Non-flammable refrigerants having low GWP and systems and methods for providing refrigeration

Abstract

To provide systems and methods for cooling commodities (fruits, vegetables, water, etc.) without being exposed to a temperature below a freezing point of water.SOLUTION: A refrigerant composition includes: (a) from about 65 wt.% to about 90 wt.% of HFO-1234ze(E); (b) from about 10 wt.% to about 35 wt.% of HFO-1336mzz (E); and optionally (c) from about 0 wt.% to about 4.4 wt.% of HFC-227ea.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present invention relates to highly efficient, low global warming potential ("low GWP") refrigerants and air conditioning and / or refrigeration systems and methods for providing safe and effective cooling, and more particularly to systems and methods for cooling items (such as fruits, vegetables, and water) without exposing the items to temperatures below the freezing point of water. [Background technology]

[0002] Certain refrigeration applications require cooling of items without exposing them to temperatures below a certain temperature, such as the freezing point of water. For example, in supermarket environments, it is common to keep certain products at low temperatures relative to their surroundings, but at the same time, it is disadvantageous to cool the product below the freezing point of water, especially since the preferred method of cooling involves indirect cooling with moist, ambient air. For these applications, it is also disadvantageous to have refrigerant temperatures below the freezing point of water along the evaporator, as this would cause frost buildup and result in the need to defrost the equipment. Avoiding frost buildup is an important aspect of these applications. Similarly, cooling of beverages, including water, should also be performed under conditions that avoid exposing such products to temperatures below the freezing point of water, as freezing of such products is undesirable at the point of sale. For convenience, applicants refer to such applications, methods, and systems herein as "non-freezing" applications, methods, and systems.

[0003] Contains chlorofluorocarbons ("CFCs"), hydrochlorofluorocarbons ("HCFCs"), and hydrofluorolefins ("HFOs"). Certain single-component fluorocarbons, including fluorocarbons, have been used in "frost-free" applications, where the refrigerant temperature along the evaporator must remain above the freezing point of water so that frost does not accumulate on the coil surface, thereby eliminating the need for a defroster. In such refrigeration applications, systems, and methods, the use of single-component fluids has been considered particularly desirable because the saturation temperature of such fluids does not change upon evaporation of the fluid at constant pressure. The use of single-component fluids is highly desirable because it allows systems and methods to be designed with a refrigerant temperature along the evaporator that remains essentially constant during the evaporation process and exceeds the freezing point of water, assuming little or no pressure drop as the refrigerant flows through the evaporator. Additionally, product applications also typically require a small temperature difference between the air and the refrigerant to dehumidify the air and reduce the resulting moisture content removal and loss of product quality. The small temperature difference requirement and frost avoidance requirement, combined with the need for the evaporator to have a certain positive superheat at the outlet, are important when selecting a particular refrigerant. A superheat below zero, i.e., the refrigerant is not superheated, can lead to reduced cooling capacity, efficiency, and potential compressor failure. The term "superheat" or simply "superheat" refers to the temperature rise of the refrigerant at the outlet of the evaporator above the saturated vapor temperature (or dew point temperature) of the refrigerant.

[0004] This is shown by way of example in Figure 1, which represents in schematic form a typical supermarket produce cooling case. Typically, as shown in Figure 1, cooled, humidified air is provided to the product display zone of the display case by passing air both from outside the case 102 and from recirculated air 104 over the heat exchange surface of an evaporator coil 106, which is typically located within the display case in an area separate from (or at least hidden from the consumer's view) but adjacent to) the product display zone. The evaporator 106 has a single component refrigerant inlet 108 and a single component refrigerant outlet 110. A circulating fan 114 is also used. It is highly desirable in systems of the type illustrated above for the refrigeration system's cooling space 112 to have a refrigerant temperature along the evaporator that is always, or substantially always, above a certain level. For example, in many applications, such as produce refrigeration, the minimum discharge (outlet) temperature of the air in the display case is set by design at approximately 2°C to 3°C to provide a safety margin to avoid having the cooling space or cooled items below the freezing point of water. In addition, to minimize moisture removal from the air and the resulting drying out of the produce (loss of quality), the temperature difference between the air outlet and the refrigerant needs to be small, typically 2°C to 3°C. This, combined with the fact that the evaporators in these applications require a superheat of approximately 3°C to approximately 5°C, will impose constraints on the allowable evaporator gradient of the refrigerant so that the evaporation temperature remains above the freezing point of water and, as a result, frost does not accumulate. This is illustrated in Figures 2 and 3.

[0005] As an example in Figure 2, when the air discharge temperature is 3°C, a maximum evaporator gradient of 3°C (Refrigerant A) is allowed, and it can be seen that if the refrigerant has an evaporator gradient of more than 3°C, for example 4°C with Refrigerant B, the refrigerant temperature will fall below the freezing point of water and frost may accumulate.

[0006] In Figure 3, the air discharge temperature is 2°C, limiting the evaporator gradient to about 2°C (Refrigerant C); if the refrigerant has an evaporator gradient greater than 2°C, such as 3°C for Refrigerant D, the refrigerant temperature will reach freezing and frost may accumulate. In summary, to avoid frost accumulation in these applications, a gradient of less than 4.5°C is preferred, a gradient of less than 3°C is more preferred, and a gradient of less than 2°C is most preferred.

[0007] Those skilled in the art will appreciate that these two desirable results have often made it very difficult to provide refrigerants that are multi-component blends of different single component refrigerants.

[0008] Prior to the present invention, those skilled in the art have primarily utilized single component refrigerants, such as HFC-134a, in such low temperature sensitive applications, as discussed above, and have avoided refrigerant blends because blends generally suffer significant changes in boiling point temperature upon evaporation. Refrigerant blending has traditionally been recognized as a major obstacle to the ability to identify blends with the correct balance of properties useful in such systems.

[0009] However, Applicants have come to realize that identifying a single-component fluid with a set of properties that provide particular advantages in the above types of applications is also difficult in many applications. For example, many important applications require the identification of a refrigerant that simultaneously: (1) has an effective gradient, i.e., less than 4.5°C, preferably less than about 3°C, and even more preferably less than about 2°C, to avoid frost formation and maintain typical superheat, e.g., about 3°C ​​to about 5°C; (2) is non-flammable; (3) has low or substantially no toxicity; (4) has a low Global Warming Potential (GWP) (e.g., less than about 150, even more preferably less than about 75); and (5) has heat transfer and other properties (such as chemical stability) consistent with the needs of the particular application, particularly in medium-temperature heat transfer systems, and even more preferably in frost-free or low-frost medium-temperature refrigeration systems. While the use of a single component refrigerant can often satisfy items (1), (2), and (3), those skilled in the art will recognize refrigerants (single component or other) that can satisfy not only items (1), (2), and (3), but also most and preferably all of items (4)-(5). It has traditionally been found difficult (if not impossible) to detect non-combustible materials (those that are non-combustible and have low toxicity). Non-combustible materials are classified as Class "1" by ASHRAE, and low-toxic materials are classified as Class "A" by ASHRAE Standard 34-2016. Materials that are both non-combustible and low-toxic are classified as "A1" by ASHRAE Standard 34-2016.

[0010] For example, HFC-134a has traditionally been used in certain non-freezing applications, but nevertheless does not meet, for example, the low GWP requirement (item 5 above) because HFC-134a has a GWP of about 1300.

[0011] Applicants have proceeded in a manner that goes against conventional wisdom and have discovered unexpected and advantageous results. For example, Applicants have discovered that certain blends including carefully selected combinations of components, as described in detail below, can possess advantageous yet unexpected combinations of non-flammability while simultaneously possessing, among other things, excellent heat transfer properties, low GWP (e.g., GWP less than about 150), low or no toxicity, chemical stability, and lubricant compatibility. Furthermore, Applicants have discovered that the refrigerant compositions of the present invention have particular advantages for use in medium-temperature refrigeration systems, and particularly in medium-temperature refrigeration systems where it is desirable to maintain the temperature of the refrigerated air above about 0°C and to avoid exposing the refrigerated air to temperatures below about 0°C in order to protect the goods being refrigerated from frost and / or to prevent frost formation on the evaporator coil, which in itself can adversely affect the overall efficiency of such systems due to the need for defrosting across the coil and / or inconsistent cooling. Summary of the Invention

[0012] Applicants have discovered refrigeration methods and systems, including refrigerant compositions, heat transfer compositions comprising refrigerants, methods and systems for cooling materials having low temperature constraints, such as the low temperature or non-freezing applications described above, that utilize one or more of the compositions of the present invention as a refrigerant.

[0013] Thus, the present invention preferably provides compositions that are non-flammable, have low or substantially no toxicity, low global warming potential, and excellent heat transfer performance, particularly in medium temperature refrigeration systems and methods, and even more preferably in no-frost and low-frost medium temperature refrigeration systems.

[0014] Medium temperature refrigeration systems and methods are also provided by the present invention, as described in detail below.

[0015] Furthermore, applicants have come to understand that in many evaporators, such as direct expansion evaporators, there is a pressure drop as the refrigerant moves through the evaporator, and in many cases, that pressure drop is an amount that results in a saturation temperature drop of approximately 1°C to 2°C.

[0016] Thus, the refrigerants of the present invention include refrigerants having a GWP greater than about 75 and less than about 150, classified by ASHRAE as A1 (non-flammable and low toxicity), and having an evaporator gradient of less than about 3°C, and even more preferably less than about 2°C, and are preferably used in a system including an evaporator, and the pressure of the refrigerant is adjusted from the inlet to the outlet of the evaporator to raise the saturation temperature of the refrigerant by about 1°C to about 3°C. , most preferably by an amount that reduces the refrigerant temperature by about 1°C to about 2°C. This means that the refrigerants of the present invention according to such embodiments can achieve unexpectedly small changes in refrigerant temperature through the evaporator. For example, the change in refrigerant temperature between the inlet and outlet of the evaporator as a result of pressure drop is preferably less than the evaporator gradient (measured at a substantially constant evaporator inlet pressure), and even more preferably less than about 75% of the evaporator gradient, and even more preferably less than about 50% of the evaporator gradient. Thus, such preferred refrigerant compositions of the present invention having a GWP greater than about 75 and less than about 150 and classified by ASHRAE as A1 (non-flammable and low toxicity) are those in which the refrigerant's temperature can change by an amount of less than about 1°C as the refrigerant moves through the evaporator (i.e., the change in refrigerant temperature between the inlet and outlet of the evaporator as a result of pressure drop is preferably less than about 1°C). At least in part as a result of this discovery, the methods and systems of the present invention can be achieved utilizing highly efficient heat exchanger designs, particularly for applications such as reversible heat pumps in which refrigerant flow changes direction in the heat exchanger depending on the mode of operation (cooling or heating).

[0017] The refrigerants of the present invention also include refrigerants having a GWP of less than about 75, classified by ASHRAE as A1 (non-flammable and low toxicity), and an evaporator gradient of less than about 4.5°C, and are preferably used in a system including an evaporator, where the pressure of the refrigerant is reduced from the inlet to the outlet of the evaporator by an amount that reduces the saturation temperature of the refrigerant by about 0.5°C to about 2.0°C.

[0018] Therefore, in a preferred embodiment, the refrigerant according to the invention is used in an evaporator having a pressure drop corresponding to a saturation temperature loss which approximately corresponds to the increase in refrigerant temperature due to the gradient. [Brief explanation of the drawings]

[0019] [Figure 1] 1 depicts a schematic diagram from a typical supermarket produce cooling case. [Figure 2] The evaporator gradients for refrigerant A and refrigerant B are shown. [Figure 3] The evaporator gradients for refrigerant C and refrigerant D are shown. [Figure 4] The pressure reduction effect of the present invention is shown. DETAILED DESCRIPTION OF THE INVENTION

[0020] Description of Preferred Compositions The present invention provides a refrigerant that simultaneously: (1) has a gradient of less than 4.5 to help reduce or avoid frost formation and is capable of maintaining typical superheat, e.g., from about 3°C ​​to about 5°C; (2) is non-flammable; (3) has low or substantially no toxicity; (4) has a Global Warming Potential (GWP) of less than about 150; and (5) has heat transfer and other physical properties (such as chemical stability) consistent with the needs of a particular application, particularly in medium temperature heat transfer systems, and even more preferably in frost-free or low-frost medium temperature refrigeration systems.

[0021] The present invention also provides refrigerants that simultaneously: (1) have a gradient of less than about 3°C, preferably less than about 2°C (thus substantially avoiding frost formation and capable of maintaining typical superheat, e.g., about 3°C ​​to about 5°C), (2) are non-flammable, (3) have low or substantially no toxicity, (4) have a GWP of greater than about 75 and less than about 150, and (5) have heat transfer and other physical properties (such as chemical stability) consistent with the needs of a particular application, particularly in medium temperature heat transfer systems, and even more preferably in frost-free or low-frost medium temperature refrigeration systems.

