Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
  • F02C1/00—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid
  • F02C1/04—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly
  • F02C1/10—Closed cycles
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
  • F02C1/00—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid
  • F02C1/04—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly
  • F02C1/10—Closed cycles
  • F02C1/105—Closed cycles construction; details
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
  • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
  • F02C7/08—Heating air supply before combustion, e.g. by exhaust gases
  • F02C7/10—Heating air supply before combustion, e.g. by exhaust gases by means of regenerative heat-exchangers

Definitions

• the invention relates to a thermodynamic cycle that evolves according to a Brayton cycle, in which the temperature of the hot focus and that of the cold focus, which is the environment, the hydrosphere, the atmosphere, is especially taken into account. Its use is of relevant interest in the energy industry, particularly when the calorific focus is of reduced temperatures compared to usual in chemical combustion plants. This makes it especially applicable to solar thermal or geothermal energy. It may also be applicable as a low temperature cycle that collects excess heat from a high temperature cycle.
• Thermodynamic cycles of the Brayton type are widely known in the state of the art.
• the background of this cycle is found in US patent US 125 166 A, requested by George B. Brayton in 1872.
• This document presented the evolution of a fluid in a piston machine;
• the ideal cycle consists of: 1) the isentropic compression of a fluid, 2) heat supply at constant pressure, 3) isentropic expansion of the fluid, and 4) heat transfer at constant pressure until returning to the initial conditions.
• the Brayton cycle has been used with great profusion in energy applications, being the theoretical basis of gas turbines.
• Thermodynamic cycles for obtaining power using fluids that are in thermally supercritical state throughout the cycle are known in the state of the art, that is, they do not fall below the critical temperature T cr and therefore do not suffer condensation, even partially, which is distinctive of the Brayton cycles.
• the concept of the Brayton extends to the so-called regenerative cycles, in which the turbine outlet temperature is higher than the compressor outlet, so that it is convenient to transfer the excess heat of the fluid to the turbine outlet, and therefore in the low pressure branch, to the high pressure fluid, after the compressor outlet, before receiving it the heat input from the hot spot of the installation.
• EP 1 801 364 A1 which refers to a thermodynamic cycle, Rankine type, which evolves during turbine expansion at temperatures above the critical isotherm, although afterwards the fluid evolves within the biphasic bell , the condensation taking place until the saturated liquid phase, and from there evolving by means of a pumping to the boiler pressure and its entrance in turbine. Therefore, unlike the invention presented here, the working fluid of EP 1 801 364 A1 undergoes phase changes.
• US7926276 describes a regenerative closed Brayton cycle whose originality resides in the heat source, with a molten metal and an oxidant, but does not prescribe any thermodynamic conditions for the cycle.
• WO20011018663 discloses another type of closed Brayton, with positive displacement machines, without specifications for the cold spot or for the regenerative phase of internal heat recovery.
• Document US2009308072 describes an open Brayton, based on the novelty in the use of solar energy to activate the extraction of hydrogen from a hydride, to be used in a combustion chamber.
• Application US2011113780 describes a closed Brayton that uses C0 2 as a working fluid, but using a heat recuperator as a cold source to power a Rankine cycle, so it is a combined cycle, similar to the usual ones, but with a cycle closed.
• thermodynamic description of the Brayton-type cycles is given below, with special attention to those who use ideal gas as a working fluid, as they are the most widespread, being air, or a similar combination, the working fluid in question, which evolves at temperatures above the critical, without phase change (which can be easily visualized in a Ph, enthalpy-pressure, or TS, entropy-temperature diagram).
• the dominant Brayton cycle is that of gas turbines, both of electric power generation and propulsion, mainly aeronautical, and in them the low isotonic pressure is atmospheric, because the exhaust is open to the atmosphere, and likewise the oxidizing air is taken from the atmosphere, being really an open cycle.
• the maximum temperature of the cycle at the end of the isobar above, before the expansion in the turbine, it reaches several hundreds of degrees above 1000 ° C, and at the exit of the turbine the exhaust gas still has very high temperatures, of 500 ° C and more, that is, very above ambient temperatures.
