BACKGROUND OF THE INVENTION Fig. 1 is a block diagram of a conventional refrigeration system, generally denoted at 10. The system includes a compressor 12, a condenser 14, an expansion device 16 and an evaporator 18. These components are connected together via copper tubing such as indicated at 20 to form a closed loop system through which a refrigerant such as R-12, R-22, R-134a, R-407c, R-410a, ammonia, carbon dioxide or natural gas is cycled.

The main steps in the refrigeration cycle are compression of the refrigerant by compressor 12, heat extraction from the refrigerant to the environment by condenser 14, throttling of the refrigerant in the expansion device 16, and heat absorption by the refrigerant from the space being cooled in evaporator 18. This process, sometimes referred to as a vapor-compression refrigeration cycle, is used in air conditioning systems, which cool and dehumidify air in a living space, in a moving vehicle (e. g. , automobile, airplane, train, etc. ), in refrigerators and in heat pumps.

Fig. 2 shows the temperature-entropy curve for the vapor compression refrigeration cycle illustrated in Fig. 1. The refrigerant exits evaporator 18 as a saturated vapor (Point 1), and is compressed by compressor 12 to a very high pressure. The temperature of the refrigerant also increases during compression, and it leaves the compressor as superheated vapor (Point 2).

A typical condenser comprises a single conduit formed into a serpentine-like shape with a plurality of rows of conduit lying in a spaced parallel relationship. Metal fins or

other structures which provide high heat conductivity are usually attached to the serpentine conduit to maximize the transfer of heat between the refrigerant passing through the condenser and the ambient air. As the superheated refrigerant gives up heat in the upstream portion of the condenser, the superheated vapor becomes a saturated vapor (Point 2a), and after losing further heat as it travels through the remainder of condenser 14, the refrigerant exits as saturated liquid (Point 3).

As the saturated liquid refrigerant passes through expansion device 16, its pressure is reduced, and it becomes a liquid-vapor mixture comprised of approximately 20% vapor and 80% liquid. Also, its temperature drops below the temperature of the ambient air (Point 4 in Fig. 2).

Evaporator 18 physically resembles the serpentine-shaped conduit of the condenser.

Air to be cooled is exposed to the surface of the evaporator where heat is transferred to the refrigerant. As the refrigerant absorbs heat in evaporator 18, it becomes a saturated or slightly superheated vapor at the suction pressure of the compressor and reenters the compressor thereby completing the cycle (Point 1 in Fig. 2).

Figure 3 shows the temperature-entropy curve for the vapor compression refrigeration cycle, in which the de-superheating process in the condenser is indicated explicitly. The pressure of the discharge vapor from the compressor has to be raised such that the phase-change temperature (known as the saturation temperature) at the saturation pressure can be large enough to reject heat at the condenser. This requires that the discharge vapor from the compressor is superheated as the entropy increases slightly over the compressor as shown in Fig. 2. Typically one-third of a condenser is utilized for the de- superheating process in most air-conditioning and refrigeration systems.

This is a source of significant inefficiency in conventional refrigeration systems as the condenser must be larger and more costly than needed for the heat transfer function involving the phase-change of the refrigerant. Conversely, for a condenser of a given size, if the first one-third does not need to be devoted to de-superheating, greater subcooling

could be achieved.

An additional benefit which could be achieved by performing the de-superheating step outside the condenser would be an improved energy-efficiency ratio (EER). This is defined as Qv/Wc, where Qv is the heat absorption by the evaporator of the system and Wc is the work done by the compressor. By increasing subcooling for a given size condenser, a greater quantity of liquid in the refrigerant would enter the evaporator. This would increase the cooling capacity Qv, thus the EER would also increase. Furthermore, as the condenser becomes more efficient, the condenser pressure decreases, reducing the required pressure lift across the compressor, thereby reducing the compressor work and accordingly increasing the EER.

Figure 4 illustrates a modified temperature-entropy curve showing what would happen if the de-superheating step could be performed between the compressor and the condenser. Heat would be removed from the vapor discharged from the compressor, reducing the temperature of the vapor substantially while the saturation pressure is almost unchanged. Consequently, the vapor from the compressor could enter the condenser at or close to its saturation temperature and pressure. This is illustrated in the modified temperature-entropy curve of Fig. 4 between Points 2c and 2a. Up to now, however, no suitably cost effective technique has been available to eliminate the need for de- superheating in the condenser.