[0022] The present invention also provides refrigerants that simultaneously: (1) have a gradient of less than 4.5°C, (2) are non-flammable, (3) have low or substantially no toxicity, (4) have a GWP of less than about 75, and (5) have heat transfer characteristics and other physical properties (such as chemical stability) consistent with the needs of a particular application, particularly in medium temperature heat transfer systems, and even more preferably in frost-free or low-frost medium temperature refrigeration systems. Definition:

[0023] The phrase "coefficient of performance" (hereinafter "COP") is a widely accepted measure of refrigerant performance that is particularly useful for expressing the relative thermodynamic efficiency of a refrigerant in a specific heating or cooling cycle involving evaporation or condensation of the refrigerant. In refrigeration, this term represents the ratio of available refrigeration or cooling capacity to the energy applied by the compressor during vapor compression, and thus represents the ability of a given compressor to deliver a quantity of heat for a given volumetric flow rate of a heat transfer fluid, such as a refrigerant. In other words, given a specific compressor, a refrigerant with a higher COP will deliver more cooling or heating power. One means for estimating the COP of a refrigerant at specific operating conditions is from the thermodynamic properties of the refrigerant using standard refrigeration cycle analysis techniques (see, for example, R.C. Downing, FLUOROCARBON REFRIGERANTS HANDBOOK, Chapter 3, Prentice-Hall, 1988, incorporated herein by reference in its entirety).

[0024] The "Global Warming Potential" (hereafter "GWP") was developed to allow for the comparison of the global warming impact of various gases. It compares the amount of heat trapped by a particular mass of gas with the amount of heat trapped by a similar mass of carbon dioxide over a particular period of time. Carbon dioxide was chosen by the Intergovernmental Panel on Climate Change (IPCC) as the standard gas, giving it a GWP of 1. The higher the GWP, the more a given gas will warm the Earth over that period compared to CO2.

[0025] The term "non-flammable" refers to the ASTM Standard E-681-2009 Standard Test Method for Concentration Limits of Flammability of Chemicals (Vapors and Gases) in accordance with ASHRAE Standard 34-2016 Designation and Safety Classification of "Non-flammable" refers to a compound or composition that is determined to be non-flammable when determined under the conditions set forth in ASHRAE Standard 34-2016, Appendix B1, as each standard exists as of the filing date of this application, and is incorporated herein by reference in its entirety (the "Non-flammability Test"). Flammability is defined as the ability of a composition to ignite and / or spread a flame. Under this test, flammability is determined by measuring the flame angle. Non-flammable materials are classified as Class "1" by ASHRAE Standard 34-2016, Designation and Safety Classification of Refrigerants, as each standard exists as of the filing date of this application.

[0026] As used herein, the term "evaporator gradient" refers to the difference between the saturation temperature of the refrigerant at the evaporator inlet and the dew point of the refrigerant at the evaporator outlet, assuming the pressure at the evaporator outlet is the same as the pressure at the inlet. As used herein, the expression "saturation temperature" refers to the temperature at which liquid refrigerant boils to a vapor at a given pressure.

[0027] As used herein, the phrase "non-toxic or low-toxicity" refers to a composition that is classified as Class "A" by ASHRAE Standard 34-2016 Designation and Safety Classification of Refrigerants and is listed in Appendix B1 of ASHRAE Standard 34-2016, as such standards exist as of the filing date of this application. A material that is non-flammable and low-toxicity is classified as "A1" by ASHRAE Standard 34-2016 Designation and Safety Classification of Refrigerants and is listed in Appendix B1 of ASHRAE Standard 34-2016, as such standards exist as of the filing date of this application.

[0028] The term "superheat" or simply "superheat" refers to the temperature rise of the refrigerant at the outlet of the evaporator above the saturated vapor temperature (or dew point temperature) of the refrigerant.

[0029] As used herein, the term E-1,3,3,3-tetrafluoropropene refers to the trans isomer of HFO-1234ze and is abbreviated as HFO-1234ze(E).

[0030] As used herein, the term E-1,1,1,4,4,4-hexafluorobut-2-ene refers to the trans isomer of HFO-1336mzz and is abbreviated as HFO-1336mzz(E).

[0031] As used herein, the term 1,1,1,2,3,3,3-heptafluoropropane is abbreviated as HFC-227ea.

[0032] As used herein, the term "about" in reference to amounts expressed as weight percent means that the amount of the ingredient can vary in an amount of + / - 2% by weight. Refrigerant composition HFO-1234ze(E) and HFO-1336mzz(E):

[0033] The present invention may comprise, consist essentially of, or consist of HFO-1234ze(E) and HFO-1336mzz(E).

[0034] The refrigerant may comprise (a) 65% to about 90% by weight HFO-1234ze(E), and (b) about 10% to about 35% by weight HFO-1336mzz(E). It will be understood that the refrigerant may consist essentially of HFO-1234ze(E) and HFO-1336mzz(E) in the amounts noted above, or may consist of HFO-1234ze(E) and HFO-1336mzz(E). The refrigerant described in this paragraph is sometimes referred to as "Refrigerant 1" for convenience.

[0035] The refrigerant may comprise (a) about 76% to about 90% by weight HFO-1234ze(E), and (b) about 10% to about 24% by weight HFO-1336mzz(E). It will be understood that the refrigerant may consist essentially of HFO-1234ze(E) and HFO-1336mzz(E) in the amounts noted above, or may consist of HFO-1234ze(E) and HFO-1336mzz(E). The refrigerant described in this paragraph is sometimes referred to as "Refrigerant 1A" for convenience.

[0036] The refrigerant may consist essentially of (a) about 65% to about 78% by weight HFO-1234ze(E), and (b) about 22% to about 35% by weight HFO-1336mzz(E). It will be understood that the refrigerant may consist of HFO-1234ze(E) and HFO-1336mzz(E) in the amounts described above. The refrigerant described in this paragraph is sometimes referred to as "Refrigerant 1B" for convenience.

[0037] The refrigerant may consist essentially of (a) about 70% to about 78% by weight HFO-1234ze(E), and (b) about 22% to about 30% by weight HFO-1336mzz(E). It will be understood that the refrigerant may consist of HFO-1234ze(E) and HFO-1336mzz(E) in the amounts described above. The refrigerant described in this paragraph is sometimes referred to as "Refrigerant 1C" for convenience.

[0038] The refrigerant may consist essentially of (a) 69.5% to 80% by weight HFO-1234ze(E), and (b) 20% to 30.5% by weight HFO-1336mzz(E). It will be understood that the refrigerant may consist of HFO-1234ze(E) and HFO-1336mzz(E) in the amounts stated above. The refrigerant described in this paragraph is sometimes referred to as "Refrigerant 1D" for convenience.

[0039] The refrigerant may consist essentially of (a) 65% + 0.5% / - 2.0% by weight HFO-1234ze(E), and (b) 35% + 2.0% / - 0.5% by weight HFO-1336mzz(E). It will be understood that the refrigerant may consist of HFO-1234ze(E) and HFO-1336mzz(E) in the amounts stated above. The refrigerant described in this paragraph is sometimes referred to as "Refrigerant 1E" for convenience.

[0040] The refrigerant may consist essentially of (a) 70 wt% + 0.5 wt% / - 2.0 wt% HFO-1234ze(E), and (b) 30 wt% + 2.0 wt% / - 0.5 wt% HFO-1336mzz(E). It will be understood that the refrigerant may consist of HFO-1234ze(E) and HFO-1336mzz(E) in the amounts stated above. The refrigerant described in this paragraph is sometimes referred to as "Refrigerant 1F" for convenience.

[0041] The refrigerant may consist essentially of (a) 69.5% to 80% by weight HFO-1234ze(E), and (b) 20% to 30.5% by weight HFO-1336mzz(E). It will be understood that the refrigerant may consist of HFO-1234ze(E) and HFO-1336mzz(E) in the amounts stated above. The refrigerant described in this paragraph is sometimes referred to as "Refrigerant 1D" for convenience.

[0042] The refrigerant may consist essentially of (a) 65% + 0.5% / - 2.0% by weight HFO-1234ze(E), and (b) 35% + 2.0% / - 0.5% by weight HFO-1336mzz(E). It will be understood that the refrigerant may consist of HFO-1234ze(E) and HFO-1336mzz(E) in the amounts stated above. The refrigerant described in this paragraph is sometimes referred to as "Refrigerant 1E" for convenience.

[0043] The refrigerant may consist essentially of (a) 70 wt% + 0.5 wt% / - 2.0 wt% HFO-1234ze(E), and (b) 30 wt% + 2.0 wt% / - 0.5 wt% HFO-1336mzz(E). It will be understood that the refrigerant may consist of HFO-1234ze(E) and HFO-1336mzz(E) in the amounts stated above. The refrigerant described in this paragraph is sometimes referred to as "Refrigerant 1F" for convenience.

[0044] The refrigerant may consist essentially of (a) 75% + 0.5% / - 2.0% by weight HFO-1234ze(E), and (b) 25% + 2.0% / - 0.5% by weight HFO-1336mzz(E). It will be understood that the refrigerant may consist of HFO-1234ze(E) and HFO-1336mzz(E) in the amounts stated above. The refrigerant described in this paragraph is sometimes referred to as "Refrigerant 1G" for convenience.

[0045] The refrigerant may consist essentially of (a) 78% by weight + 0.5% by weight / - 2.0% by weight HFO-1234ze(E), and (b) 20% by weight + 2.0% by weight / - 0.5% by weight HFO-1336mzz(E). It will be understood that the refrigerant may consist of HFO-1234ze(E) and HFO-1336mzz(E) in the amounts stated above. The refrigerant described in this paragraph is sometimes referred to as "Refrigerant 1H" for convenience.

[0046] The refrigerant may comprise (a) about 76% to about 80% by weight of HFO-1234ze(E), and (b) about 20% to about 24% by weight of HFO-1336mzz(E). It will be understood that the refrigerant may consist essentially of HFO-1234ze(E) and HFO-1336mzz(E) in the amounts stated above, or may consist of HFO-1234ze(E) and HFO-1336mzz(E). The refrigerant described in this paragraph is sometimes referred to as "Refrigerant 2" for convenience.

[0047] The refrigerant may comprise (a) about 78% to about 80% by weight of HFO-1234ze(E), and (b) about 20% to about 22% by weight of HFO-1336mzz(E). It will be understood that the refrigerant may consist essentially of HFO-1234ze(E) and HFO-1336mzz(E) in the amounts stated above, or may consist of HFO-1234ze(E) and HFO-1336mzz(E). The refrigerant described in this paragraph is sometimes referred to as "Refrigerant 3" for convenience.

[0048] The refrigerant may comprise (a) about 76% by weight HFO-1234ze(E) and (b) about 19% by weight HFO-1336mzz(E). It is understood that the refrigerant may consist essentially of HFO-1234ze(E) and HFO-1336mzz(E) in the amounts noted above, or may consist of HFO-1234ze(E) and HFO-1336mzz(E). The refrigerant described in this paragraph is sometimes referred to as "Refrigerant 4" for convenience. HFO-1234ze(E), HFO-1336mzz(E) and HFC-227ea:

[0049] The present invention may comprise, consist essentially of, or consist of HFO-1234ze(E), HFO-1336mzz(E), and HFC-227ea.

[0050] The refrigerant may contain (a) about 74.6% to about 78.6% by weight of HFO-1234ze(E), (b) about 17% to about 21% by weight of HFO-1336mzz(E), and (c) greater than 0% to about 4.4% by weight of HFC-227ea. Preferably, the refrigerant contains (a) 74.6% to about 78.6% by weight of HFO-1234ze(E), (b) about 17% to about 19% by weight of HFO-1336mzz(E), and (c) about 4.4% by weight of HFC-227ea. For example, the refrigerant may contain HFC-227ea in an amount of about 4.4% by weight. It will be understood that the refrigerant may consist essentially of, or consist of, HFO-1234ze(E), HFO-1336mzz(E), and HFC-227ea in the amounts described above. The refrigerant described in this paragraph is sometimes referred to as "Refrigerant 5" for convenience.

[0051] The refrigerant may comprise (a) about 78.6 wt.% HFO-1234ze(E), (b) about 17 wt.% HFO-1336mzz(E), and (c) about 4.4 wt.% HFC-227ea. It will be understood that the refrigerant may consist essentially of HFO-1234ze(E), HFO-1336mzz(E), and HFC-227ea in the amounts noted above, or may consist of HFO-1234ze(E), HFO-1336mzz(E), and HFC-227ea. The refrigerant described in this paragraph is sometimes referred to as "Refrigerant 6A" for convenience.

[0052] The refrigerant may comprise (a) about 76.6 wt. % HFO-1234ze(E), (b) about 19 wt. % HFO-1336mzz(E), and (c) about 4.4 wt. % HFC-227ea. It will be understood that the refrigerant may consist essentially of HFO-1234ze(E), HFO-1336mzz(E), and HFC-227ea in the amounts noted above, or may consist of HFO-1234ze(E), HFO-1336mzz(E), and HFC-227ea. The refrigerant described in this paragraph is sometimes referred to as "Refrigerant 6B" for convenience.

