supplies feed to expansion tank 154 connected in series with second expansion tank 156. Inlet of FMD 158 is also connected to a node between solenoid valve 152 and expansion tank 154. The outlet of FMD 158 supplies the feed into the refrigerant return path at the node between heat exchanger 136 and heat exchanger 132.

The cooling system 100 can operate in one of three modes: cooling, defrosting and atmosphere. The refrigerant mixtures described above allow operation in each of these three modes. If solenoid valve 160 and solenoid valve 118 are both in the closed position, the system is in ready mode. No refrigerant flows into the evaporator. The refrigerant flows only within the cooling process 108 by an internal flow measurement device (ie, FMD 146, FMD 148, FMD 150) that delivers the high pressure refrigerant to the cold side of the cooling process 108. This allows the operation of the cooling process 108 to continue indefinitely. When a single throttle cooling process is used, the ready mode of the operating mode is only available if the means for allowing the flow to pass through the throttle is available during the ready mode for the refrigerant to flow from the high pressure side of the cooling process 108 to the low pressure side. It is possible. This is possible by means of a pair of solenoid valves for controlling the flow of the refrigerant, depending on the configuration, to the evaporator or to return to the cooling process. In other configurations, additional throttling and solenoid valves are used to enable this internal flow during ready mode.

By opening solenoid valve 118 the system is in cooling mode. In this mode of operation, solenoid valve 160 is in the closed position. The refrigerant having a very low temperature from the cooling process 108 is expanded by the FMD 116 and flows through the solenoid valve 118 to the evaporator 112 and then through the refrigerant return line 120 to the cooling process 108. To return. The cooling system 100 can operate indefinitely in this mode.

By opening solenoid valve 160, cooling system 100 enters a defrost mode. In this mode of operation, solenoid valve 118 is in the closed position. In the defrost mode, hot gas from the compressor 102 is supplied to the evaporator 112. Defrost mode removes condensation vapor (ie ice) that accumulates to prevent condensation on the surface of evaporator 112 when the vacuum chamber is vented to the atmosphere, or to eliminate the risk of workers being exposed to very low temperatures. It is typically initiated to heat the surface of 112 to room temperature. The hot refrigerant flows through the oil separator 124 via the defrost line 128 to the solenoid valve 160, is supplied to the node between the solenoid valve 118 and the evaporator 112 and flows to the evaporator 112. At the beginning of defrost, the evaporator 112 is very cold to cool the hot refrigerant gas and condense it in whole or in part. The refrigerant then returns to cooling process 108 via refrigerant return line 120. The initial temperature of the returning defrost refrigerant is a very temperature which is very similar to the temperature normally provided in the cooling mode. As the defrosting process proceeds, the temperature of the evaporator 112 rises. Finally, the temperature of the returning defrost gas is much higher than the temperature provided in the cooling mode. The result is a large amount of thermal load of the cooling process 108. This can be tolerated for a short period of time, typically 2-7 minutes, which is usually sufficient time to heat the entire surface of the evaporator 112 to room temperature. Typically a temperature sensor (not shown) is in thermal contact with the refrigerant return line 120. When the temperature of the refrigerant return line 120 reaches the desired value, the temperature sensor causes the control system (not shown) to terminate the defrost to close the solenoid valve 160 and allow the cooling system 100 to enter standby mode. do. Typically, a short waiting time, typically 5 minutes, is required after the end of defrost to allow the temperature to cool down before the cooling process 108 enters the cooling mode.

Another means of providing a defrost to enable continuous operation is disclosed in US patent application Ser. No. 09 / 870,385.

The interconnection of all elements of the cooling system 100 as described above is for the refrigerant to flow. All elements of the cooling system 100 (ie, compressor 102, condenser 104, cooling process 108, evaporator 112, FMD 116, solenoid valve 118, oil separator 124, heat exchanger) Machine 132, phase separator 134, heat exchanger 136, phase separator 138, heat exchanger 140, phase separator 142, heat exchanger 144, solenoid valve 152, expansion tank ( 154, expansion tank 156 and FMD 158 are well known in the art. However, these elements are briefly described below.

For illustration of this disclosure, the cooling process 108 of the cooling system 100 is shown in one form of an automatic cooling cascade cycle in FIG. 1. However, the cooling process 108 of the very low temperature cooling system 100 is any very low temperature cooling system using a mixed refrigerant.

