• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
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  • 优先权
    • 专利摘要:
    Thermodynamic system for the generation of electrical energy. Thermodynamic system (1) for the generation of electrical energy, comprising a compression circuit (2), a power circuit (3) and a heat exchanger (10) located between both circuits. The compression circuit (2) comprises a first working fluid (12), an evaporator (4) to evaporate at least partially the first working fluid (12) from environmental thermal energy, and a compressor (6) located at the evaporator outlet (4). The power circuit (3) comprises a second working fluid (11), a turbine (5) located to receive and expand the second working fluid (11) heated after passing through the heat exchanger (10), and adapted to generate electric power, and a condenser (7) located at the exit of the turbine (5). The evaporator (4) is exposed to a higher ambient temperature than the condenser (7) is exposed to. (Machine-translation by Google Translate, not legally binding)
    公开号:ES2601582A1
    申请号:ES201630223
    申请日:2016-02-26
    公开日:2017-02-15
    发明作者:Adrian MORALES HERNANDEZ
    申请人:Ideadora S L；Ideadora SL；
    IPC主号:
    专利说明:

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    DESCRIPTION
    Thermodynamic system for the generation of electrical energy.
    Object of the invention
    The present invention belongs to the industrial sector of the generation of energy from renewable sources in general, and more particularly to the field of thermoelectric energy, that is, to the generation of electric energy from environmental thermal energy through a process thermodynamic
    The object of the invention is to provide a sustainable, reliable and economical electric power generation system.
    Background of the invention
    In recent years, the production of energy through renewable sources has acquired great relevance within the energy sector. These energy sources come from inexhaustible natural resources, producing a null environmental impact on the emission of greenhouse gases, such as CO2.
    One of the main drawbacks of renewable energy is the low energy efficiency obtained. Thus, on many occasions, the large investments required for energy production are abandoned or continually reconditioned to achieve an increase in energy production.
    Today, for the production of thermal energy, refrigeration compression machines that can function as a heat pump or refrigerator are known. These machines are capable of supplying a thermal energy of the order of three to five times the electrical energy they consume.
    On the other hand, for the production of electric energy, conventional power plants are capable of generating electric power with yields lower than the unit (ratio of electric power produced / energy of used fuel).
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    Another main drawback of renewable energy is the lack of proof of energy supply, in many cases subject to certain atmospheric or weather conditions.
    Therefore, it is desirable in the state of the art to improve the production of electrical energy in a sustainable, constant, economical and lasting manner.
    Description of the invention
    The thermodynamic system for the generation of electric energy that the present invention proposes, is presented as an improvement over what is known in the state of the art, since it manages to satisfactorily achieve the objectives previously indicated as suitable for the technique, by increasing the performance , without using fossil fuels and without relying on the randomness of the climate to ensure continuity of supply.
    The invention consists of a thermodynamic system for the generation of electrical energy comprising a compression circuit, a power circuit, and at least one heat exchanger located between both circuits.
    The compression circuit contains a first compressible working fluid, capable of absorbing and yielding heat. Furthermore, said compression circuit comprises an evaporator and at least one compressor. The evaporator is adapted to evaporate at least a part of the first working fluid from the environmental thermal energy, obtaining a first working fluid by reaching at least the saturated vapor point of said first working fluid. The compressor is located to receive the first working fluid at least partially evaporated, and is adapted to compress said fluid at least partially evaporated, increasing the pressure and temperature thereof until evaporation thereof is obtained.
    The power circuit contains a second compressible working fluid capable of absorbing and yielding heat. The heat exchanger is located between both circuits to transfer heat from the first working fluid to the second working fluid.
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    The power circuit also comprises at least one turbine and one condenser. The turbine is located to receive the second working fluid heated and at least partially evaporated after passing through the heat exchanger at a pressure and temperature such that in its expansion in said turbine a certain amount of energy can be produced. The turbine is adapted to generate electrical energy from the expansion of the second working fluid. The condenser is located to receive the second working fluid at least partially evaporated (expanded), and is adapted to condense the fluid at least partially evaporated, releasing at least part of the heat stored therein. The condenser receives the second expanded working fluid until a pressure value is reached such that its saturation temperature coincides with the temperature at which heat is exchanged with the environment in this element.
    Finally, the evaporator is exposed to an ambient temperature higher than the ambient temperature to which the condenser is exposed.