[0053] The refrigerant may comprise (a) about 74.6 wt. % HFO-1234ze(E), (b) about 21 wt. % HFO-1336mzz(E), and (c) about 4.4 wt. % HFC-227ea. It will be understood that the refrigerant may consist essentially of HFO-1234ze(E), HFO-1336mzz(E), and HFC-227ea in the amounts noted above, or may consist of HFO-1234ze(E), HFO-1336mzz(E), and HFC-227ea. The refrigerant described in this paragraph is sometimes referred to as "Refrigerant 6C" for convenience.

[0054] The refrigerant may comprise (a) about 78.6 wt% + 0.5 wt% / - 2.0 wt% HFO-1234ze(E), (b) 17 wt% + 2.0 wt% / - 0.5 wt% HFO-1336mzz(E), and (c) 4.4 wt% + 2.0 wt% / - 0.5 wt% HFC-227ea. It will be understood that the refrigerant may consist essentially of HFO-1234ze(E), HFO-1336mzz(E), and HFC-227ea in the amounts noted above, or may consist of HFO-1234ze(E), HFO-1336mzz(E), and HFC-227ea. The refrigerant described in this paragraph is sometimes referred to as "Refrigerant 6D" for convenience.

[0055] The refrigerant may comprise (a) approximately 76.6 wt% + 0.5 wt% / - 2.0 wt% HFO-1234ze(E), (b) 19 wt% + 2.0 wt% / - 0.5 wt% HFO-1336mzz(E), and (c) 4.4 wt% + 2.0 wt% / - 0.5 wt% HFC-227ea. It will be understood that the refrigerant may consist essentially of HFO-1234ze(E), HFO-1336mzz(E), and HFC-227ea in the amounts noted above, or may consist of HFO-1234ze(E), HFO-1336mzz(E), and HFC-227ea. The refrigerant described in this paragraph is sometimes referred to as "Refrigerant 6E" for convenience.

[0056] The refrigerant may comprise (a) approximately 74.6 wt% + 0.5 wt% / - 2.0 wt% HFO-1234ze(E), (b) 21 wt% + 2.0 wt% / - 0.5 wt% HFO-1336mzz(E), and (c) 4.4 wt% + 2.0 wt% / - 0.5 wt% HFC-227ea. It will be understood that the refrigerant may consist essentially of HFO-1234ze(E), HFO-1336mzz(E), and HFC-227ea in the amounts noted above, or may consist of HFO-1234ze(E), HFO-1336mzz(E), and HFC-227ea. The refrigerant described in this paragraph is sometimes referred to as "Refrigerant 6F" for convenience.

[0057] The refrigerant may comprise (a) 78.6 wt. % HFO-1234ze(E), (b) 17 wt. % HFO-1336mzz(E), and (c) 4.4 wt. % HFC-227ea. It will be understood that the refrigerant may consist essentially of HFO-1234ze(E), HFO-1336mzz(E), and HFC-227ea in the amounts noted above, or may consist of HFO-1234ze(E), HFO-1336mzz(E), and HFC-227ea. The refrigerant described in this paragraph is sometimes referred to as "Refrigerant 6G" for convenience.

[0058] The refrigerant may comprise (a) 76.6 wt. % HFO-1234ze(E), (b) 19 wt. % HFO-1336mzz(E), and (c) 4.4 wt. % HFC-227ea. It will be understood that the refrigerant may consist essentially of HFO-1234ze(E), HFO-1336mzz(E), and HFC-227ea in the amounts stated above, or may consist of HFO-1234ze(E), HFO-1336mzz(E), and HFC-227ea. The refrigerant described in this paragraph is sometimes referred to as "Refrigerant 6H" for convenience.

[0059] The refrigerant may comprise (a) 74.6 wt. % HFO-1234ze(E), (b) 21 wt. % HFO-1336mzz(E), and (c) 4.4 wt. % HFC-227ea. The refrigerant may consist essentially of HFO-1234ze(E), HFO-1336mzz(E), and HFC-227ea in the amounts described above, or may consist essentially of HFO-1234ze(E). , HFO-1336mzz(E), and HFC-227ea. The refrigerant described in this paragraph is sometimes referred to as "Refrigerant 6I" for convenience.

[0060] The refrigerant may comprise (a) about 78.6% to about 80.6% by weight of HFO-1234ze(E), (b) about 15% to about 17% by weight of HFO-1336mzz(E), and (c) about 4.4% by weight of HFC-227ea. It will be understood that the refrigerant may consist essentially of HFO-1234ze(E), HFO-1336mzz(E), and HFC-227ea in the amounts stated above, or may consist of HFO-1234ze(E), HFO-1336mzz(E), and HFC-227ea. The refrigerant described in this paragraph is sometimes referred to as "Refrigerant 7" for convenience.

[0061] Refrigerants, including each of Refrigerants 1-7, have a GWP of less than about 150. As used herein, the term "Refrigerants 1-7" refers separately and independently to each of Refrigerants 1, 1A, 1B, 1C, 1D, 1E, 1F, 1G, 1H, 2, 3, 4, 5, 6A, 6B, 6C, 6D, 6E, 6F, 6G, 6H, 61, and 7.

[0062] Certain preferred refrigerants of the present invention, including each of Refrigerants 1E-1H, have a GWP of less than about 75.

[0063] The refrigerants, including each of Refrigerants 1 to 7, may advantageously be non-flammable, in other words, they may be Class 1 refrigerants.

[0064] The refrigerants, including each of Refrigerants 1 to 7, are non-toxic or have low toxicity, i.e., are Class A refrigerants.

[0065] The refrigerants, including each of refrigerants 1-7, preferably have a gradient of less than 4.5, more preferably less than about 3°C, and even more preferably less than about 2°C.

[0066] It will be appreciated that the refrigerants, including each of Refrigerants 1-7 in the preferred embodiments, have one or more, and most preferably all, combinations of the above properties. Heat transfer composition:

[0067] The refrigerants of the invention can be provided in a heat transfer composition. Thus, the heat transfer compositions of the invention include the preferred refrigerant compositions disclosed herein, and in particular the refrigerants of the invention comprising any of Refrigerants 1-7. Preferably, the invention relates to heat transfer compositions comprising a refrigerant, wherein the refrigerant comprises each of Refrigerants 1-7 in an amount of at least about 80% by weight of the heat transfer composition, or at least about 90% by weight of the heat transfer composition, or at least about 97% by weight of the heat transfer composition, or at least about 99% by weight of the heat transfer composition. The heat transfer composition may consist essentially of the refrigerant, or may consist of the refrigerant. Lubricant:

[0068] Preferably, the heat transfer composition may further comprise a lubricant. The lubricant lubricates the refrigerant compressor using the refrigerant. Preferably, the lubricant is present in the heat transfer composition in an amount of about 1% to about 50% by weight of the heat transfer composition, more preferably about 10% to about 50% by weight of the heat transfer composition, and most preferably about 30% to about 50% by weight of the heat transfer composition. Useful lubricants include alkylbenzenes, esters, polyol esters ("POE"), polyalkylene glycols ("PAG"), polyvinyl ethers ("PVE"), poly(α-olefins) ("PAO"), and combinations thereof. Commercially available alkylbenzene lubricants include Zerol 150®. PAGs are available as GM Goodwrench Refrigeration Oil and MOPAR-56. Other useful esters include phosphate esters, dibasic acid esters, and fluoroesters.

[0069] Commercially available POEs include neopentyl glycol dipelargonate, available as Emery 2917® and Hatcol 2370®, and pentaerythritol derivatives such as those sold under the trade names Emkarate RL32-3MAF and Emkarate RL68H by CPI Fluid Engineering. Emkarate RL32-3MAF and Emkarate RL68H have the properties identified in the table below. [Table 1]

[0070] Commercially available PVEs include polyvinyl ethers FVC-32D® and FVC-68D® by Idemitsu.

[0071] Preferred lubricants include POE and PVE, more preferably POE. Of course, different mixtures of different types of lubricants may be used.

[0072] The heat transfer compositions of the present invention can consist essentially of or consist of refrigerants, including each of Refrigerants 1-7, and lubricants, including each of the preferred lubricants, especially as described above.

[0073] A preferred heat transfer composition of the invention comprises any one of Refrigerants 1-7 and a POE lubricant.

[0074] A preferred heat transfer composition of the invention comprises refrigerant 6D and a POE lubricant.

[0075] A preferred heat transfer composition of the invention comprises refrigerant 6D and a POE lubricant having a viscosity (ASTM D445) of about 31 to about 67 at 40°C.

[0076] A preferred heat transfer composition of the invention comprises refrigerant 6D and a POE lubricant having a viscosity (ASTM D445) of about 5 to about 10 at 100°C.

[0077] A preferred heat transfer composition of the invention comprises refrigerant 6E and a POE lubricant.

[0078] A preferred heat transfer composition of the invention comprises a refrigerant 6E and a POE lubricant having a viscosity (ASTM D445) of about 31 to about 67 at 40°C.

[0079] A preferred heat transfer composition of the invention comprises a refrigerant 6E and a POE lubricant having a viscosity at 100°C (ASTM D445) of about 5 to about 10.

[0080] A preferred heat transfer composition of the invention comprises refrigerant 6F and a POE lubricant.

[0081] A preferred heat transfer composition of the invention comprises a refrigerant 6F having a viscosity (ASTM D445) of about 31 to about 67 at 40° C. and a POE lubricant.

[0082] A preferred heat transfer composition of the invention comprises a refrigerant 6F having a viscosity (ASTM D445) of about 5 to about 10 at 100° C. and a POE lubricant.

[0083] A preferred heat transfer composition of the invention comprises refrigerant 6G and a POE lubricant.

[0084] A preferred heat transfer composition of the invention comprises refrigerant 6G and a POE lubricant having a viscosity (ASTM D445) of about 31 to about 67 at 40°C.

[0085] A preferred heat transfer composition of the invention comprises refrigerant 6G having a viscosity (ASTM D445) of about 5 to about 10 at 100° C. and a POE lubricant.

[0086] A preferred heat transfer composition of the invention comprises the refrigerant 6H and a POE lubricant.

[0087] A preferred heat transfer composition of the invention comprises a refrigerant 6H and a POE lubricant having a viscosity at 40°C (ASTM D445) of about 31 to about 67.

[0088] A preferred heat transfer composition of the invention comprises a refrigerant 6H and a POE lubricant having a viscosity at 100°C (ASTM D445) of about 5 to about 10.

[0089] A preferred heat transfer composition of the invention comprises refrigerant 6I and a POE lubricant.

[0090] A preferred heat transfer composition of the invention comprises a refrigerant 61 having a viscosity (ASTM D445) of about 31 to about 67 at 40° C. and a POE lubricant.

[0091] A preferred heat transfer composition of the invention comprises a refrigerant 6I having a viscosity (ASTM D445) of about 5 to about 10 at 100° C. and a POE lubricant.

[0092] A preferred heat transfer composition of the invention comprises any one of Refrigerants 1-7 and a PVE lubricant.

[0093] A preferred heat transfer composition of the invention comprises refrigerant 6D and PVE lubricant.

[0094] A preferred heat transfer composition of the invention comprises refrigerant 6E and PVE lubricant.

[0095] A preferred heat transfer composition of the invention comprises refrigerant 6F and a PVE lubricant.

[0096] A preferred heat transfer composition of the invention comprises refrigerant 6G and PVE lubricant.

[0097] A preferred heat transfer composition of the invention comprises refrigerant 6H and PVE lubricant.

[0098] A preferred heat transfer composition of the invention comprises refrigerant 6I and a PVE lubricant. use

[0099] The methods and systems of the present invention may include any heat transfer system and / or any heat transfer method that utilizes a refrigerant, including each of Refrigerants 1-7, or a heat transfer composition comprising a refrigerant of the present invention, including each of Refrigerants 1-7, to absorb heat, reject heat, or both absorb and reject heat. Accordingly, the present invention provides methods for heating or cooling a fluid or object using a refrigerant, including each of Refrigerants 1-7, or a heat transfer composition comprising a refrigerant of the present invention, including each of Refrigerants 1-7. The invention also provides heat transfer systems comprising a refrigerant, including each of Refrigerants 1-7, or a heat transfer composition comprising a refrigerant of the present invention, including each of Refrigerants 1-7. It will be understood that the heat transfer systems described herein may be vapor compression systems having an evaporator, condenser, and compressor in fluid communication.