• this heat is used, in the so-called combined cycles, by thermally feeding a Rankine cycle of water / steam with the exhaust gases of the Brayton.
• the common theoretical limit of the regenerative and non-regenerative cases is when the compressor outlet and turbine outlet temperatures coincide, which will be called the adjusted case, which thus serves as a common reference.
• the compressor outlet temperature can be selected so that it is higher than that of the adjusted case, for which a pressure ratio must be used, between the high pressure P a and the low pressure P b , greater than the pressure ratio of the adjusted case.
• an upper limit which is that of the maximum temperature T M that the working fluid can achieve depending on the hot spot available.
• T n has already been called at the lowest temperature that the working fluid acquires, depending on the cold focus.
• the non-regenerative closed cycle is ideally defined by two isóbaras and two isentrópicas, with the following phases:
• the cold spot is constituted by an exchanger, through whose primary circuit the working fluid circulates, and through which secondary the external refrigerant circulates, the atmosphere or hydrosphere being the ultimate sink of that heat; with a variety of devices that can perform outside cooling.
• Isentropic compression from point C, which is the lowest T of the low isotary P, to the high isotary P, calling point D, at the end of that compression, which is the point of least T at that isóbara high of the cycle. Compression is performed on a compressor, selected to fit the compression ratio set.
• Essential heat input from at least one heat source, such as a solar energy sensing device, or a
• heat exchanger whose primary is the combustion of any fuel, be it biomass, fossil fuel, etc. This contribution occurs along the isotary line of high P, from point D to point A.
• the cycle can be given a more general character assuming that compression and expansion are not exactly isentropic, but polytropic, with coefficients
• the yield ⁇ of the cycle can be defined as a function of the specific enthalpies of the fluid, according to the expression
• the yield depends on the variation of the thermodynamic properties in the general pressure-temperature domain (P, T) although other representations may be used.
• the expression of these properties is useful in a diagram (h, P) of coordinates "specific enthalpy" (h, in abscissa) and "pressure” (P, in ordinates), since thermal exchanges are measured in enthalpy variations , and the work of the machines, either negative or consumed (in the compressor machines) either positive or performed outward (in the expanding machines) is also measured in enthalpy variations.
• Ah c to the increase in specific enthalpy in the working fluid as it passes through the compressor, and m 'to the mass flow of working fluid, the mechanical power N c consumed by it is
• the transformation is considered to be isentropic, which makes the forms acquired by the isentropic lines on the map (h, P), or in any other thermodynamic diagram, of utmost importance. to define the cycle prescriptions.
• the ideal gas evolves along a line of constant entropy, S t, falling from the high pressure P to the low D; reducing the enthalpy of the fluid, which is converted into power applied to the axis of the machine.
• power is applied to its axis so that the fluid gains enthalpy, and passes from the low pressure P b to the high pressure P a along a constant entropy line S c . So, the equation of the useful power on the axis can be written
• N m ' ⁇ ⁇ (óh / óP) st - (5h / 5P) Sc ⁇ dP
• the integral of the right member extends from the low pressure P to the high pressure P a , which gives an idea of the importance of the first derivative of the integrand being greater than the second.
• the slope of the isentropic expansion must be greater than that of compression so that useful work can be obtained on the axis of the machine.
• isotherms are important, since temperatures are related to the heat input in the heat source, and cooling in the cold source. Isotherms are therefore essential lines to define the boundary conditions in which the cycle has to be moved. It should be noted that, due to the irreversibility of any real thermodynamic evolution and that takes place in a finite time, the above-mentioned evolution of the cycle does not correspond exactly to isobars, when they have been defined as such, since the pressure is decreasing to some extent throughout that phase, neither areentropics are such, as entropy is growing. These effects will be taken into account when it comes to specific applications, since they depend heavily on the machines and circuits used to move the fluid; but to define the cycle, and even give prescriptions on its thermodynamic parameters, its theoretical definition will be used.