Therefore, a need clearly exists for a cost-effective way to achieve de-superheating at the inlet side of the condenser. The present invention seeks to meet this need.

SUMMARY OF THE INVENTION According to the present invention, the de-superheating step is performed on the inlet side of the condenser, rather than in the condenser. To achieve this, a portion of liquid refrigerant exiting from the condenser is diverted into a bypass line from which it is re- injected into the primary refrigerant path at a location between the evaporator outlet and

compressor inlet. In the bypass line, a secondary expansion valve is used to throttle the diverted liquid refrigerant from the condenser, thus decreasing the temperature substantially below the condenser outlet temperature.

The cooled refrigerant exiting the secondary expansion valve then passes through a heat exchanger which is thermally coupled to the primary refrigerant line between the compressor outlet and the condenser inlet. The heat exchanger removes heat from the refrigerant vapor exiting from the compressor, thus reducing its temperature. As a result, the refrigerant enters the condenser at or near its saturation temperature, and no portion of the condenser needs to be devoted to de-superheating.

Because the refrigerant pressure in the bypass line at the outlet of the heat exchanger is greater than the pressure at the evaporator outlet, a pressure differential compensating device is used to couple the outlet of the bypass line to the primary refrigerant line. The pressure differential compensating device can be either a vacuum generating device or a pressure-reducing device.

According to a first aspect of the invention, there is provided a refrigeration system including refrigerant compressing means, refrigerant condensing means, expansion means and evaporation means connected together to form a closed loop system with a refrigerant circulating therein, and a bypass line connected between the outlet of the condensing means and the inlet of the compressing means, the bypass line including a secondary expansion means, heat exchanging means to remove heat from the discharge vapor from the compressor between the outlet of the compressing means and an inlet of the condensing means, and a pressure differential accommodating means for mixing two vapors at two different pressures connecting the outlets of the evaporation means and the heat exchanging means to an inlet of the compressing means.

According to a second aspect of the invention, there is provided a refrigeration system comprised of a primary refrigerant path including a compressor, a condenser, a primary expansion device, and an evaporator connected together to form a closed loop

system with a refrigerant circulating therein, and a bypass line connected between the outlet of the condenser and the inlet of the compressor, the bypass line including a heat exchanger thermally coupled to the primary refrigerant path between the compressor outlet and the condenser inlet to remove heat from the discharge vapor from the compressor, and a pressure differential accommodating device for mixing two vapors at two different pressures connecting the outlets of the evaporator and the heat exchanger to an inlet of the compressor.

Further according to the second aspect of the invention, the pressure differential accommodating means is a vacuum generating device with no moving parts such as a venturi tube, or a so-called"vortex tube"which is conventionally used to create two fluid steams of differing temperature from a single high pressure input stream. (Such a vortex generator is the subject of a copending U. S. provisional patent application entitled USE OF A VORTEX GENERATOR TO GENERATE VACUUM, Serial No. 60/356, 059filed in the names of Young Cho, Cheolho Bai, and Joong-Hyoung Lee on February 11,2002, the contents of which are hereby incorporated by reference.) Further according to the second aspect of the invention, the pressure differential accommodating means is a pressure reducing device with no moving parts such as a capillary tube, an orifice, a valve, or a porous plug. The pressure reducing device is used in the bypass line which is maintained at a higher pressure than the evaporator. The pressure reducing device reduces the high pressure at the bypass line to the evaporator pressure so that two vapors can be mixed.

According to a third aspect of the invention, there is provided a method of increasing the efficiency of a refrigeration system comprised of a primary refrigerant path including a compressor, a condenser, a primary expansion device, and an evaporator connected together to form a closed loop system with a refrigerant circulating therein, the method comprising the steps of bypassing a portion of the refrigerant exiting the condenser into a secondary refrigerant line, passing the bypassed refrigerant through a heat exchanger

thermally coupled to the primary refrigerant path between the compressor outlet and the condenser inlet to remove heat from the discharge vapor from the compressor, and passing the refrigerant exiting the heat exchanger and the refrigerant exiting the evaporator through a pressure differential accommodating device means that mixes two vapors at different pressures and feeding the refrigerant exiting the pressure differential accommodating device to an inlet of the compressor.