More specifically, the cooling process 108 may be an automated cooling cascade process of IGC-Polycold Systems (Raphael, San Francisco, CA), or an APD system of IGC-APD Cryogenics (Allentown, PA) (ie, phase separation). Single stage low temperature chiller without functionality), Mississimer type cycles (i.e., Auto Cooling Cascade, US Patent No. 3,768,273 from Misimer), Kleemenko type (i.e. two-phase separation system), single phase separation System, or a single expansion device type of US Pat. No. 5,441,658 to Longsworth. The cooling process 108 may also be a variant of the process described in Forrest US Pat. No. 4,597,267 and Mississimer US Pat. No. 4,535,597, or without one or a stage of a phase separator, Any temperature of two or more may be a very low cooling process. Additional references to low temperature cooling and very low temperature cooling can be found in chapter 39 of the 1998 ASHRAE Refrigeration Handbook, published by the American Society of Heating, Refrigeration, and Air Conditioning Engineering. In addition to the number of phase separators used, the number of heat exchangers used and the number of internal throttling devices used may also be appropriately increased or decreased for a particular use according to various configurations.

The cooling process 108 shown in FIG. 1 is basically capable of several variations. The cooling system 100 shown in FIG. 1 is associated with a single compressor. However, it can be seen that the same compression effect can be achieved by using two compressors in parallel, and that the compression process can be divided into stages through a compressor or two stage compressor arranged in series. All possible variations are within the scope of the present disclosure. Preferred embodiments use a single compressor, because the reproducibility is improved. The use of two compressors in parallel is useful for reducing energy consumption when the load on the cooling system is light. Disadvantages of this approach are the addition of components, controls, required installation space and cost and reduced reliability. The use of two compressors in series provides a means for reducing the compression ratio of each stage of compression. This provides the advantage of reducing the maximum discharge temperature reached by the compressed refrigerant gas. However, this requires too much additional components, control and cost and degrades system reliability. Preferred embodiments use a single compressor. In the case of a single compressor, the mixed refrigerant was successfully compressed without excessive compression ratios or discharge temperatures in a single stage of compression. With compressors that are designed to perform multi-stage compression and allow cooling of the refrigerant between the compression stages, a single compressor is still used, so that the advantages of the separate compression stages are minimized while minimizing the increased complexity. Will have

The cooling system 100 shown in FIG. 1 is associated with a single evaporator. One common variant is to control defrosting and cooling separately for multiple evaporators. In such a configuration, the evaporators are placed in parallel, and valve 160 and valve 118 are used to control the flow of cold refrigerant or hot defrost gas. And a valve set and a necessary connection line, respectively. Then, for example, one or more evaporators may be in cooling, defrosting or standby mode while the other evaporators are individually in cooling, defrosting or standby mode.

The cooling system 100 further includes a solenoid valve 152 that is supplied with a feed by a branch from the first outlet of the phase separator 134. The outlet of solenoid valve 152 supplies feed to expansion tank 154 connected in series with second expansion tank 156. Inlet of FMD 158 is also connected to a node between solenoid valve 152 and expansion tank 154. The outlet of FMD 158 supplies the feed into the refrigerant return path at the node between heat exchanger 136 and heat exchanger 132.

At startup, most of the refrigerant in the cooling system 100 is typically gaseous because the entire cooling system is at room temperature. It is important to manage the refrigerant gas so that the cooling time is optimized. Selective removal of gas from the circulation in the cooling system 100 at startup is advantageous for such optimization. In addition, the rate at which gas flows back into the cooling system 100 also affects the cooling rate.

A system controller (not shown) opens solenoid valve 152 briefly, typically 10-20 seconds, at start up. The solenoid valve 152 is a Sporlan Model B6 valve (Washington, Montana), for example. As a result, at startup, the refrigerant gas exits the phase separator 134 and supplies the feed in a series combination of the expansion tank 154 and the expansion tank 156. FMD 158 enters expansion tank 154 and expansion tank 156 and regulates the flow of refrigerant gas therefrom. Two considerations in establishing a flow through the FMD 158 are described. This flow must flow so slowly that gas returning to the cooling system 100 can condense in the condenser regardless of time and operating state, so that cooling can be optimized. It is the initial formation of the liquid during this startup process that allows the cooling time to be on the order of 15 to 60 minutes. At the same time, however, the speed of the flow through the FMD 158 must be large enough to allow sufficient refrigerant to flow into the cooling system 100 to prevent the system from shutting down due to low suction pressure. The flow of gas into and out of expansion tank 154 and expansion tank 156 is manually controlled using FMD 158 as shown in FIG. 1. Alternatively, a controller can be used in conjunction with a sensor to actively control the flow.