• the expansion and compression phases could be better adjusted by means of polytropic transformations with exponents adjusted to the real evolutions; but when these exponents vary from one machine to another, the formulation must be made in the theoretical representation of the isentropics, depending on the ⁇ coefficient, for the case of ideal gas, or of k, for those of non-ideal behavior.
• the power of the external heat input in the hot spot is called Q ', and its specific enthalpy variation is called Ah q , the expression of Q' being in watts
• a power of the extraction, to the atmosphere or hydrosphere, of the heat in the cold focus is called E ', and to its variation of specific enthalpy (in absolute value) we call it Ah e , being the expression of E'
• the useful power is proportional to the difference (Ah t - Ah c ) while the specific enthalpy variation to maintain the cycle is the increase from its lowest enthalpy point, at the exit of the cold focus, to the enthalpy point. higher, at the exit of the hot spot, which can be expressed, in absolute values of enthalpy variations, such as
• the regenerative closed cycle is ideally defined by two isobars and two isentropics, with the following phases, taking into account that two significant points appear in the cycle more, so that all are renumbered as follows:
• point 05 passing the fluid from point 102 to the exit point of said exchanger, which is called point 103, which is in the low line P, the temperature of the point being 103 equal to or greater than the T of the compressor exit point, at the end of phase 4 (referred to as point 05).
• the cold spot is constituted by an exchanger, through whose primary circuit the working fluid circulates, and through which secondary the external refrigerant circulates, the atmosphere or hydrosphere being the ultimate sink of that heat; with a variety of devices that can perform outside cooling.
• Isentropic compression from point 104, which is the lowest T of the low isotary P, to the high isotary P, point 105 being the one that designates the compressor output. Compression is done in a compressor, selected to match the rate of compression set, denominating S c to the entropy of the isentropic.
• regenerative heat exchanger passing the fluid from point 105 to point 106 along the high P line, and the temperature of point 106 being equal to or less than the T of the exit point of the expander machine, at the end of the phase 1 (point 102).
• the point named 106 is the exit point of the regenerative heat exchanger, in the high P circuit. In the ideal cycle, the enthalpy gained in this phase (h106 -h105) is equal to that lost in phase 2, (h102 - h103).
• Essential heat input from at least one heat source, such as a solar energy sensing device, or a heat exchanger whose primary is the combustion of any fuel, be it biomass, fossil fuel, etc. This contribution occurs along the high P isotary line, from point 106 to point 101.
• a heat source such as a solar energy sensing device, or a heat exchanger whose primary is the combustion of any fuel, be it biomass, fossil fuel, etc. This contribution occurs along the high P isotary line, from point 106 to point 101.
• the yield ⁇ of the cycle can be defined as
• N m'- ⁇ ⁇ ⁇ - V Sc ⁇ dP
• the invention consists in taking advantage of the specificities of some fluids to operate a closed Brayton cycle, operating under pressure conditions that optimize its operation for temperature conditions given in the hot and cold foci, characterized by the values and T N. This will take into account not only the ordinary energy efficiency, but what it costs to generate the unit of energy, including all the components that constitute the cycle, measured in enthalpy terms and also measured with the economic weighting corresponding to each component, which leads to express the invention in terms of selecting the fluid based on its thermodynamic critical point, and also selecting the operating isobars, and starting points of each phase of the cycle.
• the invention consists in selecting a working fluid that has a thermodynamic zone close to the critical one, which we call peri-critical, in which is the isotherm of T n , which, like all isotherms in said zone, it presents in the enthalpy-pressure diagram a turning point as a consequence of the high values of the specific heat at constant pressure that are inherent in that area, particularly for the critical isobar.