[0100] Applicants have discovered that substantial advantages, such as may occur for cooling produce and / or other frozen foods or in connection with cooling certain electronic devices, may be achieved in connection with heat transfer systems and methods in which refrigerants including each of Refrigerants 1-7, or inventive heat transfer compositions including Refrigerants 1-7, are used to absorb heat from a fluid surrounding an article or otherwise transfer heat to and from the article itself. In such cases, the fluid may be air or a secondary coolant (e.g., water, glycol, water / glycol, etc.). coal mixtures, saline solutions, etc.), such as occurs in the case of refrigerants used in evaporators in systems and methods that require that the temperature of the article or fluid being cooled is not exposed to temperatures below a certain limit.

[0101] Thus, in general, the methods and systems of the present invention utilize devices and / or processes that enable the refrigerant or heat transfer composition of the present invention to absorb heat, and subsequently remove the absorbed heat from the refrigerant.

[0102] The present invention provides a refrigeration system, an air conditioning system, or a heat pump system comprising a refrigerant including each of Refrigerants 1 to 7, or a heat transfer composition comprising a refrigerant of the present invention, including each of Refrigerants 1 to 7.

[0103] The present invention provides a refrigeration system, an air conditioning system, or a heat pump system comprising a heat transfer composition comprising a refrigerant according to any one of Refrigerants 6D, 6E, 6F, 6G, 6H, and 6I, or a refrigerant of the present invention comprising each of Refrigerants 6D, 6E, 6F, 6G, 6H, and 6I.

[0104] It will be understood that an evaporator used to absorb heat from an item or fluid being cooled may include a conduit, such as a cooling coil, through which a refrigerant, including each of Refrigerants 1-7, flows while such conduit is exposed (directly or indirectly) to the item or fluid to be cooled. In this manner, heat flows from the fluid being cooled (e.g., air) and / or surrounding items (e.g., fresh produce such as fruits, vegetables, and flowers), through the metal or other thermally conductive material of the conduit, and into the refrigerant of the present invention, including each of Refrigerants 1-7.

[0105] Applicants have discovered that for systems in which the cooled discharge air is controlled at a temperature of about 2°C to about 5°C, when the cooled discharge air is at a temperature of about 2°C to about 4°C, and more preferably in certain embodiments (e.g., cooled fresh cut fruit, vegetables, and flowers), when the cooled discharge air is at a temperature of about 2°C to about 3°C, the refrigerant compositions of the present invention, including each of Refrigerants 1-7, have an evaporator slope that is preferably less than about 3°C, and even more preferably less than about 2°C.

[0106] Applicant's discovery of this effect, achievable according to the present methods and systems utilizing the present preferred refrigerant compositions, including each of Refrigerants 1-7, and the present heat exchanger designs, is shown schematically in FIG. 4.

[0107] It will be appreciated that refrigerants according to the present invention, including each of Refrigerants 1-7, can be used in systems having an evaporator with a pressure drop corresponding to a saturation temperature loss that approximately corresponds to the increase in refrigerant temperature due to the gradient.

[0108] Certain systems and methods of the present invention are described below. Refrigeration system

[0109] The present invention provides a refrigeration system comprising an inventive refrigerant or heat transfer composition. The present invention also provides a method for cooling a fluid or object using a refrigeration system, the method comprising the steps of (a) evaporating an inventive refrigerant composition, including each of Refrigerants 1-7, in the vicinity of the fluid or object to be cooled, and (b) condensing the refrigerant.

[0110] The refrigerants and heat transfer compositions of the invention can be used in any refrigeration system. However, Applicants have discovered that the refrigerants, including each of Refrigerants 1-7, and the heat transfer compositions comprising the refrigerants of the invention, including each of Refrigerants 1-7, offer particular advantages in medium-temperature refrigeration systems, particularly those used in "frost-free" applications, such as those in which the refrigerant temperature along the evaporator must be maintained above the freezing point of water (i.e., above 0°C). This prevents frost from building up on the evaporator surface, resulting in no or less frequent defrost cycles being required.

[0111] The refrigerants and heat transfer compositions of the invention can be used in any refrigeration system. However, applicants have discovered that the present refrigerants, including Refrigerants 6D, 6E, 6F, 6G, 6H, and 6I, or heat transfer compositions containing the refrigerants of the invention, including Refrigerants 6D, 6E, 6F, 6G, 6H, and 6I, respectively, offer particular advantages in medium-temperature refrigeration systems, particularly those used in "frost-free" applications, such as those in which the refrigerant temperature along the evaporator must be maintained above the freezing point of water (i.e., above 0°C). This prevents frost from building up on the evaporator surface, thereby eliminating or reducing the frequency of defrost cycles required.

[0112] Thus, the present invention relates to a medium-temperature refrigeration system containing a refrigerant comprising any one of Refrigerants 6D, 6E, 6F, 6G, 6H, and 6I, or a heat transfer composition comprising a refrigerant of the present invention comprising each of Refrigerants 6D, 6E, 6F, 6G, 6H, and 6I. The present invention also provides a method for cooling a fluid or object in a medium-temperature refrigeration system, the method comprising the steps of: (a) evaporating, in the vicinity of the fluid or object to be cooled, a refrigerant composition of the present invention comprising Refrigerants 6D, 6E, 6F, 6G, 6H, and 6I, or a heat transfer composition comprising a refrigerant of the present invention comprising each of Refrigerants 6D, 6E, 6F, 6G, 6H, and 6I, and (b) condensing the refrigerant. Preferably, the evaporator temperature is from about -15°C to about 5°C, more preferably from about -10°C to about 5°C.

[0113] As used herein, a medium temperature refrigeration system refers to a refrigeration system utilizing one or more compressors and operating under or within the following conditions: (a) a condenser temperature of about 15°C to about 60°C, preferably about 25°C to about 45°C; (b) an evaporator temperature of about -15°C to about 5°C, preferably about -10°C to about 5°C; optionally (c) an evaporator outlet superheat of about 0°C to about 10°C, preferably about 1°C to about 6°C; and optionally (d) a superheat in the intake line of about 5°C to about 40°C, preferably about 15°C to about 30°C. The superheat along the intake line may be generated by a heat exchanger.

[0114] Examples of medium-temperature refrigeration systems include small refrigeration systems (including vending machines, ice makers, and household appliances), commercial refrigeration systems (such as supermarket refrigeration systems and walk-in coolers), residential refrigeration systems, industrial refrigeration systems, and skating rinks. can be done.

[0115] For storage of perishable produce such as vegetables and fruits in a medium temperature refrigeration system, for example, the fluid to be cooled is air with a desired cooling temperature of about 2°C to about 5°C, preferably about 2°C to about 4°C, and more preferably about 2°C to about 3°C ​​(e.g., cooling fresh-cut fruit, vegetables, and flowers). Furthermore, in many applications, it is preferred that the refrigerant temperature along the evaporator not reach below about 0°C (the freezing point of water) to avoid frost formation. Preferably, at the same time, the superheat at the outlet of the evaporator should be maintained at a typical value of about 3°C ​​to about 5°C, preferably about 4°C.

[0116] Accordingly, the invention preferably provides a medium temperature refrigeration system comprising a refrigerant, including each of Refrigerants 1-7, or a heat transfer composition comprising a refrigerant of the invention, including each of Refrigerants 1-7, wherein the system has an evaporator temperature of about 0°C to about 5°C.

[0117] Accordingly, the invention provides a medium temperature refrigeration system, preferably comprising a refrigerant comprising each of Refrigerants 6D, 6E, 6F, 6G, 6H and 6I, or a heat transfer composition comprising a refrigerant of the invention comprising each of Refrigerants 6D, 6E, 6F, 6G, 6H and 6I, wherein the system has an evaporator temperature of about 0°C to about 5°C.

[0118] The present invention also provides a method for cooling a fluid or object in a medium temperature refrigeration system, the method comprising the steps of: (a) evaporating an inventive refrigerant composition, including each of Refrigerants 1-7, in the vicinity of the fluid or object to be cooled; and (b) condensing the refrigerant, the system having an evaporator temperature of from about 0°C to about 5°C.

[0119] The refrigerant and heat transfer compositions of the invention can also be used in other refrigeration applications.

[0120] For example, the present invention relates to a low-temperature refrigeration system comprising a refrigerant, including each of Refrigerants 1-7, or a heat transfer composition comprising a refrigerant of the present invention, including each of Refrigerants 1-7. The present invention also provides a method for cooling a fluid or object in a low-temperature refrigeration system, the method comprising the steps of: (a) evaporating an inventive refrigerant composition, including each of Refrigerants 1-7, in the vicinity of the fluid or object to be cooled; and (b) condensing the refrigerant. Preferably, the evaporator temperature is from about -40°C to less than about -15°C, more preferably from about -40°C to about -25°C.

[0121] For example, the present invention relates to a low-temperature refrigeration system containing a refrigerant comprising Refrigerants 6D, 6E, 6F, 6G, 6H, and 6I, or a heat transfer composition comprising a refrigerant of the present invention comprising Refrigerants 6D, 6E, 6F, 6G, 6H, and 6I, respectively. The present invention also provides a method for cooling a fluid or object in a low-temperature refrigeration system, the method comprising the steps of: (a) evaporating, in the vicinity of the fluid or object to be cooled, a refrigerant composition of the present invention comprising Refrigerants 6D, 6E, 6F, 6G, 6H, and 6I, or a heat transfer composition comprising a refrigerant of the present invention comprising Refrigerants 6D, 6E, 6F, 6G, 6H, and 6I, respectively; and (b) condensing the refrigerant. Preferably, the evaporator temperature is from about -40°C to less than about -15°C, more preferably from about -40°C to about -25°C.

[0122] As used herein, a low temperature refrigeration system refers to a refrigeration system utilizing one or more compressors and operating under or within the following conditions: (a) a condenser temperature of about 15°C to about 50°C, preferably about 25°C to about 45°C, (b) an evaporator temperature of about -40°C to about -15°C or less than about -15°C, preferably about -40°C to about -25°C, optionally (c) an evaporator outlet superheat of about 0°C to about 10°C, preferably about 1°C to about 6°C, and optionally (d) a superheat in the intake line of about 15°C to about 40°C, preferably about 20°C to about 30°C.

[0123] Examples of low temperature refrigeration systems include supermarket refrigeration systems, commercial refrigerator systems (including supermarket refrigerators), residential refrigerator systems, and industrial refrigerator systems.

[0124] Low temperature refrigeration systems can be used to cool frozen goods.

[0125] The present invention relates to a cascade refrigeration system comprising an inventive refrigerant or heat transfer composition.

[0126] Generally, a cascade system has two or more stages. When a cascade system has two stages, these are generally referred to as the upper and lower stages. The refrigerants of the invention, including Refrigerants 1-7, or heat transfer compositions containing the refrigerants of the present invention, including Refrigerants 1-7, may be used in either the upper or lower stage of a cascade refrigeration system. However, it is preferred that the refrigerants of the invention, including Refrigerants 1-7, or heat transfer compositions containing the refrigerants of the present invention, including Refrigerants 1-7, be used in the upper stage of a cascade system. Given the teachings contained herein, one skilled in the art will be able to determine suitable refrigerants for use in the lower stage of a cascade system, which may include, for example, CO2, R1234yf, and R455A. R455A is a blend of 75.5% R1234yf, 21.5% R32, and 3% CO2. In a cascade system, this refrigerant can replace R404A.

[0127] Generally, a cascade system has two or more stages. When a cascade system has two stages, these are generally referred to as the upper and lower stages. The refrigerants of the invention, including refrigerants 6D, 6E, 6F, 6G, 6H, and 6I, or heat transfer compositions of the invention, including refrigerants 6D, 6E, 6F, 6G, 6H, and 6I, may be used in either the upper or lower stage of a cascade refrigeration system. However, the refrigerants of the invention, including refrigerants 6D, 6E, 6F, 6G, 6H, and 6I, or heat transfer compositions of the invention, including refrigerants 6D, 6E, 6F, 6G, 6H, and 6I, are preferably used in the upper stage of a cascade system. Given the teachings contained herein, one skilled in the art will be able to determine suitable refrigerants for use in the lower stage of a cascade system, which may include, for example, CO2, R1234yf, and R455A. R455A is a blend of 75.5% R1234yf, 21.5% R32, and 3% CO. In cascade systems, this refrigerant can replace R404A.

[0128] Transport refrigeration creates a link in the cold chain that allows frozen or chilled produce to reach the end user in the correct temperature environment. The present invention relates to the use of inventive refrigerants, including each of Refrigerants 1-7, or thermal storage systems that contain the inventive refrigerants, including each of Refrigerants 1-7. The present invention relates to a transport refrigeration system comprising a transfer composition.

[0129] Transport refrigeration creates a link in the cold chain that allows frozen or chilled produce to reach the end user in the correct temperature environment. The present invention relates to transport refrigeration systems comprising an inventive refrigerant, including each of Refrigerants 6D, 6E, 6F, 6G, 6H, and 6I, or a heat transfer composition comprising an inventive refrigerant, including each of Refrigerants 6D, 6E, 6F, 6G, 6H, and 6I.