The expansion tank device comprises at least one pressure vessel and may consist of any number of expansion tanks or any combination of expansion tanks arranged in series or in parallel.

2 shows a variant of the cooling process 108 using one or two mixed refrigerants according to the present invention. This configuration is commonly referred to as a single phase separator automatic cooling cascade process. The cooling process 200 of FIG. 2 includes a heat exchanger 202, a phase separator 204, a heat exchanger 206, a heat exchanger 208, and an FMD 210.

A path through which the supply refrigerant flows through the cooling process 200 will be described. The feed inlet of the heat exchanger 202 receives the feed from the liquid line 110, and the feed outlet of the heat exchanger 202 supplies the feed to the feed inlet of the phase separator 204. The feed outlet of the phase separator 204 supplies the feed to the feed inlet of the heat exchanger 206, and the feed outlet of the heat exchanger 206 feeds the feed to the feed inlet of the heat exchanger 208. do. The feed outlet of the heat exchanger 208 feeds the feed to the refrigerant supply line 114.

A path through which the return refrigerant flows through the cooling process 200 will be described. The return inlet of the heat exchanger 208 receives the feed from the refrigerant return line 120, and the return outlet of the heat exchanger 208 supplies the feed to the return inlet of the heat exchanger 206. The return outlet of the heat exchanger 206 feeds the feed to the return inlet of the heat exchanger 202. The return outlet of the heat exchanger 202 feeds the feed to the compressor suction line 122. In addition, liquid from the second outlet of the phase separator 204 flows into the refrigerant return path at the node between the heat exchanger 206 and the heat exchanger 208 via the FMD 210. The liquid is in a high pressure state when exiting the phase separator 204 and in a low pressure state when mixed with the returning low pressure refrigerant.

3 shows another variant of a cooling process 108 using one or two embodiments of mixed refrigerants according to the present invention. The cooling process 300 of FIG. 3 includes only one heat exchanger 302. This configuration is called a system without phase separation and is similar to that described in Longsworth's patent.

A path through which the supply refrigerant flows through the cooling process 300 will be described. The feed inlet of the heat exchanger 302 receives the feed from the liquid line 110, and the feed outlet of the heat exchanger 302 supplies the feed to the refrigerant supply line 114.

A path through which the return refrigerant flows through the cooling process 300 will be described. The return inlet of the heat exchanger 302 receives a feed from the refrigerant return line 120, and the return outlet of the heat exchanger 302 supplies the feed to the compressor suction line 122.

The cooling process 300 requires additional components for the defrost mode or the standby board. At least one FMD must be included to provide a return path that allows the high pressure refrigerant to throttle to low pressure and return to the compressor. In addition, additional components, such as solenoid valves, can be added in series with the FMD to allow flow only in standby mode.

In order for the cooling system 100 to operate continuously at start-up and to operate in standby, defrost and cooling modes, the refrigerant components described herein must be properly balanced. If there is no correct component in the correct composition range in the refrigerant mixture, a failure condition occurs that causes the control system to shut down the cooling system 100. Typical failure conditions include low suction pressures, high discharge pressures, and high discharge temperatures. Sensors for detecting each of these conditions should be included in the safety interlock of the cooling system 100 and the control system. It has been demonstrated that components of the type described herein can be used for cooling to very low temperatures and can also be used to operate the cooling system in cooling mode, defrost mode and standby mode. Examples of refrigerant charges developed to enable these three modes of operation (ie, standby mode, cooling mode and defrost mode) are shown in Table 1 (FIG. 1) as mixtures A, B and C.

These refrigerants were developed for specific manufacturing models of devices that previously used mixtures containing HCFC components. The new refrigerant mixture was used with an unmodified spherical hardware structure. The same heat exchanger, FMD, compressor, oil separator and phase separator were used without modifying the control settings of the system at all. The same level of cooling performance (heat removal) as with the mixed refrigerant containing the previous HCFCs was obtained. The new HFC mixed refrigerant allows for start-up and defrost transitions without any operational difficulties. To achieve this wide range of functionality without modifying the underlying hardware, many experiments have been required to test and evaluate.