Providing a bypass path for performing de-superheating makes the condenser more efficient thereby reducing the condenser pressure, a phenomenon which decreases the pressure lift at compressor, and thus reduces the compressor work. Correspondingly, because de-superheating does not have to be done inside the condenser, the condenser becomes more efficient, and subcooling at the end of the condenser is increased. This increases the amount of liquid refrigerant after the throttling process through the main expansion valve. Thus, the heat absorption at the evaporator (often referred as the cooling capacity) increases.

The above-described benefits of the de-superheating bypass are achieved with diversion of 10-15% of the liquid refrigerant outflow from the condenser. At this level, reduced compressor work and increased cooling capacity are achieved. Since the EER (energy efficiency ratio) is defined as the ratio of the cooling capacity to compressor work, this increases the EER.

According to a fourth aspect of the invention, when more than 15%, for example, 30%, of the liquid refrigerant from the condenser is diverted to the bypass path, the cooling capacity is reduced due to the substantial decrease in the refrigerant mass flow rate circulating through the evaporator. By use of an adjustable valve in the bypass path, the bypass mass flow rate, and thus, the cooling capacity, can be varied according to the thermal load, whereby it is possible to operate an air conditioning or refrigeration system without frequent, highly energy-inefficient, ON-OFF operations of the compressor. This results in improved long-term seasonal energy efficiency ratio (SEER).

According to a fifth aspect of the invention, multiple evaporators can be employed, e. g. , in a zoned cooling system. Thus, several small evaporators could be provided for separate rooms, with one condenser and one compressor. When all the rooms require cooling, the system can be operated with a 10% bypass rate to provide the maximum cooling capacity and the maximum efficiency. If the thermal load decreases, as when fewer rooms need to be cooled, the bypass rate can be increased to reduce the cooling capacity without the need to cycle the compressor on and off. This is quite beneficial because the repeated ON-OFF cycling of the compressor is a very energy-inefficient process.

The concepts of this invention are applicable to conventional single-refrigerant systems, and also to mixed-refrigerant systems using a combination of refrigerants selected to provide the desired combination of thermal and flammability characteristics. Such mixed-refrigerant systems may also include regenerative features which provide higher evaporator efficiency by increasing the percentage of liquid in the refrigerant as it enters the evaporator. Regenerative mixed refrigerant systems are disclosed, for example, in our U. S.

Patents 6,250, 086 and 6,293, 108, the contents of which are hereby incorporated by reference.

It is accordingly an object of this invention to provide an apparatus and method that eliminates the need for de-superheating to take place in the condenser of a refrigeration system.

It is also an object of the invention to increase the efficiency of known refrigeration systems by providing a cost-effective way of reducing the temperature and pressure of the discharge vapor from the compressor.

It is another object of the invention to increase the cooling capacity and EER of known refrigeration systems by providing a cost-effective way of reducing the temperature and pressure of the discharge vapor from the compressor.

A related object of the invention to allow use of smaller condensers in known refrigeration systems by providing a cost-effective way of reducing the temperature and

pressure of the discharge vapor from the compressor.

An additional object of the invention is to provide a way of reducing the temperature and pressure of the discharge vapor from the compressor, which may be used in single-refrigerant systems and also in mixed-refrigerant systems, with and without regenerative features.

An additional object of the invention is to provide an improved refrigeration system in which the evaporator is connected to a substantially low pressure created by a vacuum- generating device thereby boosting the evaporator capacity.

An additional object of the invention is to provide an improved refrigeration system in which the mixing two different pressures using a vacuum generating device increases the suction pressure of the compressor, whereby the required pressure rise over the compressor is reduced, which, in turn, reduces the compressor work and increases the EER.

An additional object of the invention is to provide an improved refrigeration system in which the mixing two different pressure vapors are carried out using a vacuum generating device so that the pressure at the bypass line can be maintained at a higher pressure than the evaporator pressure.

An additional object of the invention is to provide an improved refrigeration system in which the mixing two different pressure vapors are carried out using a pressure-reducing device so that the pressure at the bypass line can be maintained at a higher pressure than the evaporator pressure.

Yet another object of the invention is to provide an improved refrigeration system in which de-superheating is performed outside the condenser in a bypass path to which refrigerant from the condenser outlet is diverted, into a bypass path, and in which the quantity of refrigerant diverted is controlled such that the cooling capacity can be adjusted to meet varying thermal requirements, whereby the system can be operated without the need for energy-inefficient repeated on and off cycling of the compressor.

BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 shows a block diagram of a conventional refrigeration system.