    In this way, the invention presents an electric power generation system that, making use of the low temperature thermal energy contained in the ambient state, is capable of producing more electric energy than the electric energy it consumes to obtain it . Thus, the described system allows the transformation of the thermal energy of the ambient state at low temperature into thermal energy of higher temperature, thanks to the contribution of electrical energy in the compression circuit, and subsequently the transformation of this thermal energy of higher temperature into Electric power in the power circuit.
    The compression circuit is designed to obtain thermal energy at a higher temperature, from the thermal energy of the ambient state at a lower temperature, and from the electrical energy necessary to power the circuit components (at least one evaporator and one compressor) . The power circuit is designed to obtain electrical energy, from the thermal energy transferred from the compression circuit by means of the heat exchanger.
    The invention discloses a sustainable and durable electrical energy production system, based on the use of low temperature thermal energy contained in the
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    environment and avoid the use of any type of fuel.
    Likewise, the system offers a relatively constant production of electric energy during certain months of the year, based on the use of low temperature thermal energy contained in the environment and the temperature difference between the evaporator and the condenser, in which The evaporator is at a higher ambient temperature than the condenser to ensure the proper functioning of the invention.
    Likewise, the invention presents an economical and simple electric energy production system, which does not require numerous elements, as is usual in the state of the art, such as cold and hot storage tanks, steam generators ( boilers) necessary to operate with steam or combustion chambers, etc.
    Likewise, the invention does not require fuel, and therefore, does not require any storage, treatment or transport system for this.
    According to a preferred embodiment, the evaporator is exposed to an ambient temperature of at least 24 ° C, and the condenser is exposed to an ambient temperature less than or equal to 17 ° C. By maintaining at least this temperature difference between the evaporator and the condenser, the invention is capable of ensuring the proper functioning of the system, and in particular, that the evaporator is capable of absorbing heat from the outside, to transfer it to the first working liquid, and that the condenser is capable of releasing heat outside the second working liquid.
    According to a preferred embodiment, the condenser is buried, acting as an underground heat exchanger, or submerged under water, acting as a heat exchanger with water. Likewise, preferably, the evaporator is in contact with the outside. In this way, the invention ensures for certain stages of the year that the evaporator is exposed to an ambient temperature higher than the ambient temperature to which the condenser is exposed.
    According to another preferred embodiment, the heat exchanger is located at the outlet of the compressor and before the entry of the turbine. Thus, the heat exchanger receives the
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    first evaporated working fluid and the second working fluid in liquid state. In that case, and preferably, the heat exchanger is adapted so that the heat transfer between the first evaporated working fluid and the second working fluid, is such that the first evaporated working fluid is liquefied, and that the Second working fluid is at least partially evaporated.
    According to another preferred embodiment, the power circuit also comprises a circulation pump responsible for driving the second working fluid through the power circuit, and where said circulation pump is located between the condenser outlet and the heat exchanger inlet . Advantageously, the pump will raise the pressure of the second working fluid to that of the turbine inlet.
    According to another preferred embodiment, the compression circuit also comprises a throttle valve responsible for reducing the pressure of the first working fluid until the working pressure of the evaporator is reached, where said throttle valve is located between the outlet of the heat exchanger and the evaporator inlet
    Alternatively, the compression circuit may comprise a turbine responsible for reducing the pressure of the first working fluid until the working pressure of the evaporator is reached, and where said turbine is located between the heat exchanger outlet and the evaporator inlet. In this case, the turbine could also be used to expand the fluid to the evaporator pressure, and generate electricity to supply some of the system elements, such as the circulation pump of the power circuit.
    According to a preferred embodiment, the thermodynamic system of the invention comprises the same number of compressors, as of turbines, and heat exchangers. Thus, the invention will present the same number of compressions as of expansions, achieving a stable system.
    Preferably, the first working fluid and / or the second working fluid is water. Water is a compressible fluid, capable of absorbing heat, cheap and easy to obtain, with
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    It offers several advantages in its use as a working fluid, both in the compression circuit and in the power circuit. In addition, the invention offers a safe alternative in case of leaks, since it is a non-polluting fluid. It should be mentioned that the mass flow rates of the compression and power cycle could be the same or different.
    Description of the drawings
    To complement the description that is being made and in order to help a better understanding of the characteristics of the invention, according to a preferred example of practical realization thereof, some drawings are included as an integral part of said description. Illustrative and not limiting, the following has been represented:
    Figure 1 shows a schematic view of the thermodynamic system, according to a preferred embodiment of the invention.