The mixture described in FIG. 1 was developed according to the invention for use in an automatic cooling cascade cooling process similar to that shown in FIG. 1 except for PGC-152. All compositions described in FIG. 1 are the entire mixed composition filled in each model listed.

Four different base mixtures are listed in Table 1 (FIG. 4). The compositions in the ranges listed in Table 1 are expected to be applicable to many different cooling cycles as described above. Mixtures A to D are examples of mixtures actually developed in an automatic cooling cascade for evaluating the present invention. Each mixture is a variant based on the specific requirements of the cooling unit for using it. The mixture was carried out in four different commercially available cooling systems with minor modifications and operating in a cooling mode, a defrost mode and a standby mode similar to the apparatus shown in FIG. 1. Variations between different systems are the result of small differences in the performance specifications for each unit. Table 2 (FIG. 5) describes the critical system operating states when the cooling system was operated alternately with the previous mixture containing HCFCs and Mixture A. As is apparent from the data, the performance between these two mixtures was about the same. Another example where mixture C is an alternative refrigerant is also included in Table 2.

Mixture B was developed for products operating in cooling mode, defrost mode and standby mode, similar to the apparatus shown in FIG. 1.

Mixture C was also developed for products operating in cooling mode, defrost mode and standby mode, similar to the apparatus shown in FIG. 1.

Mixture D was developed for use in products that perform gas cooling. PGC-152 is a modification of the apparatus shown in FIG. This PGC-152 device lacks the defrosting capability provided by components 128, 160 and 116. In addition, there is no element 142, 144 and 150 in the cooling process for this PGC-152. The main purpose of the PGC-152 is to cool the gas stream. This is achieved by having heat exchangers 132, 136 and 140 configured as three flow heat exchangers in which the gas flow flows in the countercurrent direction and is cooled by the low pressure refrigerant. This precooled gas then flows in the countercurrent direction with the evaporator refrigerant.

Table 2 lists the critical system operating states when the cooling system was operated alternately with Mixture A and the previous mixture containing HCFCs. As is apparent from the data, the performance between these two mixtures was about the same. Similar comparisons were made for mixture D.

In the absence of HCFC, the development of a refrigerant mixture that can be used to provide the same cooling performance as previous charges containing HCFC was achieved without changing the compressor, throttling device, liquid-vapor phase separator of the refrigerant and heat exchanger.

In addition to the development of alternative refrigerant mixtures for prior art systems, new mixed refrigerant systems are being developed. Thus, the appropriate composition range has been expanded in the column heading Full Range in Table 1 and in the light of this experience.

In addition, the study was conducted to evaluate the performance of a cooling system in which the refrigerant temperature is very low. The refrigerants studied were R-245fa, R-134a, E-347 and R-4112. Testing R-245fa showed similar performance as R-236fa. In addition, tests of R-134a, E-347, and R-4112 have shown that these refrigerants can also be used in cooling systems with very low temperatures. Further details are given in the sections relating to Tables 3-8.

In addition, it can be seen that the mixed refrigerant containing HCFC used R-170 (ethane) compatible with R-23. Thus, for these new mixtures, R-170 can be used instead of R-23. Of course, using such combustible components, the entire mixture will be combustible if the molar concentration of R-170 exceeds approximately 5% to 10%.

In the expanded refrigerant group according to the invention, the mixed refrigerant formulation for use in the low temperature throttle cycle cooling system consists of the components listed in Tables 3-7, with a limited range of various components to prevent freezing of the refrigerant components. It is.

Tables 3 to 7 show various ranges of compositions that operate efficiently to cool to the minimum temperatures indicated at the top of each table without any components being frozen. In each case, the described refrigerant composition is a refrigerant composition that circulates through the evaporator coil. In the case of an automatic cooling cascade system, the refrigerant composition circulating through the evaporator is different from the composition circulating through the compressor. This difference is due to the intentional separation of the refrigerant condensing at high temperatures. Those skilled in the art will appreciate that there are various ways to address the difference between the refrigerant composition in the compressor and the refrigerant composition in the evaporator. The most important criterion is that the refrigerant composition in the evaporator is within the limits described herein. Within this range, the number of branches and the performance of the composition is potentially infinite.