[0130] Examples of transport refrigeration include refrigerated road vehicles (such as trucks and vans), train cars, and containers transportable by road vehicles, trains, and ships / boats. Secondary Loop System

[0131] Refrigerants of the present invention, including each of Refrigerants 1-7, or heat transfer compositions comprising refrigerants of the present invention, including each of Refrigerants 1-7, may be used as secondary fluids in secondary loop systems. A secondary loop system includes a primary vapor compression system loop using a primary refrigerant and an evaporator that cools the secondary loop fluid. The secondary fluid then provides the cooling required for the application. Because refrigerants in such loops may be exposed to humans near the cooled space, the secondary fluid must be non-flammable and have low toxicity. In other words, refrigerants of the present invention, including each of Refrigerants 1-7, may be used as "secondary fluids." Primary fluids for use in the primary loop (vapor compression cycle, external / outdoor component of the loop) may include, but are not limited to, the following refrigerants: R404A, R507, R410A, R455A, R32, R466A, R44B, R290, R717, R452B, R448A, R1234ze(E), R1234yf, and R449A.

[0132] The refrigerants of the present invention, including Refrigerants 6D, 6E, 6F, 6G, 6H, and 6I, or heat transfer compositions containing the refrigerants of the present invention, including Refrigerants 6D, 6E, 6F, 6G, 6H, and 6I, can be used as secondary fluids in secondary loop systems. The secondary loop system includes a primary vapor compression system loop using a primary refrigerant and an evaporator that cools the secondary loop fluid. The secondary fluid then provides the cooling required for the application. Because the refrigerants in such loops may be exposed to humans near the cooled space, the secondary fluid must be non-flammable and have low toxicity. In other words, the refrigerants of the present invention, including Refrigerants 6D, 6E, 6F, 6G, 6H, and 6I, can be used as "secondary fluids." Primary fluids for use in the primary loop (vapor compression cycle, external / outdoor part of the loop) may include, but are not limited to, the following refrigerants: R404A, R507, R410A, R455A, R32, R466A, R44B, R290, R717, R452B, R448A, R1234ze(E), R1234yf, and R449A. heat pump system

[0133] The present invention relates to a heat pump system comprising an inventive refrigerant, including each of Refrigerants 1-7, or a heat transfer composition comprising an inventive refrigerant, including each of Refrigerants 1-7.

[0134] The present invention also provides a method for heating a fluid or object using a heat pump, the method comprising the steps of: (a) condensing an inventive refrigerant composition comprising each of Refrigerants 1-7 in the vicinity of the fluid or object to be heated; and (b) evaporating the refrigerant.

[0135] The present invention relates to a heat pump system comprising an inventive refrigerant, including each of Refrigerants 6D, 6E, 6F, 6G, 6H and 6I, or a heat transfer composition comprising an inventive refrigerant, including each of Refrigerants 6D, 6E, 6F, 6G, 6H and 6I.

[0136] The present invention also provides a method for heating a fluid or object using a heat pump, the method comprising the steps of: (a) condensing an inventive refrigerant composition comprising each of Refrigerants 6D, 6E, 6F, 6G, 6H, and 6I in the vicinity of the fluid or object to be heated; and (b) evaporating the refrigerant.

[0137] Examples of heat pumps include heat pump tumble dryers, reversible heat pumps, high temperature heat pumps, and air-to-air heat pumps. Air conditioning system

[0138] The present invention relates to an air conditioning system comprising a refrigerant or inventive refrigerant, including each of Refrigerants 1-7, or a heat transfer composition comprising a refrigerant of the present invention, including each of Refrigerants 1-7. The present invention also provides a method of air conditioning using the air conditioning system, the method comprising the steps of (a) evaporating an inventive refrigerant composition, including each of Refrigerants 1-7, in the vicinity of a fluid of a body to be cooled, and (b) condensing the refrigerant. The air may be conditioned directly or indirectly by an inventive refrigerant, including each of Refrigerants 1-7.

[0139] The present invention relates to an air conditioning system comprising an inventive refrigerant, including refrigerants 6D, 6E, 6F, 6G, 6H, and 6I, or a heat transfer composition comprising an inventive refrigerant, including refrigerants 6D, 6E, 6F, 6G, 6H, and 6I, respectively. The present invention also provides a method of air conditioning using an air conditioning system, the method comprising the steps of (a) evaporating an inventive refrigerant composition, including refrigerants 6D, 6E, 6F, 6G, 6H, and 6I, respectively, in the vicinity of a fluid of a body to be cooled, and (b) condensing the refrigerant. The air may be conditioned directly or indirectly by an inventive refrigerant, including refrigerants 6D, 6E, 6F, 6G, 6H, and 6I, respectively.

[0140] Examples of air conditioning systems include chillers, residential, industrial, commercial, and mobile air conditioning, including air conditioning for road vehicles such as automobiles, trucks, and buses, and air conditioning for boats and trains.

[0141] Preferred refrigeration systems of the present invention include chillers containing refrigerants of the present invention, particularly including each of Refrigerants 1-7, and even more particularly Refrigerants 4 and 6A-6I.

[0142] Preferred refrigeration systems of the present invention include residential air conditioning systems comprising refrigerants of the present invention, particularly including each of Refrigerants 1-7, and even more particularly Refrigerants 4 and 6A-6I.

[0143] Preferred refrigeration systems of the present invention include industrial air conditioning systems comprising refrigerants of the present invention, particularly including each of Refrigerants 1-7, and even more particularly Refrigerants 4 and 6A-6I.

[0144] Preferred refrigeration systems of the present invention include commercial air conditioning systems containing refrigerants of the present invention, particularly including each of Refrigerants 1-7, and even more particularly Refrigerants 4 and 6A-6I.

[0145] Preferred refrigeration systems of the present invention include mobile air conditioning systems comprising refrigerants of the present invention, particularly including each of Refrigerants 1-7, and even more particularly Refrigerants 4 and 6A-6I.

[0146] It will be understood that any of the above-described refrigeration, air conditioning, or heat pump systems using an inventive refrigerant, including each of Refrigerants 1-7, or a heat transfer composition comprising an inventive refrigerant, including each of Refrigerants 1-7, may include a suction line / liquid line heat exchanger (SL-LL HX).

[0147] It will be understood that any of the above-described refrigeration, air conditioning, or heat pump systems using an inventive refrigerant, including each of refrigerants 6D, 6E, 6F, 6G, 6H, and 6I, or a heat transfer composition comprising an inventive refrigerant, including each of refrigerants 6D, 6E, 6F, 6G, 6H, and 6I, may include a suction line / liquid line heat exchanger (SL-LL HX). Organic Rankine Cycle System

[0148] Inventive refrigerant compositions, including each of Refrigerants 1-7, or heat transfer compositions comprising the inventive refrigerants, including each of Refrigerants 1-7, may be used in Organic Rankine Cycles (ORCs). In the context of ORCs, the refrigerants used in these systems may also be classified as "working fluids."

[0149] Inventive refrigerant compositions comprising refrigerants 6D, 6E, 6F, 6G, 6H, and 6I, or heat transfer compositions comprising inventive refrigerants comprising refrigerants 6D, 6E, 6F, 6G, 6H, and 6I, may be used in Organic Rankine Cycles (ORCs). In the context of ORCs, the refrigerants used in these systems may also be classified as "working fluids."

[0150] Rankine cycle systems are known to be a simple and reliable means for converting thermal energy into mechanical shaft power.

[0151] In industrial environments, it may be possible to use flammable working fluids such as toluene and pentane, especially if the industrial environment already has large amounts of flammable materials in operation or storage on-site. However, when the risks associated with using flammable and / or toxic working fluids are unacceptable, such as power generation in populated areas or near buildings, it is necessary to use non-flammable and / or non-toxic refrigerants as working fluids. Also, there are some industries that consider these materials to be environmentally unacceptable from a GWP perspective. There is also a movement to make it acceptable.

[0152] The process for recovering waste heat in an organic Rankine cycle system involves pumping a liquid-phase working fluid through a heat exchanger (boiler) where an external (waste) heat source, such as a process stream, heats the working fluid and vaporizes it into saturated or superheated vapor. This vapor expands through a turbine, converting the waste heat energy into mechanical energy. The vapor-phase working fluid is then condensed to a liquid and pumped back into the boiler to repeat the heat extraction cycle.

[0153] Thus, the present invention relates to the use of an inventive refrigerant, including each of Refrigerants 1 to 7, or a heat transfer composition comprising an inventive refrigerant, including each of Refrigerants 1 to 7, in an organic Rankine cycle.

[0154] Accordingly, the present invention provides a process for converting thermal energy to mechanical energy in a Rankine cycle, the method comprising: i) vaporizing a working fluid at a heat source and expanding the resulting vapor, or vaporizing a working fluid at a heat source and expanding the resulting vapor, and then ii) cooling the working fluid at a heat sink to condense the vapor, wherein the working fluid is a refrigerant or inventive refrigerant, including each of Refrigerants 1-7, or a heat transfer composition comprising a refrigerant of the invention, including each of Refrigerants 1-7.

[0155] The mechanical work can be transmitted to an electrical device, such as a generator, to produce electrical power.

[0156] The heat source may be provided by a thermal energy source selected from industrial waste heat, solar energy, geothermal hot water, low pressure steam, a distributed power generation system utilizing a fuel cell, an internal combustion engine, or a prime mover. Preferably, the low pressure steam is low pressure geothermal steam or is provided by a fossil fuel powered power plant.

[0157] It will be understood that heat source temperatures can vary widely, e.g., from about 90°C to over 800°C, and can depend on a myriad of factors, including the particular combustion gas and, for some fuel cells, geography, time of year, etc. Sources such as wastewater or low-pressure steam from, for example, plastic manufacturing plants, and / or chemical or other industrial plants, oil refineries, etc., as well as geothermal-based systems, can have source temperatures of about 100°C or less, in some cases as low as about 90°C, or even as low as about 80°C. Gaseous heat sources, such as exhaust gases from combustion processes or any heat source where subsequent processing to remove particulates and / or corrosive species leads to lower temperatures, can also have source temperatures of about 130°C or less, about 120°C or less, about 100°C or less, in some cases as low as about 90°C, or even as low as about 80°C. electronic cooling

[0158] Refrigerant compositions of the invention, including any one of Refrigerants 1-7, can be used in connection with systems and methods for electronic cooling, such as cooling chips, electronic substrates, batteries (including batteries used in automobiles, trucks, buses, and other electronic transportation vehicles), computers, and the like.

[0159] The refrigerant of the invention includes any one of refrigerants 6D, 6E, 6F, 6G, 6H and 6I. The catalyst compositions may be used in connection with systems and methods for electronic cooling, such as cooling chips, electronic substrates, batteries (including batteries used in automobiles, trucks, buses, and other electronic transportation vehicles), computers, and the like. Heat Transfer Composition

[0160] The heat transfer composition comprises any one of Refrigerants 1-7 and a lubricant in a low temperature refrigeration system as follows: [Table 2]

[0161] The heat transfer composition comprises any one of Refrigerants 1-7 and a lubricant in a medium temperature refrigeration system as follows: [Table 3]

[0162] The heat transfer composition comprises any one of Refrigerants 1-7, and a lubricant, as follows, in a retail food refrigeration system: [Table 4]

[0163] The heat transfer composition comprises any one of Refrigerants 1-7 and a lubricant in a shipping container refrigeration system as follows: [Table 5] [Example]

[0164] In the following examples, the subject refrigerant compositions are identified as compositions A1 to A8 in Table 1 below. Refrigerants A1, A2, A3, A4, A4', A4'', A5, A6, A7 and A8 are identified as compositions A1 to A8 in Table 1 below. The refrigerant compositions identified in Table 1 below are refrigerants within the scope of the invention as described herein. Each refrigerant was subjected to thermodynamic analysis to determine its ability to match the operating characteristics of R-134a in various refrigeration systems. The analysis was performed using experimental data collected on the properties of various binary and ternary pairs of components used in the refrigerants. The composition of each pair was varied over a range of relative percentages in the experimental evaluation, and the mixture parameters for each pair were regressed to the experimentally obtained data. The examples used known vapor / liquid equilibrium behavior data available in the National Institute of Science and Technology (NIST) Reference Fluid Thermodynamic and Transport Properties Database software (Refprop 9.1 NIST Standard Database 23 from April 2016). The parameters selected to perform the analysis were the same compressor volume for all refrigerants, the same operating conditions for all refrigerants, and the same compressor adiabatic efficiency and volumetric efficiency for all refrigerants. For each example, simulations were performed using measured vapor-liquid equilibrium data. Simulation results are reported for each example. [Table 6] Table 1: Refrigerants evaluated for performance examples Example 1: Performance of a Medium Temperature Refrigeration System with and without a Suction Line (SL) / Liquid Line (LL) Heat Exchanger (HX)