    Figure 2.- Shows the T-S diagram corresponding to the thermodynamic system shown in Figure 1. Figure 2a shows the complete diagram, and Figure 2b a detailed view of the diagram of Figure 2a.
    Preferred Embodiment of the Invention
    Figure 1 shows a thermodynamic system 1 for the generation of electrical energy. The thermodynamic system 1 shown comprises a compression circuit 2, a power circuit 3, and three heat exchangers 10, 10 ’, 10’ located between both circuits 2, 3.
    The compression circuit 2 contains a first working fluid 12, and the power circuit 3, a second working fluid 11. Both fluids 11, 12 are compressible, being able to change from physical state (from gaseous to liquid, and vice versa ), and also to store heat.
    The compression circuit 2 of the thermodynamic system 1 shown in Figure 1 comprises an evaporator 4, three compressors 6, 6 ’, 6’ (compression stages) and a throttle valve 8.
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    The evaporator 4 is adapted to evaporate at least a part of the first working fluid 12 from the environmental thermal energy. Thus, in the evaporator 4, the first working fluid 12 absorbs heat from the atmosphere until it reaches at least the saturation point of the first working fluid 12, obtaining the evaporation of at least a part thereof.
    The compressors 6, 6 ', 6' 'of the compression circuit 2 are located to receive the first working fluid 12, at least partially evaporated, and are adapted to compress said fluid, at least partially evaporated, increasing the pressure and temperature thereof until at least its evaporation is obtained. Thus, the first at least partially evaporated working fluid 12 is successively compressed along the circuit, evaporating and experiencing a temperature increase.
    After passing through the evaporator 4, the first working fluid 12 passes through a first compressor 6, in which it is compressed until evaporation is obtained.
    Next, the first heated and evaporated working fluid 12 arrives at the first heat exchanger 10. The heat exchanger 10 communicates the two circuits 2, 3 transferring heat from the first 12 to the second working fluid 11.
    After assigning a large part of heat to the second working fluid 11, the first evaporated working fluid 12 enters a second compressor 6 ’adapted to compress the incoming fluid, increasing its pressure and temperature.
    Then, the first working fluid 12 reaches the second heat exchanger 10 ’, in which part of the heat of the first working fluid 12 passes to the second working fluid 11.
    Again, after assigning much of the heat to the second working fluid 11, the first working fluid 12 enters a third compressor 6 ’’ equally adapted to compress the incoming fluid, increasing its pressure and temperature.
    Next, the first working fluid 12 enters the third heat exchanger 10 ’. In this third heat exchanger 10 ’the heat transfer of the first working fluid 12
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    to the second working fluid 11 is such that the temperature drops sufficiently that the first evaporated working fluid 12 is liquefied.
    Finally, the first working fluid 12 enters the throttle valve 8, which is located to receive the first working fluid 12 that passes through the third heat exchanger 10 ’. The throttle valve 8 is responsible for reducing the pressure of the first working fluid 12 until the working pressure of the evaporator 4 is reached.
    For its part, the power circuit 3 of the thermodynamic system 1 shown in Figure 1 comprises a condenser 7, three turbines 5, 5 ’, 5’ (expansion stages) and a circulation pump 9.
    The condenser 7 is adapted to condense at least a part of the at least partially evaporated second working fluid 11, releasing at least a part of the heat stored therein. Thus, the condenser 7 gives heat to the outside until the second working fluid 11 becomes at least partially liquid.
    After passing through the condenser 7, the second working fluid 11 passes through the circulation pump 9, which drives said fluid towards the third heat exchanger 10 ’. In this third heat exchanger 10 ’, part of the heat of the first working fluid 12 is transferred to the second working fluid 11, where said heat transfer is such that the second working fluid 11 is at least partially evaporated.
    Next, the second working fluid 11 heated and at least partially evaporated reaches a first turbine 5.
    The turbines 5, 5 ', 5' 'of the power circuit 3 are positioned to receive the second working fluid 11 heated and at least partially evaporated after passing through the heat exchangers 10' ', 10', 10, and are adapted to expand said fluid, at least partially evaporated, and generate electrical energy from the expansion and heat stored in the second working fluid 11. Thus, the second working fluid 11 is successively expanded along the circuit, evaporating and experiencing a temperature rise.