In Tables 3 to 7, refrigerant components R-236fa, R-245fa, R-4112 and E-347 are used differently, and the lower limit of the composition range is 0%. In a preferred embodiment, at least one of these refrigerants is used in a small proportion. When these refrigerant mixtures are used in systems without phase separation, the maximum concentration is strictly limited to prevent freezing, which is a function of the lowest evaporator temperature as described in Tables 3-7. When these refrigerants are used in a system with a phase separator, the concentration of these refrigerant components can be increased beyond the limits set forth in Tables 3 to 7, because the phase separator increases the concentration of these refrigerants in the refrigerant mixture flowing through the evaporator. Because it will remain within the limits listed in Tables 3-7. It is desirable to maximize the concentration of these refrigerant components because more liquid will form in the condenser and remove higher levels of heat. This improves the overall efficiency of the cooling system. If these refrigerant components are removed from the cooling system, the efficiency of the system and the ability to remove heat from the evaporator will be greatly reduced. For example, removing these refrigerant components from the refrigerant mixture can reduce the heat removed in the condenser by up to 70%. This limits the total amount of heat the system can remove, thus greatly reducing the amount of heat removed by the evaporator. In addition, without these refrigerant components, there is a problem in starting the system, and excessively high pressure is generated in the defrosting process or the like.

Also, considering the use of R-236fa, R-245fa, R-4112, and E-347, R-236fa and R-245fa are HFC refrigerants while R-4112 and E-347 are not. HFC refrigerants are preferred because of their compatibility with POE type oils. R-4112 is carbon fluoride and is relatively incompatible with POE oils, causing global warming. E-347 is an ether refrigerant. It is not easily miscible with POE oil and is very unlikely to cause global warming. When using compressors lubricated with POE type oil, some use of R-236fa or R-245fa is recommended for the smooth return of oil to the compressor and for the management of oil / refrigerant in the compressor. When E-247 or R-4112 is used with an oil-lubricated compressor, special evaluation is required to ensure that the oil is properly returned to the compressor and that the internal compressor part is properly lubricated, as in normal practice.

Table 8 lists the sample mixed refrigerant formulation (mol%) and the associated freezing temperature (T _FR ) (experimental data), where T _MIN is the minimum temperature reached without freezing. The data was obtained through testing in a very low temperature system of a single throttle as described in Longsworth's patent described above. This data is the basis of Tables 3-7.

In the related invention disclosed in US Provisional Application No. 60 / 214,565, a compressor suction line is provided to prevent freezing of refrigerant components by serving to maintain suction pressure for at least the minimum cooling process so that the suction pressure of the system does not drop too low. An evaporator pressure regulator installed at 122 is used. The lower the suction pressure, the lower the temperature. When a freezing condition occurs, the suction pressure is lowered, resulting in positive feedback and further decreasing the temperature, which tends to deepen the freezing state. Such valves were used with mixtures B and C of Table 1 to prevent freezing.

Except for E-347 and R-4112, all the refrigerants listed are listed in accordance with American Society of Heating and Refrigeration and Air Conditioning Engineering (ASHRAE) Standard No. 34.

E-347 is known as 1- (methoxy) -1,1,2,2,3,3,3-heptafluoropropane (also CH3-CF2-CF2-CF3), 3M product reference Hydrofluoroether 301. At this time, the acceptable exposure limit (PEL) has not yet been established for this compound. Therefore, it is not known if it meets the nontoxic refrigerant criteria (PEL> 400 ppm). If the PEL of this compound is found to be less than 400 ppm, the entire PEL can be diluted with other ingredients to produce a refrigerant mixture where it is considered nontoxic.

R-4112 is known as dodecafluoropentane (also CF3CF2CF2CF2CF3).

A third embodiment of the present invention is required for a cooling system based on an oil lubricated compressor that operates with one of the incombustible mixed refrigerant formulations of Tables 3-8 at temperatures below 200K. Therefore, oils must be added to the mixed refrigerant formulation according to the invention. In addition, the oil should ensure long term operation of the compressor and avoid freezing from refrigerant contaminated with oil.

Compressors designed to operate with mixed refrigerants formulated with HFC components must use polyolester (POE) or polyalkylene glycol (PAG) type oils to ensure long term operation. The typical pour point temperature of this oil is higher than 220K (-53 ° C). Also in this temperature range this type of oil is miscible with pure refrigerants and mixed refrigerants formulated with HFCs. For example, POE oil Solest LT-32 has a pour point temperature of 223K and is completely miscible with pure R-23. Mixed refrigerants R-404a (combination of R-125, R-143a and R-134a) and R-407c (combination of R-32, R-125 and R-134a) are also fully miscible with this oil at T> 223K. . Table 9 lists sample refrigerant formulations and associated freezing temperatures and includes pure and mixed refrigerants with residual LT-32 oil (CPI Engineering, Solest LT-32).