• the isotherms In the inflection points that the isotherms present in said peri-critical zone, the isotherms have a section that is substantially parallel to the isobars, and therefore perpendicular to the isenthalpic; when the usual behavior of isotherms, understood as the ideal gas, is that they are practically perpendicular to the isobars. This effectively occurs at pressures above the peri-critical zone, also being at pressures below the peri-critical zone. For this reason, the isotherms present in each case, up and down, two arcs similar to a quarter of a circle, which lead from the ideal or similar gas behavior zones, to the inflection points that each isotherm presents in the area peri-criticism
• T high T low -c (k - 1) / k
• T D T n - C ⁇ K "1 > / K
• the invention requires that the selected fluid provide a useful power greater than that of an ideal gas cycle with equal T n and T M , the useful power being the product of the performance by the power contributed in the heating. That is, the difference
• thermodynamic properties in the peritic zone these properties being the following: - That, along any iséntalpica of that thermodynamic zone, C p increases with increasing pressure.
• the adjusted cycle has no degrees of freedom in its definition, except for the choice of low (or high) pressure, since T n and T M are the boundary conditions defined for that application.
• the regenerative cycles, of which the adjusted one is a limiting case allow a degree of freedom that is fundamental to obtain the best results in each case that is specified.
• n 1 -T n (zs-1) / (T M (1 -zs))
• the adjusted case is the one that produces the greatest useful power in the cycle, in spite of being the one with the worst performance, and this is because it is the one that accepts more heat from the hot spot, for given contour conditions, expressed by T n and T M.
• the invention prescribes, in a first basic formulation, the use of an adjusted Brayton cycle, located in the peri-critical zone, fulfilling that
• the selected working fluid must fulfill that, within the thermodynamic enclosure between the temperatures T n and T M , and the selected pressures of low, P b and high, P a , the average value, between T n and T M , of the specific heat at constant pressure, C p , for an isobar, increases with increasing pressure.
• the invention delves into the degree of freedom that exists in the regenerative cycles, which qualitatively can be explained as follows: to pass in the cycle from the isotherm T n to the T M , one can go by way of the maximum possible compression ratio, which is that of the adjusted case, which does not require regenerative heat exchange; or a path of less compression ratio can be chosen, and the smaller this one, the greater the enthalpy variation caused by the regenerative exchange of heat.
• thermo solar energy since the hot spot is a field of solar light concentrators focused on receivers that are cooled by a fluid that can be the same as the cycle fluid, or different, and from which the fluid is heated T / ES2013 / 000071
• the ideal gas case is presented as a working fluid in the regenerative cycles, to then be transferred to the real fluids in the own peri-critical zone.
• a fluid for example C0 2 , which extends from 10 bar to 150 bar, and from 31 ° C to 400 ° C, approximately, another fluid, such as N 2 , can have an ideal behavior, which allows to compare the real case and the ideal, in the same thermodynamic domain.
• Heating / expansion Q C P (T M - T M / x)
• Cooling / compression E C p (T n x - T n )
• Regenerative exchange G C p (T M / x - T n x)
• the innovation in its full version identifies the peri-critical area of selected work fluids, as the ideal one to exploit this type of cycles with real gases, taking advantage of the characteristics already stated about C p and the phenomenological coefficient k in relation to evolution of temperature and pressure along an isentropic; for which the following analysis is formulated, from which the formulation of the innovation will be extracted in a more complete version.
• C ' p (which disappears in the quotient) has been used because the one that dominates the benefits of the exchanger, and limits them, is the fluid that changes the most temperature, and that is the one with the lowest specific heat.
• the peri-critical zone is defined not only in P but also in T, and for values of T greater than double of the T Cr (in K) this zone can be considered finished, and the value of C p is constant.
• the isobars will have an average value of C p higher than the average value in the isobars outside that zone. The average value of C p is obtained by dividing the enthalpy increase along an isobar, between two temperatures that delimit the area, by said increase in temperatures.