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    After passing the first turbine 5, the second working fluid 11 at least partially evaporated and expanded arrives at the second heat exchanger 10 ’, in which part of the heat of the first evaporated working fluid 12 passes to the second working fluid 11.
    Again, after receiving heat from the first working fluid 12, the second working fluid 11 enters a second turbine 5 ’adapted to expand the second working fluid 11, decreasing the pressure and temperature thereof.
    Next, the second working fluid 11 arrives at the first heat exchanger 10, in which it again receives heat from the first working fluid 12.
    Subsequently, and to complete the cycle, the second working fluid 11 enters a third turbine 5 '' in which the second working fluid 11 expands to such a point that it passes into a partially evaporated state (mixture of liquid and steam) . Preferably, the second working fluid 11 is completely evaporated at the outlet of the third turbine 5 ’to avoid cavitation.
    Figure 2a shows the TS diagram (temperature-entropy diagram or entropic diagram) corresponding to the thermodynamic system 1 shown in figure 1 for the specific case of a system operating with this cycle in the city of Madrid during the hottest 3 months of the year. Madrid has an average annual temperature of 13.7 ° C and an average temperature in the summer months of 22.5 ° C.
    Based on these data, the following hypotheses are established:
    - In the evaporator heat is absorbed from the atmosphere at 22.5 ° C,
    - In the condenser heat is transferred to the ground at 16 ° C (conservative situation, if heat were transferred to 13.7 ° C, the system would obtain better performance), and
    - the mass flow value for the first working fluid and for the second working fluid is 1 kg / s.
    In said figure 2a, by way of example, the changes experienced by the first 12 and the second 11 working fluid can be seen when crossing the different elements that comprise both the compression circuit 2 and the power circuit 3.
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    The compression circuit 2 begins with the passage of the first working fluid 12 through the evaporator 4, (references h-a of Figure 1). As can be seen in figure 2a, when the evaporator 4 passes through, the first working fluid 12 is subjected to an isobar heat absorption process (at constant pressure). With this heat absorption, the first working fluid 12 reaches saturation.
    In the first compressor 6 (a-b), the first working fluid 12 increases its pressure and temperature, reaching the gaseous state, and being placed in the reheated steam zone, since before the expansion it was saturated steam. When passing through the first heat exchanger 10 (b-c), the first working fluid 12 experiences a temperature drop when part of its heat is transferred to the power circuit 3, continuing, however, in at least partially gaseous state. It is only in the third heat exchanger 10 ’(f-g) in which the temperature decreases so much that the working fluid 12 passes to Kquido at high pressure. Finally, in step g-h (Figure 2b), the throttle valve 8 reduces the pressure of the working fluid 12 to its initial state, the pressure of the evaporator 4.
    On the other hand, the second working fluid 11 behaves similarly in the power circuit 3.
    At the exit of the circulation pump 9 (s) (figure 2b), the second working fluid 11, in a liquid state, passes through the third heat exchanger 10 ’(s-t). In this stage (s-t), the second working fluid 11 undergoes a constant temperature increase at a pressure such that said second working fluid 11 goes into a gaseous state.
    Subsequently, at each step through the first turbine 5 (tu), the second turbine 5 '(vw), and the third turbine 5' '(xy), the second working fluid 11 experiences a decrease in pressure and temperature, keeping its At least partially gaseous state. And, at each step through the second 10 ’(u-v) and the first heat exchanger 10 (w-x), the second working fluid 11 experiences an increase in its pressure and temperature.
    As it is observed, in its passage through the third turbine 5 '' (xy), the pressure decreases so much that it reaches the saturation pressure for the heat exchange temperature sought in the condenser, in this case the fluid being in superheated steam state or wet steam.
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    At the exit of this third turbine 5 ’(y), the pressure must be low, since it must match the saturation pressure for the subway temperature sought.
    Finally, in its passage through the condenser 7 (y-z), the second working fluid 11 gives heat to the environment at constant pressure and temperature, going from a wet vapor state to a saturated liquid.