It has been found that small amounts of LT 32 oil can be mixed with mixed refrigerant at very low temperatures without freezing. This is shown in Table 9. This allows long-term operation of the system when equipped with an oil lubricated compressor and an appropriately sized oil separator to maintain oil concentrations below the levels listed in Table 9. Alternatively, in the case of an automatic cooling cascade system, a phase separator may be used in the cooling process to limit the concentration of oil mixed with the refrigerant having a very low temperature flowing through the coldest part of the system. The efficiency of the phase separator should be high enough so that the oil concentration does not exceed the limits listed in Table 9.

Other oils with similar properties are commercially available and are considered to be within the scope of the present invention.

Claims (42)

A refrigerant mixture which is used in a cooling system having a very low temperature and which does not contain HCFC and comprises the components described in the following table in a molar% ratio. Mole fraction (%) ingredient Mixture A Mixture B Mixture C Mixture D Full range (mol%) argon 13 24 18 8 4-36 R-14 34 26 35 24 10-55 R-23 28 22 21 32 10-50 R-125 11 11 12 11 5-20 R-236fa 14 17 14 25 7-40 A refrigerant mixture which is used in a very low temperature cooling system with low temperature (evaporator temperature) as low as 105K and does not contain HCFC and comprises the components described in the table below. Ingredient Name Range (mol%) One At least one of Ne or Helium 0.0-10.0 2 At least one of argon (Ar) or nitrogen (N2) 10.0-45.0 3 R-14 (CF4) 20.0-50.0 4 R-23 (CHF3) 10.0-30.0 5 R-125 (C2HF5) 8.0-15.0 6 R-134a 0.0-5.0 7 Other high boiling components: at least one of R-236fa, E-347, R-245fa, R-4112 0.0-3.0 A refrigerant mixture which is used in a very low temperature cooling system with low temperature (evaporator temperature) as low as 118 K, does not contain HCFC, and comprises the components described in the table below. Ingredient Name Range (mol%) One At least one of argon (Ar) or nitrogen (N2) 10.0-40.0 2 R-14 20.0-50.0 3 R-23 10.0-40.0 4 R-125 0.0-35.0 5 R-134a 0.0-10.0 6 At least one of E-347, R-4112, R-236fa, R-245fa 0.0-6.0 A refrigerant mixture which is used in a very low temperature cooling system with low temperature (evaporator temperature) as low as 130K and does not contain HCFC and comprises the components described in the table below. Ingredient Name Range (mol%) One At least one of argon (Ar) or nitrogen (N2) 2.0-40.0% 2 R-14 10.0-50.0% 3 R-23 10.0-40.0% 4 R-125 0.0-40.0% 5 R-134a 0.0-15.0% 6 At least one of R-245fa, R-236fa, or E-347, or R-4112 0.0-30.0% A refrigerant mixture which is used in a very low temperature cooling system with a low temperature (evaporator temperature) as low as 140K, does not contain HCFC and comprises the components described in the table below. Ingredient Name Range (mol%) One At least one of argon (Ar) or nitrogen (N2) 2.0-40.0% 2 R-14 10.0-50.0% 3 R-23 10.0-40.0% 4 R-125 0.0-30.0% 5 At least one of R-236fa, R-245fa, E-347, or R-4112 0.0-15.0% A refrigerant mixture, which is used in a very low temperature cooling system with a low temperature (evaporator temperature) as low as 155K, does not contain HCFC, and contains the components described in the following table. Ingredient Name Range (mol%) One At least one of Ne or Helium 0.0-40.0% 2 R-14 5.0-50.0% 3 R-23 5.0-40.0% 4 R-125 0.0-40.0% 5 R-134a 0.0-30.0% 6 At least one of R-236fa or R-245fa 0.0-30.0% 7 At least one of E-347 or R-4112 0.0-20.0% The refrigerant mixture of claim 1, further comprising at least one additional component in each mixture, wherein the ratio of the components to each other remains the same after addition of the additional component. The refrigerant mixture of claim 2, further comprising at least one additional component in each mixture, wherein the ratio of the components to each other remains the same after addition of the additional component. 4. The refrigerant mixture of claim 3, further comprising at least one additional component in each mixture, wherein the ratio of the components to each other remains the same after addition of the additional component. 5. The refrigerant mixture of claim 4, further comprising at least one additional component in each mixture, wherein the ratio of the components to each other remains the same after addition of the additional component. 6. The refrigerant mixture of claim 5, further comprising at least one additional component in each mixture, wherein the ratio of the components to each other remains the same after addition of the additional component. 