• the peri-critical zone is delimited in a temperature domain that ranges from the critical temperature T Cr plus an increase in delimitation, ⁇ , selected between 1 K and 40 K, and an end zone temperature, Ttin whose value is Select between 1.5 times T Cr and 3 times T Cr , always measured in absolute temperature scale;
• the perimeter zone being delimited in pressure between the isobars of one fifth of the critical pressure, P Cr , and five times said critical pressure;
• this isóbara supreme being the isóbara that is selected as the isóbara of discharge of the cycle; setting the isobar of low for providing the maximum of a real utility function, which corresponds to a reason in which the numerator is the specific net work of the cycle
• Figure 1 shows a thermodynamic diagram (h, P) in which the peri-critical zone of carbon dioxide, C0 2 , showing the specific enthalpy in J / kg, and in ordinates the pressure, in bar. It also represents the critical isotherm and a set of nearby isotherms, as well as the two-phase liquid-vapor hood, and several isentropic lines, in short dashed lines, and several isocoras, in long dashed lines.
• Figure 2 shows the scheme of a generic diagram (h, P) in which five different cycles have been included, four of them classic, and another in which the invention is applied.
• Figure 3 shows an ideal regenerative cycle with its main thermodynamic points, in a diagram of a diagram (h, P), two isotherms being indicated by dashed lines.
• Figure 4 shows a diagram of the components necessary to materialize a regenerative cycle, with its essential thermodynamic points.
• Figure 5 shows another scheme of the components of the cycle, including components for its control, especially barometric.
• Figure 6 shows a diagram of a regenerative cycle fed by the excess heat of a Brayton with combustion chamber, and therefore, with a lot of thermal energy in the exhaust gases.
• Compressor intake manifold, or compressor 16.
• Compressor machine or compressor.
• High pressure fluid outlet of the heat exchanger for essential heat, or heat source.
• Partial shut-off valve located in the compressor supply line.
• Compressor of a higher temperature Brayton cycle to which the cycle of the invention is coupled to take advantage of the heat of the exhaust gases of its gas turbine.
• Thermodynamic cycle of the invention represented in a diagram (h, P). 101. Thermodynamic point of exit of the heat source and entry into the expansion machine.
• the invention requires identifying fluids that meet the requirements set forth in the prescriptions of the invention; which affect the critical temperature, which must be between 0 ° C and T r + ⁇ ,.
• T r varies considerably with the geographical location, but a set of fluids to consider, as candidates of the invention, is that of table 2
• T r can be taken 30 ° C.
• ⁇ its value will depend on whether it is cooled with water or with air, since its film coefficient is much lower than that of water, and therefore its difference ⁇ , will have to be older.
• the range between 5 and 20 ° C for water, and between 20 and 40 ° C for air can be given, with advisable values of 10 ° C for water and 25 ° C for air. This leads us to values of T min of 40 ° C and 55 to C respectively.
• Ethane can be used, but it has the disadvantage of its flammability.
• C0 2 and R116 ethyl hexafluoride
• T r or AT t or both were taken, R125, R32 and even R134a could be used.
• Table 3 lists the values of C p for C0 2 in its peri-critical zone Pressure C p (kJ / kg.K)
• the invention actually materializes on non-ideal components, which suffer irreversibility (in particular, machines) that have finite size (in particular, heat exchangers) and that have a finite time for the corresponding phase to be executed. of the cycle, which also causes non-ideal evolutions.
• the ideal option is that it is the isobar called supreme, represented by its pressure P sup , in which the derivative of the average value of C p in that isobar, with respect to the compression ratio measured with respect to the critical pressure, acquires the highest value of all isobars in that area.
• the values of the derivative are given below for various pressures, with C pm being the average value of the specific heat at constant pressure in the isobar in question, and c c the ratio between the pressure in question and the critical pressure.
• C pm being the average value of the specific heat at constant pressure in the isobar in question
• c c the ratio between the pressure in question and the critical pressure.
• that derivative is worth 0.265 (in kJ / kg-K); goes up to 0.300 for 70 bar; reaches a maximum of 0.35 for 130 bar; and drops to 0.21 for 200 bar. According to these data, the supreme isobar would be 130 bar.