[0165] Performance tests were conducted on refrigerants A1-A8 in a medium temperature refrigeration system with and without a suction line / liquid line heat exchanger (SL / LL HX). This analysis was conducted to evaluate the efficiency (COP) of refrigerants A1-A8 in this system at different effectiveness levels of SL-LL HX under the following conditions:

[0166] The operating conditions were as follows: Condensation temperature = 45℃ Condensation temperature - ambient temperature = 10°C Condenser subcooling = 0.0°C (system with a receiver) Evaporation temperature = -8°C Evaporator superheat = 5.5℃ Compressor adiabatic efficiency = 65% Volumetric efficiency = 100% -Temperature rise in intake line = 10°C Intake line / liquid line heat exchanger heat exchange rate: 0%, 35%, 55%, 75% [Table 7] Table 2. Performance of a medium-temperature refrigeration system with SL / LL HX

[0167] Table 2 shows the performance of refrigerants in medium temperature refrigeration systems. The results under the column with "0%" efficiency for SL-LL HX represent a system without SL-LL HX, and it will be appreciated that refrigerants A1-A8 show improved performance over R134a in terms of efficiency (COP) when a SL / LL heat exchanger is used, with compositions A4, A4', and A4'' showing superior performance when all relevant performance factors are considered. Example 2: Performance of a low temperature refrigeration system with and without an air line / liquid line heat exchanger

[0168] Performance tests were conducted on refrigerants A1-A8 in a low-temperature refrigeration system with and without a suction line / liquid line heat exchanger (SL / LL HX). This analysis was conducted to evaluate the efficiency (COP) of refrigerants A1-A8 in this system at different effectiveness levels of SL-LL HX under the following conditions:

[0169] The operating conditions were as follows: Condensation temperature = 45℃ Condensation temperature - ambient temperature = 10°C Condenser subcooling = 0.0°C (system with a receiver) Evaporation temperature = -35°C, corresponding internal temperature = -25°C Evaporator superheat = 5.5℃ Compressor adiabatic efficiency = 65% Volumetric efficiency = 100% -Temperature rise in intake line = 10℃ Intake line / liquid line heat exchanger heat exchange rate: 0%, 35%, 55%, 75% [Table 8] Table 3. Performance of low-temperature refrigeration systems with SL / LL HX

[0170] Table 3 shows the performance of refrigerants in low-temperature refrigeration systems.

[0171] The results under the column with "0%" efficiency for SL-LL HX represent a system without SL-LL HX, and it will be appreciated that refrigerants A1-A8 show improved performance over R134a in terms of efficiency (COP) when a SL / LL heat exchanger is used, with compositions A4, A4' and A4'' showing superior performance when all relevant performance factors are considered. Example 3: Performance in a Medium Temperature Refrigeration System with Two-Stage Vapor Injected Compression

[0172] Performance tests were conducted on refrigerants A1 to A8 in a medium-temperature refrigeration system with two-stage vapor injection compression. This analysis was conducted to evaluate the efficiency (COP) of refrigerants A1 to A8 in this system under the following conditions:

[0173] The operating conditions were as follows: Condensation temperature = 45℃ Condensation temperature - ambient temperature = 10°C Condenser subcooling = 5.0℃ Evaporation temperature = -8°C, corresponding internal temperature = 1.7°C Evaporator superheat = 5.5℃ Compressor adiabatic efficiency = 70% Volumetric efficiency = 100% -Temperature rise in intake line = 10℃ Steam injection heat exchanger (HX) efficiency: 15%, 35%, 55%, 75% [Table 9] Table 4. Performance of a medium-temperature refrigeration system using two-stage compression with vapor injection

[0174] Table 4 shows the performance of the refrigerants in a medium temperature refrigeration system. Compositions A2 to A8 show improved performance over R134a in terms of efficiency (COP) in two-stage compression with vapor injection, while compositions A4, A4' and A4'' show superior performance when all relevant performance factors are considered. Example 4: Performance in a CO2 cascade refrigeration system

[0175] Cascade systems are typically used in applications where there is a large temperature difference (e.g., about 50-80°C, such as about 60-70°C) between the ambient temperature and the temperature inside the cabinet (e.g., the temperature difference between the air side of the condenser in the upper stage and the air side of the evaporator in the lower stage). For example, cascade systems may be used to freeze products in supermarkets. In the following examples, exemplary compositions of the invention were tested as refrigerants in the upper stage of a cascade refrigeration system. The refrigerant used in the lower stage of the system was carbon dioxide.

[0176] The operating conditions were as follows: Condensation temperature = 45℃ Upper stage condensation temperature - ambient temperature = 10°C Subcooling of high-stage condenser = 0.0°C (system with receiver) Evaporation temperature = -30°C, corresponding internal temperature = -18°C Low-stage evaporator superheat = 3.3°C High and low stage compressor adiabatic efficiency = 65% Volumetric efficiency = 100% -Temperature rise at low intake line = 15℃ -Temperature rise at high intake line = 10℃ Intermediate heat exchanger CO2 condensation temperature = 0℃, 5℃ and 10℃ ·Intermediate heat exchanger superheat = 3.3℃ Temperature difference at intermediate heat exchanger = 8°C [Table 10] Table 5. Performance of CO2 cascade refrigeration system

[0177] Table 5 shows the performance of the refrigerants in the high stages of a cascade refrigeration system. Refrigerants A1-A8 match the efficiency of R134a for different condensing temperatures in the low stage cycle, while compositions A4, A4', and A4'' show superior performance when all relevant performance factors are considered. Example 5: Performance in a Vending Machine with an Intake Line / Liquid Line Heat Exchanger

[0178] Performance tests were conducted on refrigerants A1-A8 in a vending machine refrigeration system with and without a suction line / liquid line heat exchanger (SL / LL HX). This analysis was conducted to evaluate the efficiency (COP) of refrigerants A1-A8 in this system at different effectiveness levels of SL-LL HX under the following conditions:

[0179] Operating conditions: Condensation temperature = 45℃ Condensation temperature - ambient temperature = 10°C Condenser subcooling = 5.5℃ Evaporation temperature = -8°C Evaporator superheat = 3.5℃ Compressor adiabatic efficiency = 60% Volumetric efficiency = 100% -Temperature rise in intake line = 5°C Intake line / liquid line heat exchanger heat exchange rate: 0%, 35%, 55%, 75% [Table 11] Table 6. Performance of vending machines with SL / LL HX

[0180] Table 6 shows the performance of refrigerants in vending machine systems with and without SL / LL HX. The results under the column with "0%" efficiency for SL-LL HX represent a system without SL-LL HX. It will also be seen that refrigerants A1-A8 show improved performance over R134a in terms of efficiency (COP) when a SL / LL heat exchanger is used, with compositions A4, A4', and A4'' showing superior performance when all relevant performance factors are considered. Example 6: Performance of an air-source heat pump hot water heater

[0181] Performance tests were conducted on refrigerants A1 to A8 in an air-source heat pump hot water heater system. This analysis was carried out to evaluate the efficiency (COP) of refrigerants A1 to A8 in this system under the following conditions.

[0182] The operating conditions were as follows: Condensation temperature = 55℃ ·Water inlet temperature = 45℃, water outlet temperature = 50℃ Condenser subcooling = 5.0℃ Evaporation temperature = -5℃, corresponding ambient temperature = 10℃ Evaporator superheat = 3.5℃ Compressor adiabatic efficiency = 65% Volumetric efficiency = 100% -Temperature rise in intake line = 5°C Intake line / liquid line heat exchanger heat exchange rate: 0%, 35%, 55%, 75% [Table 12] Table 7. Performance of heat pump hot water heaters

[0183] Table 7 shows the performance of the refrigerants in heat pump hot water heaters. Refrigerants A1 to A8 show similar efficiency to R134a, while compositions A4, A4', and A4'' show superior performance when all relevant performance factors are considered. Refrigerants A1 to A8 show lower discharge temperatures than R134a, indicating better compressor reliability. Example 7: Performance of an air-source heat pump hot water heater with an air-line / liquid-line heat exchanger

[0184] Performance tests were conducted on refrigerants A1-A8 in air-source heat pump hot water heater systems with and without suction line / liquid line heat exchangers (SL / LL HX). This analysis was conducted to determine the performance of refrigerants A1-A8 at different effectiveness levels of SL-LL HX under the following conditions: The efficiency (COP) of refrigerants A1 to A8 in this system was evaluated.

[0185] The operating conditions were as follows: Condensation temperature = 55℃ ·Water inlet temperature = 45℃, water outlet temperature = 50℃ Condenser subcooling = 5.0℃ Evaporation temperature = -5℃, corresponding ambient temperature = 10℃ Evaporator superheat = 3.5℃ Compressor adiabatic efficiency = 65% Volumetric efficiency = 100% -Temperature rise in intake line = 5°C Intake line / liquid line heat exchanger heat exchange rate: 0%, 35%, 55%, 75% [Table 13] Table 8. Performance of heat pump hot water heater with SL / LL HX

[0186] Table 8 shows the performance of refrigerants in a heat pump hot water heater with SL / LL HX. Refrigerants A1-A8 show higher efficiency than R134a when an SL / LL heat exchanger is used, and compositions A4, A4', and A4'' show superior performance when all relevant performance factors are considered. Refrigerants A1-A8 show lower discharge temperatures than R134a, indicating better compressor reliability. Example 8: Performance in mobile air conditioning systems (buses, trains, cars)

[0187] Performance tests were conducted on refrigerants A1 to A8 in a mobile air conditioning system under various condenser temperature conditions. This analysis was conducted to evaluate the efficiency (COP) of refrigerants A1 to A8 in this system under the following conditions:

[0188] Operating conditions: Condensation temperature: 45℃~75℃ Condenser subcooling = 5.0℃ Evaporation temperature = 4°C, corresponding indoor temperature = 35°C Evaporator superheat = 5.0℃ Compressor adiabatic efficiency = 65% Volumetric efficiency = 100% Temperature rise in intake line = 0°C [Table 14] Table 9. Performance in a mobile AC system

[0189] In Table 9, refrigerants A1 to A8 show similar efficiency to R134a over a range of condensing temperatures corresponding to different ambient temperatures, with compositions A4, A4' and A4'' showing superior performance when all relevant performance factors are considered. Example 9: Microcascade refrigeration system

[0190] A micro-cascade system combines a traditional medium temperature DX refrigeration system, with or without a suction line liquid line heat exchanger (SLHX) operating with fluid invention, with low temperature cascade refrigeration where the upper stage uses fluid invention and is connected to several smaller low temperature stages, using fluids such as, but not limited to, CO2, R1234yf, and R455A, in a self-contained form. As used herein, the term "medium temperature DX refrigeration system" refers to a medium temperature system where the evaporator is a dry evaporator.

[0191] Useful micro-cascade systems are disclosed in pending U.S. patent application Ser. Nos. 16 / 014,863, filed June 21, 2018, and 16 / 015,145, filed June 21, 2018, which claim priority to U.S. patent application Ser. Nos. 62 / 522386, filed June 21, 2017, 62 / 522846, filed June 21, 2017, 62 / 522851, filed June 21, 2017, and 62 / 522860, filed June 21, 2017, which are incorporated herein by reference in their entireties.