Figure 2 shows a temperature-entropy curve for the conventional refrigeration system of Figure 1.

Figure 3 shows a temperature-entropy curve for the refrigeration system of Figure 1, where de-superheating process is indicated.

Figure 4 shows a temperature-entropy curve for a refrigeration system in which de- superheating process is performed outside the condenser according to the present invention.

Figure 5 shows a block diagram of an embodiment of the present invention in which a heat exchanger in a bypass line removes heat from the discharge vapor from the compressor, and a pressure differential accommodating device is used to mix two vapors at two different pressures.

Figures 6A and 6B illustrate the construction of a vortex generator which may be used as a pressure differential accommodating device according to the invention.

Figure 7 illustrates the construction of a venturi tube which may be used instead of the vortex generator shown in Figures 6A and 6B.

Figure 8 shows a block diagram of an embodiment of the present invention in which a heat exchanger in a bypass line removes heat from the discharge vapor from the compressor, and a pressure-reducing device is used at the bypass line to reduce the high pressure at the bypass line to a level at the evaporator so that two vapors at two different pressures can be mixed.

Figure 9 is a block diagram showing application of the present invention to a zoned cooling system.

Figure 10 is a block diagram showing application of the present invention to a mixed-refrigerant system.

Throughout the drawings, like parts are given the same reference numerals.

DETAILED DESCRIPTION Fig. 5 illustrates in block diagram form, a first embodiment of the invention. The system of Fig. 5, generally denoted at 30, is similar to that of Fig. 1, except that a secondary bypass path 32 is coupled between the outlet of condenser 14, and the inlet of compressor 12. Bypass path 32 includes a secondary expansion device 34. a heat exchanger 36 thermally coupled between the outlet of compressor 12 and the inlet of condenser 14, and a pressure differential accommodating device 38, which mixes the refrigerant exiting the evaporator 18 and the heat exchanger 36 for return to the inlet of compressor 12. Pressure differential accommodating device 38 is needed because, as shown, the pressure at the outlet of the evaporator may be lower than the pressure at the outlet of the heat exchanger The pressure differential accommodating device 38 can be either a vacuum generating device such as a vortex generator or a venturi tube or a pressure reducing device.

The construction of a vortex generator is shown schematically in Figs. 6A and 6B.

The design of the vortex generator, generally denoted at 40, is derived from the so- called vortex tube, a known device which converts an incoming flow of compressed gas into two outlet streams-one stream hotter than and the other stream colder than the temperature of the gas supplied to the vortex tube. A vortex tube does not contain any moving parts.

Such a device is illustrated in our U. S. Patent 6,250, 086, which is hereby incorporated herein by reference.

As illustrated in Figs. 6A and 6B, vortex generator 40 is used to mix two vapors at different pressures into one stream. The present invention uses the vortex generator as a mixing means. It is comprised of a tubular body 60, with an axial inlet 52 and a tangential inlet 54 at an inlet end 62, and an outlet 58 at an opposite outlet end 64. The interior construction of tube 60 at the inlet end is such that a high-pressure gas stream entering tangential inlet 54 travels along a helical path toward the outlet 58. This produces a strong vortex flow in tube 60, and a radial pressure differential due to the centrifugal force created by the vortex flow forces the vapor radially outward and produces high pressure at the

periphery and low pressure at the axis. The low pressure allows fluid drawn in through axial inlet 52 to mix with the high-pressure helical stream and to exit with it through outlet 58.

Further information concerning vortex generator 40 may. be found in the Cho, Bai, Lee Application Serial No. 60/356,059 mentioned above.

In the system illustrated in Fig. 5, the high-pressure tangential flow is provided through tube 54 from heat exchanger 36, and the incoming stream at axial inlet 52 is provided from the outlet of evaporator 18. Using a vacuum-generating device based on the vortex generator makes it possible to combine the refrigerant exiting from evaporator 18 and the higher pressure refrigerant exiting from heat exchanger 36 without the need for a costly pump having moving parts.

Other devices which rely on geometry and fluid dynamics may also be used to generate a vacuum which permits mixing the refrigerant streams exiting from evaporator 18 and heat exchanger 36. For example, a device operating on the principle of a venturi tube may also be used. In such a device, as illustrated in Fig. 7 at 69, a high pressure fluid stream (here, the refrigerant exiting from heat exchanger 36), enters axially into an elongated tube 70 having an interior diameter 72 which decreases gradually to a point of minimum diameter 74 and thereafter increases gradually toward an outlet end 76. As the cross-sectional area decreases, the vapor stream is accelerated. According to Bernoulli's principle, the pressure decreases, and reaches a minimum at the so-called"throat corresponding to the point of minimum diameter 74 where a vacuum is created.