    For this example, considering:
    - an isoentropic yield of turbines 5, 5 ’, 5’ ’of 94%, where, for turbines:
    Actual enthalpy difference
    Isoentropic performance = - ---------------------—-----—-
    Ideal enthalpy difference
    that is, 5, 5 ’, 5’ turbines produce less energy than they would ideally produce with isentropic efficiency = 1,
    - an isoentropic efficiency in compressors 6, 6 ’, 6’ ’of 90%, where, for compressors:
    Ideal enthalpy difference
    Isoentropic performance = --------------------------—---------
    Actual enthalpy difference
    that is, compressors 6, 6 ’, 6’ ’consume more energy than they would ideally consume with isoentropic efficiency = 1,
    - and a heat loss in heat exchangers 10, 10 ’, 10’ ’of 5% (95% yield), where the effect of heat loss in each heat exchanger follows the following expression:
    Heat determined by the exchanger to the power circuit
    0.95 = ---------------------------------------------- -------------------------------------------------- ------------------------------
    Heat assigned to the exchanger in the compression circuit
    And taking into account that the power in each turbine 5, 5 ', 5' 'and compressor 6, 6', 6 '' is defined as the product of the mass flow through each element multiplied by the enthalpy difference at the input and at the exit of each element, that is,
    - for the first turbine 5:
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    ^ turbine 5 ^ 11 • (ht
    where mxl is the mass flow of the second working fluid 11, ht enters it in state t and hu enthalpy in state u. Mass flow in kg / s, enthalpy in kJ / kg, and P in kW.
    - for the second 5 ’turbine:
    ^ turbine 5 '^ 11 • (hv hw)
    where m11 is the mass flow of the second working fluid 11, hv enthalpy in state v and hw enthalpy in state w. Mass flow in kg / s, enthalpy in kJ / kg, and P in kW.
    - for the third 5 ’turbine:
    Pturbina 5 "'(hx hy)
    where m11 is the mass flow of the second working fluid 11, hx enthalpy in state x and h and enthalpy in state y. Mass flow in kg / s, enthalpy in kJ / kg, and P in kW.
    - for the first compressor 6:
    Pcompressor 6 ^ 12 • (hb ha)
    where m12 is the mass flow of the first working fluid 12, hb enthalpy in state b and enthalpy in state a. Mass flow in kg / s, enthalpy in kJ / kg, and P in kW.
    - for the second 6 ’compressor:
    Pcompressor 6 '^ 12 • (hd hc)
    where m12 is the mass flow of the first working fluid 12, hd enthalpy in state d and hc enthalpy in state c. Mass flow in kg / s, enthalpy in kJ / kg, and P in kW.
    - for the third 6 ’compressor:
    Pcompressor 6 "^ 12 • (h / he)
    where m12 is the mass flow of the first working fluid 12, hf the enthalpy in the f state and the enthalpy in the e state. Mass flow in kg / s, enthalpy in kJ / kg, and P in kW.
    And disregarding the power of the circulation pump 9, being of an order value of magnitude lower than the power values of turbines 5, 5 ’, 5’ and compressors 6, 6 ’,
    6 '', a global performance value is obtained, defined as the ratio between the mechanical energy generated in the turbine (subsequently convertible into electrical energy) and the electrical energy consumed in the compressor of 1.25, where, said performance global follows the following expression:
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    First turbine power 5 + Second turbine power 5 '+ Third turbine power 5 "
    Overall performance = ----------------------------------------------- -------------------------------------------------- -------------------------------------------------- ---------------------------------
    First compressor power 6 + Second compressor power 6 + Third compressor power 6
    Thus, the thermodynamic system proposed by the present invention produces more mechanical energy (convertible to electric) than the electrical energy it consumes.
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    Finally, in view of this description and figures, the person skilled in the art may understand that the invention has been described according to some preferred embodiments thereof, but that multiple variations can be introduced in said preferred embodiments, without departing from the object of the Invention as claimed.
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    权利要求:
    Claims (10)
    [1]
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    1. - Thermodynamic system (1) for the generation of electrical energy, characterized in that it comprises:
    - a compression circuit (2) containing a first working fluid (12) compressible and capable of absorbing heat, and which at least comprises:
    - an evaporator (4) adapted to evaporate at least a part of the first working fluid (12) from the environmental thermal energy, and
    - a compressor (6) located to receive the first working fluid (12) at least partially evaporated, and adapted to compress said fluid at least partially evaporated by increasing the pressure and temperature thereof until evaporation thereof is obtained,
    - a power circuit (3) containing a second working fluid (11) compressible and capable of absorbing heat, and
    - at least one heat exchanger (10) located between both circuits (2, 3) to transfer heat from the first working fluid (12) to the second working fluid (11),
    - where, the power circuit (3) comprises:
    - a turbine (5) located to receive the second working fluid (11) heated and at least partially evaporated after passing through the heat exchanger (10), and adapted to generate electrical energy from the change of stored pressure and heat in the second working fluid (11),
    - a condenser (7) located to receive the second working fluid (11) at least partially evaporated, and adapted to condense the at least partially evaporated fluid, releasing at least part of the heat stored therein,
    - and where, the evaporator (4) is exposed to an ambient temperature higher than the ambient temperature to which the condenser (7) is exposed.