7. The refrigerant mixture of claim 6, further comprising at least one additional component in each mixture, wherein the ratio of the components to each other remains the same after addition of the additional component. The refrigerant mixture of claim 1, wherein the cooling system is a compressor cycle in one of an automatic cooling cascade with liquid / vapor phase separator, a throttle cooling system, and a Klimenco-type system. 3. The refrigerant mixture of claim 2, wherein the cooling system is a compressor cycle in one of an automatic cooling cascade with liquid / vapor phase separator, a throttle cooling system, and a Klimenco-type system. 4. The refrigerant mixture of claim 3, wherein the cooling system is a compressor cycle in one of an automatic cooling cascade with liquid / vapor phase separator, a throttle cooling system, and a Klimenco-type system. 5. The refrigerant mixture of claim 4, wherein the cooling system is a compressor cycle in one of an automatic cooling cascade with liquid / vapor phase separator, a throttle cooling system, and a Klimenco-type system. 6. The refrigerant mixture of claim 5, wherein the cooling system is a compressor cycle in one of an automatic cooling cascade with liquid / vapor phase separator, a throttle cooling system, and a Klimenco-type system. 7. The refrigerant mixture of claim 6, wherein the cooling system is a compressor cycle in one of an automatic cooling cascade with liquid / vapor phase separator, a throttle cooling system, and a Klimenco-type system. The refrigerant mixture of claim 1, wherein the cooling system alternates the low temperature refrigerant or the high temperature refrigerant to the evaporator. 3. The refrigerant mixture of claim 2, wherein the cooling system alternates the low temperature refrigerant or the high temperature refrigerant to the evaporator. 4. The refrigerant mixture of claim 3, wherein the cooling system alternates the low temperature refrigerant or the high temperature refrigerant to the evaporator. 5. The refrigerant mixture of claim 4, wherein the cooling system alternates the low temperature refrigerant or the high temperature refrigerant to the evaporator. 6. The refrigerant mixture of claim 5, wherein the cooling system alternates the low temperature refrigerant or the high temperature refrigerant to the evaporator. 7. The refrigerant mixture of claim 6, wherein the cooling system alternates the low temperature refrigerant or the high temperature refrigerant to the evaporator. The refrigerant mixture according to claim 1, wherein the refrigerant mixture does not contain HCF operating in the cooling system as a substitute for providing the cooling system with substantially the same thermodynamic performance as a conventional component mixture containing more than 0 mol% HCF. 3. The refrigerant mixture according to claim 2, wherein the refrigerant mixture does not contain HCF operating in the cooling system as a substitute for providing the cooling system with substantially the same thermodynamic performance as the conventional component mixture containing more than 0 mol% HCF. The refrigerant mixture according to claim 1, wherein the refrigerant mixture does not contain HCF operating in the cooling system as a substitute for providing the cooling system with substantially the same thermodynamic performance as a conventional component mixture containing more than 0 mol% HCF. 5. The refrigerant mixture according to claim 4, wherein the refrigerant mixture does not contain HCF operating in the cooling system as a substitute for providing the cooling system with substantially the same thermodynamic performance as the conventional component mixture containing more than 0 mol% HCF. 6. The refrigerant mixture according to claim 5, wherein the refrigerant mixture does not contain HCF operating in the cooling system as a substitute for providing the cooling system with substantially the same thermodynamic performance as a conventional component mixture containing more than 0 mol% HCF. 7. The refrigerant mixture according to claim 6, wherein the refrigerant mixture does not contain HCF, which operates in the cooling system as a substitute for providing the cooling system with substantially the same thermodynamic performance as conventional component mixtures containing more than 0 mol%. The cooling system of claim 1, wherein the cooling system comprises an object cooled by the refrigerant mixture, the cooling object being (a) a metal element in a vacuum chamber that freezes and traps unnecessary gases such as water vapor, (b) a heat exchanger for removing heat from a second fluid stream comprising at least one of a liquid, a gas, a condensation gas and a condensation gas mixture, (c) a metal element having an internal refrigerant flow passage and cooling at least one of a silicon wafer, a glass member, a plastic member and an aluminum disk, with or without a magnetic coating, (d) a biological freezer that performs