A radial inlet 78 is provided at the low-pressure point. This is connected to the outlet of evaporator 18 (see Fig. 5), thereby permitting mixing of the evaporator outflow with the axial stream from heat exchanger 36.

Referring again to Fig. 5, in operation, a portion of the liquid refrigerant exiting from condenser 14 is diverted into bypass path 32, for example, by a suitable valve (not shown).

The diverted refrigerant passes through secondary expansion device 34 and then through

heat exchanger 36 which performs the de-superheating function conventionally performed by the upstream portion of the condenser.

By proper selection of system parameters, in particular, the mass flow rate of refrigerant diverted to the bypass path, the refrigerant can be made to enter condenser 14 at or close to the saturation temperature, and the entire flow path through the condenser can be devoted to the phase-change operation by transfer of heat to the environment, whereby maximum condenser efficiency can be achieved. It has been found that this requires diversion of 10-15% of the liquid refrigerant outflow from the condenser to the bypass path.

More particularly, providing a bypass path for de-superheating makes the condenser more efficient thereby reducing the condenser pressure, which, in turn, decreases the pressure lift at compressor, thus reducing the compressor work. The coefficient of performance ("COP") of a refrigeration system, sometimes termed the energy-efficiency ratio (EER), is defined as QV/WCR where Qv is the heat absorption by the evaporator of the system and Wc is the work done by the compressor. As will be appreciated, a decrease in We increases the COP and the EER.

Correspondingly, because de-superheating does not have to be done inside condenser 14, the condenser becomes more efficient, and subcooling at the end of the condenser is increased. This increases the amount of liquid refrigerant after the throttling process through the main expansion valve 16. Thus, the heat absorption at evaporator 18 (often referred as the cooling capacity) increases.

Referring still to Fig. 5, by proper design of the vacuum generating device such as vortex generator 40 illustrated in Figs. 6A and 6B, or venturi tube 69 illustrated in Fig. 7, the pressure at the low pressure inlet can be made lower than the inlet pressure at main evaporator 18. As a consequence, a pressure drop may be imposed across the evaporator.

This is advantageous in that the lower evaporator outlet pressure means that the evaporator temperature differential is greater, resulting in enhanced evaporator capacity.

Of even more significance, after the mixing of the two vapor streams from heat exchanger 36 and evaporator 18, the pressure of the combined stream can have a higher pressure than the evaporator inlet pressure. This means that the suction pressure at the compressor inlet is increased, which reduces the required pressure lift across the compressor. The reduced compressor work can provide a beneficial increase in the EER.

Fig. 8 shows a system, generally denoted at 44, which is similar to system 30 shown in Fig. 5, but which uses pressure reducing device 48 to reduce the high pressure at the bypass line to a pressure level of the evaporator so that the two vapors can be mixed between the evaporator and the compressor. Pressure reducing device 48 can be any mechanism which reduces pressure via friction of sudden pressure drop such as a capillary tube, an orifice, a valve, a porous plug, or the like. A conventional Tee function 46 may be used to mix the vapor exiting evaporator 18 with that exiting pressure reducing device 48.

Fig. 9 illustrates a zoned air conditioning system embodying the principles of this invention, generally denoted at 90. This differs from system 30 illustrated in Fig. 5 in that bypass path 92 includes an adjustable control valve 94, and the evaporator 96 is formed of several parallel-connector evaporator units 98a and 98b located to serve different rooms, and respectively connected to the main expansion device 16 by ON-OFF valves 100a and 100b. System 90 is thus configured to provide two separate cooling zones, but as will be appreciated, more zones can be provided if desired.

The outlets of evaporator units 98a and 98b are at the same pressure, and are therefore connected in common to the input of pressure differential accommodating device 38.

In operation, when cooling in both zones is required, valves 100a and 100b are opened, and refrigerant flows through both evaporators 98a and 98b. Valve 94 is adjusted to divert between 10 and 15 percent of the refrigerant from condenser 14 into bypass path 92 to achieve maximum cooling and efficiency. Thus, all of the benefits of the de-

superheating bypass described in connection with Fig. 5 are also realized in system 90.