[0192] Operating conditions: The baseline R404A is a combination of the MT and LT systems. ●Refrigerated capacity ○Low temperature: 33,000W Medium temperature: 67,000W ●Volumetric efficiency: 95% for both MT and LT ●Compressor adiabatic efficiency Medium temperature = 70% and low temperature = 67% ●Condensing temperature=105°F Medium temperature evaporation temperature: 20°F Low temperature evaporation temperature: -20°F Evaporator superheat: 10°F (both medium and low temperatures) ●Intake line temperature rise (due to heat transfer to the surrounding area) Baseline: Medium temperature: 25°F, Low temperature: 50°F Self-contained without cascade / SLHX: Medium: 10°F, Low: 25°F Self-contained with Cascade / SLHX: Medium: 10°F, Low: 15°F SLHX efficiency in use: 65% [Table 15] Table 10 - Comparison of R404A and Micro Cascade Systems

[0193] The table above shows that the micro-cascade system has a COP that is approximately 126% higher than the baseline medium temperature DX system using R404A. Example 10: Non-flammable secondary refrigerant with pressure above atmospheric pressure

[0194] Refrigerants of the invention, including each of Refrigerants 1-7, or heat transfer compositions comprising refrigerants of the invention, including each of Refrigerants 1-7, can function as secondary fluids. Refrigerants of the invention, including each of Refrigerants 1-7, have the necessary properties to ensure that the operating pressure of the refrigerant does not fall below atmospheric pressure at a given evaporator temperature, so that air does not enter the system, while at the same time being low enough to prevent significant leakage. Table 11 shows the refrigerant pressures for evaporating temperatures ranging from -5°C to 10°C, covering a range of operating conditions for air conditioning applications. · It can be observed from the table that all the refrigerants maintain a pressure higher than atmospheric pressure. The primary refrigerant used in the vapor compression loop may be selected from the group consisting of R404A, R507, R410A, R455A, R32, R466A, R44B, R290, R717, R452B, R448A, R1234ze(E), R1234yf, and R449A. The temperature of the air (or object) to be cooled may be between about 25°C and about 0°C. [Table 16] Table 11: Secondary fluid Example 11: Performance in a fixed air conditioning system

[0195] Performance tests were conducted on refrigerants A1 to A8 in a stationary air conditioning system under various condenser temperature conditions. This analysis was conducted to evaluate the efficiency (COP) of refrigerants A1 to A8 in this system under the following conditions:

[0196] Operating conditions: Condensation temperature: 45℃~65℃ Condenser subcooling = 5.0℃ Evaporation temperature = 10°C, corresponding indoor temperature = 35°C Evaporator superheat = 5.0℃ Compressor adiabatic efficiency = 72% Volumetric efficiency = 100% [Table 17] Table 12. Performance in Stationary AC Systems

[0197] Refrigerants A1-A8 exhibit similar efficiencies to R134a over a range of condensing temperatures corresponding to different ambient temperatures, with compositions A4, A4' and A4'' exhibiting superior performance when all relevant performance factors are considered. Example 12: Performance in a commercial air conditioning system

[0198] Performance tests were conducted on refrigerants A1 to A8 in a commercial air conditioning system under various condenser temperature conditions. This analysis was conducted to evaluate the efficiency (COP) of refrigerants A1 to A8 in this system under the following conditions:

[0199] Operating conditions: Condensation temperature: 45℃~65℃ Condenser subcooling = 5.0℃ Evaporation temperature = 10°C Evaporator superheat = 5.0℃ Compressor adiabatic efficiency = 72% Volumetric efficiency = 100% [Table 18] Table 13. Performance in Stationary AC Systems

[0200] Refrigerants A1-A8 exhibit similar efficiencies to R134a over a range of condensing temperatures corresponding to different ambient temperatures, with compositions A4, A4' and A4'' exhibiting superior performance when all relevant performance factors are considered. Example 13: Performance in Transportation (Refrigerated Truck, Container) Refrigeration Applications with and without a Suction Line (SL) / Liquid Line (LL) Heat Exchanger (HX)

[0201] Performance tests were conducted on refrigerants A1-A8 in a transport refrigeration system with and without a suction line / liquid line heat exchanger (SL / LL HX) under medium temperature refrigeration conditions. This analysis was conducted to evaluate the efficiency (COP) of refrigerants A1-A8 in this system at different effectiveness levels of SL-LL HX under the following conditions:

[0202] The operating conditions were as follows: Condensation temperature = 45℃ Condensation temperature - ambient temperature = 10°C Condenser subcooling = 0.0°C (system with a receiver) Evaporation temperature = -8°C Evaporator superheat = 5.5℃ Compressor adiabatic efficiency = 65% Volumetric efficiency = 100% -Temperature rise in intake line = 15°C Intake line / liquid line heat exchanger heat exchange rate: 0%, 35%, 55%, 75% [Table 19] Table 14. Performance of a medium temperature refrigeration system with SL / LL HX

[0203] Table 14 shows the performance of refrigerants A1-A8 in a transport refrigeration system. The results under the column with "0%" efficiency for SL-LL HX represent a system without SL-LL HX, and it will be appreciated that refrigerants A1-A8 show improved performance over R134a in terms of efficiency (COP) when a SL / LL heat exchanger is used, with compositions A4, A4', and A4'' showing superior performance when all relevant performance factors are considered. Example 14: Performance in Transportation (Refrigerated Trucks, Containers) Refrigeration Applications with and without Intake Line / Liquid Line Heat Exchangers

[0204] Performance tests were conducted on refrigerants A1-A8 in a transport refrigeration system with and without a suction line / liquid line heat exchanger (SL / LL HX) under low temperature refrigeration conditions. This analysis was conducted to evaluate the efficiency (COP) of refrigerants A1-A8 in this system at different effectiveness levels of SL-LL HX under the following conditions:

[0205] The operating conditions were as follows: Condensation temperature = 45℃ Condensation temperature - ambient temperature = 10°C Condenser subcooling = 0.0°C (system with a receiver) Evaporation temperature = -35°C, corresponding internal temperature = -25°C Evaporator superheat = 5.5℃ Compressor adiabatic efficiency = 65% Volumetric efficiency = 100% -Temperature rise in intake line = 15°C Intake line / liquid line heat exchanger heat exchange rate: 0%, 35%, 55%, 75% [Table 20] Table 15. Performance of low temperature refrigeration systems with SL / LL HX

[0206] Table 15 shows the performance of refrigerants in low temperature refrigeration systems. The results under the column with "0%" efficiency for SL-LL HX represent a system without SL-LL HX, and it will be appreciated that refrigerants A1-A8 show improved performance over R134a in terms of efficiency (COP) when a SL / LL heat exchanger is used, with compositions A4, A4', and A4'' showing superior performance when all relevant performance factors are considered. Example 15: Electronic Cooling

[0207] Performance testing of Refrigerants A1-A8 is conducted to evaluate their use in cooling electronic devices, including cooling chips, electronic boards, batteries (including batteries used in automobiles, trucks, buses, and other electronic transportation vehicles), computers, and other electronic devices, including forms of heat pipes, thermosyphons, and vapor compression cooling. Analyses are performed to evaluate the performance of Refrigerants A1-A8 in these applications.

[0208] Refrigerants A1 to A8 perform similarly to R134a, with compositions A4, A4' and A4'' showing superior performance when all relevant performance factors are considered. The present invention includes the following aspects. [1] (a) an evaporator; (b) a refrigerant in the evaporator, the refrigerant being: (i) about 65% to about 90% by weight of HFO-1234ze(E); (ii) a refrigerant comprising about 10% by weight to about 35% by weight of HFO-1336mzz(E). [2] The heat transfer system according to [1], wherein the refrigerant consists essentially of the HFO-1234ze(E) and the HFO-1336mzz(E). [3] The heat transfer system according to [1], wherein the refrigerant comprises the HFO-1234ze(E) and the HFO-1336mzz(E). [4] The heat transfer system according to [1], wherein the refrigerant comprises approximately 65% ​​by weight to approximately 78% by weight of HFO-1234ze(E) and approximately 22% by weight to approximately 35% by weight of the HFO-1336mzz(E). [5] The heat transfer system according to [1], wherein the refrigerant further contains more than 0 to about 4.4 wt % HFC-227ea. [6] The heat transfer system according to [5], wherein the refrigerant consists essentially of the HFO-1234ze(E), the HFO-1336mzz(E), and the HFC-227ea. [7] The heat transfer system according to [1], wherein the refrigerant comprises about 74.6 to about 78.6 wt% HFO-1234ze(E), about 17 to about 21 wt% HFO-1336mzz(E), and about 4.4 wt% HFC-227ea. [8] (a) about 74.6 wt% to about 78.6 wt% HFO-1234ze(E); (b) about 17% to about 21% by weight of the HFO-1336mzz(E). [9] 10. The refrigerant of claim 8, consisting essentially of: (a) about 78.6 wt. % HFO-1234ze(E); (b) about 17 wt. % HFO-1336mzz(E); and (c) about 4.4 wt. % HFC-227ea.

[10] 10. The refrigerant of claim 8, consisting essentially of: (a) about 76.6 wt. % HFO-1234ze(E); (b) about 19 wt. % HFO-1336mzz(E); and (c) about 4.4 wt. % HFC-227ea.

[11] 10. The refrigerant of claim 8, consisting essentially of: (a) about 74.6 wt. % HFO-1234ze(E); (b) about 21 wt. % HFO-1336mzz(E); and (c) about 4.4 wt. % HFC-227ea.

[12] The refrigerant according to [9], consisting of HFO-1234ze(E), HFO-1336mzz(E), and HFC-227ea.

[13] The refrigerant according to

[10] , consisting of HFO-1234ze(E), HFO-1336mzz(E), and HFC-227ea.

[14] The refrigerant according to

[11] , consisting of HFO-1234ze(E), HFO-1336mzz(E), and HFC-227ea.

[15] 10. The refrigerant of claim 8, consisting essentially of: (a) 78.6 wt% + 0.5 wt% / - 2.0 wt% HFO-1234ze(E); (b) 17 wt% + 2.0 wt% / - 0.5 wt% HFO-1336mzz(E); and (c) about 4.4 wt% + 2.0 wt% / - 0.5 wt% HFC-227ea.

[16] 10. The refrigerant of claim 8, consisting essentially of: (a) 76.6 wt% + 0.5 wt% / - 2.0 wt% HFO-1234ze(E); (b) 19 wt% + 2.0 wt% / - 0.5 wt% HFO-1336mzz(E); and (c) about 4.4 wt% + 2.0 wt% / - 0.5 wt% HFC-227ea.

[17] 10. The refrigerant of claim 8, consisting essentially of: (a) 74.6 wt% + 0.5 wt% / - 2.0 wt% HFO-1234ze(E); (b) 21 wt% + 2.0 wt% / - 0.5 wt% HFO-1336mzz(E); and (c) about 4.4 wt% + 2.0 wt% / - 0.5 wt% HFC-227ea.

[18] A heat transfer composition comprising the refrigerant according to

[12] .

[19]

[18] The heat transfer system according to

[18] , including a chiller system.

[20]