• the isobar of low is selected by providing the maximum of a real utility function that corresponds to a reason in which the numerator is the specific net work of the cycle, measured as an increase in specific enthalpy in the hot spot, minus the specific enthalpy assigned in the cold spot; and the denominator is the sum of the absolute values of the specific enthalpy variations of each phase, weighted with coefficients, selected in the application of the invention in question, which evaluate the unit cost of each type of component used in each phase . 2013/000071
• the discharge is set at the maximum allowable pressure, and the discharge is selected according to the previous procedure.
• the scheme of this optimization applied to a cycle with C0 2 with 70 bar high, a minimum temperature of 31 ° C and the maximum of 400 ° C is presented below.
• enthalpy variations are defined, in absolute value: heat input (enthalpy) in the hot spot (Q); heat extraction (enthalpy) in the cold spot (E); heat exchanged in the regenerative exchanger (G); total enthalpy variation in machines, (), adding the absolute values of compression and expansion; to which a weight of weight m for M is added; and a weighting weight g for G and for E (since these are conventional heat exchangers, in both cases).
• a unit weight is reserved for Q, so that m represents the relative cost of handling a July (J) of energy in the machines, in relation to providing a July (J) in the hot spot; and similarly g represents what it costs to exchange a July (J) in an exchanger.
• connection pipe (40) is located with the low P storage tanks (52).
• the regenerative heat exchanger (7) which properly speaking has two circuits, low pressure (5) outside the tubes, and high pressure (6) inside the tubes, but it is a single component.
• the compressor (17) whose discharge manifold (18) is connected to the high pressure tubes (6) of the regenerative heat exchanger (7).
• said discharge pipe (19) it is optional to locate a flow regulation valve (50) as well as the extraction (38) that connects with the fluid storage device at high P, and the injection (48) of high fluid P in the discharge pipe (19).
• the device or system for providing heat to the heat source (9) that can acquire various morphologies, depending on the nature and origin of the heat provided, which may come directly or indirectly from a solar thermal energy collection facility, or may be geothermal origin, or from any type of combustion, or from nuclear reactions and radiations, and in particular from the rejection heat of a higher temperature Brayton cycle, in its cold branch, than the temperature of the heat source (9) of this cycle
• the high pressure isobar regulation system comprises o A fluid extraction pipe (38) in the compressor's discharge pipe (19), with a high pressure relief valve (39) in said fluid extraction pipe (38).
• the low pressure isobar regulation system comprises o A low pressure fluid bypass pipe (40), which starts from the exhaust duct (4) of the expander machine, with its low pressure relief valve (41) in said bypass pipe.
• a low pressure fluid injection pipe (54) which starts from said storage tanks (52), and injects the fluid into the exhaust duct (4) of the expander machine, using an auxiliary compressor ( 55) of low pressure installed in said injection pipe (54), there being an additional discharge valves (56) to the loading valves (53) of the tanks (52), in addition to the control valve (41).
• the low pressure tanks (52) also receive the fluid collected by the leak collection system, which exists around the shaft support bearings (25) both in the expander machine (1), whose high bearing (28) it is surrounded by the corresponding housing (30) as in the compressor machine (17) whose high bearing (29) is surrounded by the corresponding housing (34); starting from the housing (30) of the expander machine a pipe (31) provided with the pressure adjustment valve (32), which connects with the load pipe (59) of the low pressure tanks (52) whose opening and closing is governed by the corresponding valve (60); and starting from the housing (34) of the compressor machine a pipe (35) provided with the pressure adjustment valve (36), which connects with the load pipe (59) of the low pressure tanks (52).
• the operation of the cycle is adjusted by compliance with the two fundamental balances, mechanical and enthalpy.
• the first balance is squared in the stationary operating situation when the driving forces of the system equal the braking forces of the fluid, including loss of manometric load due to irreversibilities, plus the resistant action of the electric generator attached to the shaft (25); and the enthalpy balance is fulfilled when the fluid, at the end of the cycle, is in the same thermodynamic conditions at the beginning of the cycle.

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• 2012
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