at least one of freezing and storing biological tissues At least one of the refrigerant mixture. The cooling system of claim 2, wherein the cooling system includes a target to be cooled by the refrigerant mixture, wherein the cooling target is (a) a metal element in a vacuum chamber that freezes and traps unnecessary gases such as water vapor, (b) a heat exchanger for removing heat from a second fluid stream comprising at least one of a liquid, a gas, a condensation gas and a condensation gas mixture, (c) a metal element having an internal refrigerant flow passage and cooling at least one of a silicon wafer, a glass member, a plastic member and an aluminum disk, with or without a magnetic coating, (d) a biological freezer that performs at least one of freezing and storing biological tissues At least one of the refrigerant mixture. 4. The cooling system of claim 3, wherein the cooling system comprises an object cooled by the refrigerant mixture, the cooling object being (a) a metal element in a vacuum chamber that freezes and traps unnecessary gases such as water vapor, (b) a heat exchanger for removing heat from a second fluid stream comprising at least one of a liquid, a gas, a condensation gas and a condensation gas mixture, (c) a metal element having an internal refrigerant flow passage and cooling at least one of a silicon wafer, a glass member, a plastic member and an aluminum disk, with or without a magnetic coating, (d) a biological freezer that performs at least one of freezing and storing biological tissues At least one of the refrigerant mixture. The cooling system of claim 4, wherein the cooling system comprises a cooling target by the coolant mixture, the cooling cooling target being (a) a metal element in a vacuum chamber that freezes and traps unnecessary gases such as water vapor, (b) a heat exchanger for removing heat from a second fluid stream comprising at least one of a liquid, a gas, a condensation gas and a condensation gas mixture, (c) a metal element having an internal refrigerant flow passage and cooling at least one of a silicon wafer, a glass member, a plastic member and an aluminum disk, with or without a magnetic coating, (d) a biological freezer that performs at least one of freezing and storing biological tissues At least one of the refrigerant mixture. The cooling system of claim 5, wherein the cooling system comprises a target to be cooled by the refrigerant mixture, the cooling target being (a) a metal element in a vacuum chamber that freezes and traps unnecessary gases such as water vapor, (b) a heat exchanger for removing heat from a second fluid stream comprising at least one of a liquid, a gas, a condensation gas and a condensation gas mixture, (c) a metal element having an internal refrigerant flow passage and cooling at least one of a silicon wafer, a glass member, a plastic member and an aluminum disk, with or without a magnetic coating, (d) a biological freezer that performs at least one of freezing and storing biological tissues At least one of the refrigerant mixture. The cooling system of claim 6, wherein the cooling system comprises a target to be cooled by the refrigerant mixture, the cooling target being (a) a metal element in a vacuum chamber that freezes and traps unnecessary gases such as water vapor, (b) a heat exchanger for removing heat from a second fluid stream comprising at least one of a liquid, a gas, a condensation gas and a condensation gas mixture, (c) a metal element having an internal refrigerant flow passage and cooling at least one of a silicon wafer, a glass member, a plastic member and an aluminum disk, with or without a magnetic coating, (d) a biological freezer that performs at least one of freezing and storing biological tissues At least one of the refrigerant mixture. The refrigerant mixture of claim 1, further comprising a lubricating oil in the range of approximately 1% to 10% by weight, which is one of POE type oil and PAG type oil. The refrigerant mixture of claim 2, further comprising a lubricating oil in the range of approximately 1% to 10% by weight, which is one of POE type oil and PAG type oil. The refrigerant mixture of claim 3, further comprising a lubricating oil in the range of approximately 1% to 10% by weight, which is one of POE type oil and PAG type oil. The refrigerant mixture of claim 4, further comprising a lubricating oil in the range of approximately 1% to 10% by weight, which is one of POE type oil and PAG type oil. 6. The refrigerant mixture of claim 5, further comprising a lubricating oil in the range of approximately 1% to 10% by weight, which is one of POE type oil and PAG type oil. The refrigerant mixture of claim 6, further comprising a lubricating oil in the range of approximately 1% to 10% by weight, which is one of POE type oil and PAG type oil.