    [2]
    2. - Thermodynamic system (1) for the generation of electrical energy, according to revindication 1, characterized in that the evaporator (4) is exposed to an ambient temperature of at least 24 ° C, and that the condenser (7) is exposed to an ambient temperature less than or equal to 17 ° C.
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    [3]
    3. - Thermodynamic system (1) for the generation of electric energy, according to any of the preceding claims, characterized in that the heat exchanger (10) is located at the outlet of the compressor (6) and before the entry of the turbine (5).
    [4]
    4. - Thermodynamic system (1) for the generation of electrical energy, according to revindication 3, characterized in that the heat exchanger (10) is adapted so that the heat transfer between the first evaporated working fluid (12) and the second working fluid (11), is such that the first evaporated working fluid (12) is liquefied and the second working fluid (11) is evaporated.
    [5]
    5. - Thermodynamic system (1) for the generation of electric energy, according to any of the preceding claims, characterized in that the power circuit (3) also comprises a circulation pump (9) responsible for driving the circulation of the second fluid of work (11) through the power circuit (3), and where said circulation pump (9) is located between the condenser outlet (7) and the heat exchanger inlet (10).
    [6]
    6. - Thermodynamic system (1) for the generation of electric energy, according to any of the preceding claims, characterized in that the compression circuit (2) also comprises a throttle valve (8) responsible for reducing the pressure of the first fluid of work (12) until the working pressure of the evaporator (4) is reached, where said throttle valve (12) is located between the heat exchanger outlet (10) and the evaporator inlet (4).
    [7]
    7. - Thermodynamic system (1) for the generation of electric energy, according to any of claims 1-5, characterized in that the compression circuit (2) also comprises a turbine responsible for reducing the pressure of the first working fluid (12 ) until the working pressure of the evaporator (4) is reached, and where said turbine is located between the heat exchanger outlet (10) and the evaporator inlet (4).
    [8]
    8. - Thermodynamic system (1) for the generation of electric energy, according to any of the preceding claims, characterized in that the capacitor (7) is buried or submerged under water.
    [9]
    9. Thermodynamic system (1) for the generation of electric energy, according to any of the preceding claims, characterized in that it comprises the same number of compressors (6), turbines (5), and heat exchangers (10).
    5 10.- Thermodynamic system (1) for the generation of electrical energy, according to any of
    the preceding claims, characterized in that the first working fluid (12) and / or the second working fluid (11) is water.
    [11]
    11. Thermodynamic system (1) for the generation of electric energy, according to any of the preceding claims, characterized in that the evaporator (4) is in contact with the outside.
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    同族专利:
    公开号 | 公开日
    ES2601582B1|2017-12-12|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US4037413A|1974-12-09|1977-07-26|Energiagazdalkodasi Intezet|Power plant with a closed cycle comprising a gas turbine and a work gas cooling heat exchanger|
    CN101397983A|2007-09-30|2009-04-01|王作国|Working fluid phase changing enthalpy difference sea water temperature difference power machine|
    US20090126381A1|2007-11-15|2009-05-21|The Regents Of The University Of California|Trigeneration system and method|
    CN102213199A|2011-06-02|2011-10-12|东方电气集团东方汽轮机有限公司|Ocean thermal energy conversion method and ocean thermal energy conversion device|
    EP2765281A1|2013-02-07|2014-08-13|Ingenieria I Mas D-Tec Ratio, S.L.|A rankine cycle apparatus|
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    申请号 | 申请日 | 专利标题
    ES201630223A|ES2601582B1|2016-02-26|2016-02-26|Thermodynamic system for electric power generation.|ES201630223A| ES2601582B1|2016-02-26|2016-02-26|Thermodynamic system for electric power generation.|
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