As an additional feature of system 90, however, if cooling is required, e. g. , only in the zone served by evaporator unit 98a, valve 100a is opened, valve 100b is closed, and valve 94 is adjusted to divert the refrigerant which would otherwise flow through evaporator 98b into bypass path 92, along with the refrigerant required for de-superheating.

To vary the bypass mass flow rate, valve 94 in bypass line 92 should be continuously adjustable or adjustable in steps, to provide the desired number of different flow rates. For example, 10% diversion could be provided for maximum performance, with 20%, 30%, and 40% diversion for reduced cooling capacity. Valves providing the above-described capability are commercially available and any suitable or desired valve of this type may be employed.

As previously indicated, maximum efficiency and cooling capacity are achieved by diversion of 10-15% of the refrigerant mass flow to bypass path 92. As the amount of refrigerant diverted is increased beyond 15%, for example, up to 30% or more, the cooling capacity is reduced due to the substantial decrease in the refrigerant mass flow rate circulating through evaporator 96. Thus, by diverting the refrigerant not needed in the idle evaporator, the cooling capacity can be made to vary according to the thermal load, without the need for repeated on-off cycling of the compressor or resort to costly variable speed compressors.

This is particularly advantageous in that cycling the compressor on and off consumes a large quantity of energy. Eliminating this inefficiency results in significantly improved long-term energy efficiency, a parameter sometimes measured in terms of seasonal energy-efficiency ratio (SEER), which takes account of ON/OFF operation of the compressor on the efficiency of the system. SEER is defined as the ratio of the sum of Q, (heat absorbed by the evaporator) times the hours of operation to the sum of We (compressor work) times the hours of operation.

As will also be appreciated, variable cooling capacity can be provided in a single-

zone system such as illustrated in Fig. 5. Here, additional refrigerant would be diverted to bypass path 32 to accommodate a decrease in required cooling capacity, and the system could operate without the need for frequent compressor on-off cycling.

In the constructions described above, it has been assumed that a single refrigerant circulates through the system. Desuperheating bypass can also be used in conjunction with mixed refrigerants in regenerative systems to achieve highly beneficial results.

Fig. 10 illustrates use of de-superheating bypass in a simple mixed-refrigerant system, employing, for example, a mixture of refrigerants R-32, R-125, and R-134a. This is a commonly used beneficial combination as the R-32 component is flammable, but possesses excellent thermal characteristics, while the R-125 and R-134a components exhibit less desirable thermal characteristics than R-32 but are non-flammable. In the interest of simplicity, various possible regenerative paths as illustrated in our above-identified U. S.

Patents have been omitted from the illustrative system of Fig. 10.

The system, generally denoted at 106, comprises a compressor 12, an expansion device 16, an evaporator 18, a heat exchanger 3 6, and a pressure differential accommodating device 38 in a bypass path 110 as in system 30 (see Fig. 5). The condenser, however, is split into two stages 14a and 14b, and a liquid-vapor (LV) separator 108 of any suitable or desired type is provided between the two condenser stages.

LV separator 108 functions to separate the incoming vapor stream exiting from condenser stage 14a into a first vapor component which passes to the inlet of condenser stage 14b, and a second lower temperature liquid component a portion of which passes through a valve 112 to the inlet of heat exchanger 36.

The second component exiting from LV separator 108 is rich in the R-134a refrigerant due to its high condensation and boiling point relative to the other refrigerant components. Aside from the advantages of performing the de-superheating step outside condenser stage 14a as described above, the R-134a-rich composition of the refrigerant in

the bypass path to the condenser in liquid form has the added benefit of reducing the condenser pressure.

As indicated above, the system illustrated in Fig. 10 is representative of the application of the principles of this invention to mixed-refrigerant regenerative systems. It should be understood, however, that de-superheating bypass is applicable to other mixed-refrigerant regenerative system configurations as well.

In describing the invention, specific terminology has been employed for the sake of clarity. However, the invention is not intended to be limited to the specific descriptive terms, and it is to be understood that each specific term includes all technical equivalents that operate in a similar manner to accomplish a similar purpose.

Similarly, the embodiments described and illustrated are also intended to be exemplary, and various changes and modifications, and other embodiments within the scope of the invention will be apparent to those skilled in the art in light of the disclosure. The scope of the invention is therefore intended to be defined and limited only by the appended claims, and not by the description herein.