[18] The heat transfer system according to

[18] , including a medium temperature cooling system. Numbered Embodiments

[0209] The present invention is further illustrated by the following numbered embodiments, the subject matter of which may be further combined with one or more subject matter of this specification or claims. 1. A refrigerant comprising: (a) about 65% to about 90% by weight of HFO-1234ze(E); and (b) about 10% to about 35% by weight of HFO-1336mzz(E). 2. The refrigerant of numbered embodiment 1, comprising: (a) about 76% to about 90% by weight of HFO-1234ze(E); and (b) about 10% to about 24% by weight of HFO-1336mzz(E). 3. The refrigerant of numbered embodiment 1 or 2, comprising: (a) about 74% to about 80% by weight of HFO-1234ze(E); and (b) about 20% to about 26% by weight of HFO-1336mzz(E). 4. The refrigerant of numbered embodiments 1-3, comprising: (a) about 76.6 wt.% HFO-1234ze(E); and (b) about 19 wt.% HFO-1336mzz(E). 5. The refrigerant of any one of numbered embodiments 1 to 4, consisting essentially of HFO-1234ze(E) and HFO-1336mzz(E). 6. The refrigerant of any of numbered embodiments 1 to 5, consisting of HFO-1234ze(E) and HFO-1336mzz(E). 7. A refrigerant comprising: (a) about 74.6% by weight to about 78.6% by weight of HFO-1234ze(E); (b) about 17% by weight to about 21% by weight of HFO-1336mzz(E); and (c) greater than 0% by weight to about 4.4% by weight of HFC-227ea. 8. The refrigerant of numbered embodiment 7, comprising: (a) 74.6% to 78.6% by weight of HFO-1234ze(E); (b) 17% to 21% by weight of HFO-1336mzz(E); and (c) about 4.4% by weight of HFC-227ea. 9. The refrigerant of numbered embodiment 8, comprising: (a) about 78.6 wt.% HFO-1234ze(E); (b) about 17 wt.% HFO-1336mzz(E); and (c) about 4.4 wt.% HFC-227ea. 10. Numbered embodiments 1-9 comprising about 4.4 wt. % HFC-227ea The refrigerant according to any one of the preceding claims. 11. The refrigerant of any one of numbered embodiments 1 to 10, consisting essentially of HFO-1234ze(E), HFO-1336mzz(E), and HFC-227ea. 12. The refrigerant of any one of numbered embodiments 1 to 10, consisting of HFO-1234ze(E), HFO-1336mzz(E), and HFC-227ea. 13. The refrigerant of any one of numbered embodiments 1-12, having a global warming potential of about 150 or less. 14. The refrigerant of any one of numbered embodiments 1 to 13, wherein the refrigerant is non-flammable. 15. The refrigerant of any one of numbered embodiments 1 to 14, wherein the refrigerant is non-toxic or has low toxicity. 16. The refrigerant of any one of numbered embodiments 1-15, wherein the refrigerant has a gradient of less than about 3°C, preferably less than about 2°C. 17. A heat transfer composition comprising a refrigerant according to any of numbered embodiments 1-16. 18. The heat transfer composition of numbered embodiment 17, comprising a refrigerant in an amount of at least about 80% by weight of the heat transfer composition, preferably at least about 90% by weight of the heat transfer composition, more preferably at least about 97% by weight of the heat transfer composition, and more preferably at least about 99% by weight of the heat transfer composition. 19. The heat transfer composition of numbered embodiment 17 or 18, further comprising a lubricant. 20. The heat transfer composition of numbered embodiment 19, wherein the lubricant is present in the heat transfer composition in an amount from about 1% to about 50% by weight of the heat transfer composition, more preferably from about 10% to about 50% by weight of the heat transfer composition, and most preferably from about 30% to about 50% by weight of the heat transfer composition. 21. The heat transfer composition of numbered embodiment 19 or 20, wherein the lubricant is selected from the group consisting of polyol esters (POEs), polyalkylene glycols (PAGs), PAG oils, polyvinyl ethers (PVEs), poly(α-olefins) (PAOs), and combinations thereof. 22. The heat transfer composition of numbered embodiment 19 or 20, wherein the lubricant is POE or PVE, preferably the lubricant is POE. 23. A method of heating or cooling a fluid or object using a refrigerant as defined in any of numbered embodiments 1-16 or a heat transfer composition as defined in any of numbered embodiments 17-22. 24. A vapor compression system having an evaporator, a condenser, and a compressor in fluid communication, the vapor compression system comprising a refrigerant as defined in any of numbered embodiments 1-16, or a heat transfer composition as defined in any of numbered embodiments 17-23. 25. A refrigeration system comprising a refrigerant as defined in any of numbered embodiments 1-16, or a heat transfer composition as defined in any of numbered embodiments 17-23. 26. The refrigeration system of numbered embodiment 25, wherein the system is a medium-temperature refrigeration system. 27. The refrigeration system of numbered embodiment 26, wherein the medium temperature refrigeration system has an evaporator temperature of about -15°C to about 5°C, preferably about -10°C to about 5°C. 28. The refrigeration system of numbered embodiment 26 or 27, wherein the medium-temperature refrigeration system is selected from a small refrigeration system (including vending machines, ice makers, and household appliances), a commercial refrigeration system (such as supermarket refrigeration systems and walk-in coolers), a residential refrigeration system, and an industrial refrigeration system. 29. The medium-temperature refrigeration system has an evaporator temperature of about 0°C to about 5°C. 29. A refrigeration system as described in embodiment 28. 30. The refrigeration system of numbered embodiments 26-29, wherein the medium temperature refrigeration system is used to cool perishable produce, including vegetables and / or fruits, or is used to cool beverages. 31. The refrigeration system of numbered embodiments 26-30, wherein the medium temperature system has a condenser temperature of about 15°C to about 60°C, preferably about 25°C to about 45°C. 32. A refrigeration system according to numbered embodiments 26 to 31, wherein the medium temperature system has a superheat of about 0°C to about 10°C at the evaporator outlet, preferably about 1°C to about 6°C at the evaporator outlet. 33. A refrigeration system according to numbered embodiments 26 to 32, wherein the medium temperature system has a superheat of about 3°C ​​to about 5°C at the evaporator outlet, preferably about 4°C at the evaporator outlet. 34. The refrigeration system of numbered embodiment 25, wherein the system is a low-temperature refrigeration system. 35. The refrigeration system of numbered embodiment 34, wherein the low temperature refrigeration system has an evaporator temperature of about -45°C to less than about -15°C, preferably about -40°C to about -25°C. 36. The refrigeration system of numbered embodiment 34 or 35, wherein the low-temperature refrigeration system is selected from a skating rink, a commercial refrigerator system (including supermarket refrigerators), a residential refrigerator system, and an industrial refrigerator system. 37. The refrigeration system of any one of numbered embodiments 34 to 36, wherein the low-temperature refrigeration system is used to cool refrigerated produce. 38. The refrigeration system of numbered embodiments 34 to 37, wherein the low-temperature system has a condenser temperature of about 15°C to about 50°C, preferably about 25°C to about 45°C. 39. The refrigeration system of numbered embodiments 34 to 38, wherein the low-temperature system has a superheat of about 0°C to about 10°C, preferably about 1°C to about 6°C, at the evaporator outlet. 40. The method of numbered embodiment 25, wherein the system is a transport refrigeration system. 41. The refrigeration system of numbered embodiment 40, wherein the transport refrigeration system is a container transportable by ship, boat, rail car, or road vehicle (e.g., truck). 42. The refrigeration system of numbered embodiment 25, wherein the system is a cascade refrigeration system. 43. The refrigeration system of numbered embodiment 42, wherein the cascade refrigeration system has an upper and a lower tier, and wherein the refrigerant defined in any of numbered embodiments 1-16 or the heat transfer composition defined in any of numbered embodiments 17-22 is used in the upper tier. 44. The refrigeration system of numbered embodiment 43, wherein CO2, 1234yf, or R455A is used in the lower stage of the cascade refrigeration system. 45. A secondary loop system comprising a refrigerant as defined in any of numbered embodiments 1-16, or a heat transfer composition as defined in any of numbered embodiments 17-22. 46. ​​The secondary loop system of numbered embodiment 45, wherein the secondary loop system includes a primary vapor compression system loop using a primary refrigerant and an evaporator cooling a secondary loop fluid, and wherein the refrigerant defined in any of numbered embodiments 1 to 16 or the heat transfer composition defined in any of numbered embodiments 17 to 22 is used as the secondary loop fluid. 47. The primary refrigerant is R404A, R507, R410A, R455A, R32, R466A, R44B, R290, R717, R452B, R448A, or R1234ze (E), R1234yf, and R449A. 48. A heat pump system comprising a refrigerant as defined in any of numbered embodiments 1-16, or a heat transfer composition as defined in any of numbered embodiments 17-22. 49. The heat pump system of numbered embodiment 48, wherein the heat pump is a heat pump tumble dryer, a reversible heat pump, a high temperature heat pump, or an air-to-air heat pump. 50. An air conditioning system comprising a refrigerant as defined in any of numbered embodiments 1-16, or a heat transfer composition as defined in any of numbered embodiments 17-22. 51. The air conditioning system of numbered embodiment 50, wherein the system is selected from chillers, residential, industrial, commercial, and mobile air conditioning. 52. The air conditioning system of numbered embodiment 51, wherein the mobile air conditioning system includes air conditioning for road vehicles such as cars, trucks, and buses, as well as air conditioning for boats and trains. 53. The system of any one of numbered embodiments 24 to 52, wherein the system includes an intake line and a liquid line heat exchanger. 54. An organic Rankine cycle system comprising a refrigerant as defined in any of numbered embodiments 1-16, or a heat transfer composition as defined in any of numbered embodiments 17-22. 55. A method for cooling a fluid or object using a refrigeration system, the method comprising: (a) evaporating a refrigerant as defined in any of numbered embodiments 1-16 in the vicinity of the fluid of the object to be cooled; and (b) condensing the refrigerant. 56. The method of numbered embodiment 55, wherein the refrigeration system is a medium-temperature refrigeration system. 57. The method of numbered embodiment 56, wherein the medium temperature refrigeration system is as defined in any of numbered embodiments 26 to 33. 58. The method of numbered embodiment 55, wherein the refrigeration system is a low-temperature refrigeration system. 59. The method of numbered embodiment 58, wherein the medium temperature refrigeration system is as defined in any of numbered embodiments 34 to 39. 60. The method of numbered embodiment 55, wherein the refrigeration system is a transport refrigeration system. 61. The method of numbered embodiment 60, wherein the transport refrigeration system is as defined in numbered embodiment 40. 62. The method of numbered embodiment 55, wherein the refrigeration system is a cascade refrigeration system. 63. The method of numbered embodiment 62, wherein the cascade refrigeration system is as defined in any of numbered embodiments 42 to 44. 64. A method for cooling a fluid or object using a secondary loop system, the method comprising: (a) evaporating a primary refrigerant around a secondary loop fluid to transfer heat from the secondary loop fluid to the primary refrigerant; (b) condensing the primary refrigerant; and (c) circulating the secondary loop fluid through a secondary loop, thereby absorbing heat from the fluid or object to be cooled, wherein the secondary loop fluid is a refrigerant as defined in any of numbered embodiments 1-16 or a heat transfer composition as defined in any of numbered embodiments 17-22. 65. The primary refrigerant is R404A, R507, R410A, R455A, R32, R466A, R44B, R290, R717, R452B, R448A, or R1234ze (E), R1234yf, and R449A. 66. A method of heating a fluid or object using a heat pump, the method comprising: (a) condensing a refrigerant as defined in any of numbered embodiments 1-16 in the vicinity of a fluid in the object to be heated; and (b) evaporating the refrigerant. 67. The method of numbered embodiment 66, wherein the heat pump is a heat pump tumble dryer, a reversible heat pump, a high temperature heat pump, or an air-to-air heat pump. 68. A method of air conditioning using an air conditioning system, the method comprising: (a) evaporating a refrigerant as defined in any of numbered embodiments 1-16 in the vicinity of a fluid of a body to be cooled; and (b) condensing the refrigerant. 69. The method of numbered embodiment 68, wherein the system is as defined in any of numbered embodiments 50 to 52. 70. A process for converting thermal energy to mechanical energy in a Rankine cycle, the process comprising: i) vaporizing a working fluid at a heat source and expanding the resulting vapor, or vaporizing the working fluid at a heat source; and then ii) cooling the working fluid at a heat sink to condense the vapor, wherein the working fluid is a refrigerant as defined in any of numbered embodiments 1-16 or a heat transfer composition as defined in any of numbered embodiments 17-22. 71. The process of numbered embodiment 70, wherein the heat source is provided by a low-grade thermal energy source selected from industrial waste heat, solar energy, geothermal hot water, low-pressure steam, a distributed power generation system utilizing a fuel cell, or a prime mover. 72. The process of numbered embodiment 70 or 71, wherein the heat source is provided by a turbine, a microturbine, or an internal combustion engine. 73. The process of numbered embodiment 72, wherein the low-pressure steam is low-pressure geothermal steam or is provided by a fossil fuel-powered power plant. 74. The process of numbered embodiments 70-73, wherein the heat source temperature is from about 80°C to about 800°C or higher. 75. A heat transfer system for cooling an electronic device, comprising: a refrigerant as defined in any of numbered embodiments 1-16; or a heat transfer composition as defined in any of numbered embodiments 17-23. 76. The heat transfer system of claim 75 used to cool one or more of electronic chips, electronic boards, batteries (including batteries used in automobiles, trucks, buses, and other electronic transportation vehicles), computers, and the like. 77. A heat transfer system according to any one of claims 75 and 76, comprising a form of heat pipe or thermosiphon.

Claims

1. (i) 74.6 wt% to 78.6 wt% HFO-1234ze(E); (ii) 17 wt% to 19 wt% HFO-1336mzz(E); and (iii) 4.4 wt. % HFC-227ea; and 10. Use of a heat transfer composition comprising a refrigerant comprising the compound in a heat transfer system.

2. 2. The use according to claim 1, wherein the heat transfer system is a medium temperature refrigeration system.

3. 3. The use of claim 2, wherein the medium temperature refrigeration system is selected from small refrigeration systems (including vending machines, ice makers, and household appliances), commercial refrigeration systems (such as supermarket refrigeration systems and walk-in coolers), residential refrigeration systems, and industrial refrigeration systems.

4. 3. The use of claim 2, wherein the medium temperature refrigeration system has an evaporator temperature of -15°C to 5°C.

5. 5. The use of claim 4, wherein the medium temperature refrigeration system has an evaporator temperature of -10°C to 5°C.

6. The use according to claim 1 , wherein the heat transfer system is an air conditioning system.

7. 10. The use of claim 1, wherein the air conditioning system is selected from chillers, residential, industrial, commercial, and mobile air conditioning.

8. The use according to claim 1 , wherein the heat transfer system is a heat pump system.

9. 2. The use according to claim 1, wherein the heat transfer system is a heat pump tumble dryer, a reversible heat pump, a high temperature heat pump, or an air-to-air heat pump.

10. 2. The use of claim 1, wherein the heat transfer system is a transport refrigeration system.

11. 2. The use according to claim 1, wherein the heat transfer system is a cascade refrigeration system.

12. The use according to claim 1 , wherein the heat transfer system is a system for cooling electronic equipment.

13. The use according to claim 12, wherein the electronic device is selected from one or more of an electronic chip, an electronic board, a battery, and a computer.

14. 14. The use of any of claims 1 to 13, wherein the heat transfer composition further comprises a lubricant selected from the group consisting of polyol esters (POEs), polyalkylene glycols (PAGs), PAG oils, polyvinyl ethers (PVEs), poly(α-olefins) (PAOs), and combinations thereof.

15. 15. The use according to claim 14, wherein the lubricant is POE or PVE.

16. 16. The use according to claim 15, wherein the lubricant is POE.

17. 17. A method of replacing an existing heat transfer fluid in an existing heat transfer system, comprising the step of replacing at least a portion of the existing heat transfer fluid in the existing heat transfer system with the heat transfer composition of any one of claims 1 to 16, wherein the existing heat transfer fluid comprises R134a or R404A.

18. Use of a heat transfer composition to replace R134a or R404A refrigerants, wherein the heat transfer composition is a heat transfer composition according to any one of claims 1 to 16.

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