• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    Energy production system for a motor vehicle or generator set. It is characterized in that it comprises a circuit (1) of thermodynamic work that uses carbon dioxide to obtain energy by means of a turbine (t) of expansion of said carbon dioxide, and by the fact that it comprises a circuit (3) refrigerator equipped with a heat exchanger (6) sized to condense by means of a cooling fluid a fraction of the carbon dioxide expelled by the turbine (t), the same refrigerant circuit (3) including a second exchanger (8) sized to evaporate carbon dioxide carbon already condensed by the same refrigerant fluid, once said refrigerant fluid has been compressed to be able to provide heat. (Machine-translation by Google Translate, not legally binding)
    公开号:ES2643860A1
    申请号:ES201630668
    申请日:2016-05-24
    公开日:2017-11-24
    发明作者:Máximo PUJOL LATRE
    申请人:Máximo PUJOL LATRE；
    IPC主号:
    专利说明:

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    DESCRIPTION
    ENERGY PRODUCTION SYSTEM FOR AN AUTOMOBILE VEHICLE OR
    ELECTROGEN GROUP
    The present invention relates to an energy production system for a motor vehicle or for a mobile generator set equipped with a combustion engine that allows to increase the overall energy efficiency of said vehicle or generator set taking advantage of the residual heat of the exhaust gases the motor.
    Background of the invention
    Internal combustion engines use only one third of the energy from the fuel to generate mechanical energy. The remaining two thirds of energy is discarded and released into the outside environment through the exhaust or engine cooling circuit.
    Energy production systems are known for automobile vehicles that take advantage of the residual heat of the engine's exhaust gases by means of thermodynamic work circuits that employ various work fluids, such as water vapor or water and ammonia solutions.
    Patent DE102009024776 describes an energy production system for a motor vehicle in which the working fluid (for example, water) is pumped to a heat exchanger sized to evaporate a fraction of this fluid by thermal energy from the gases of escape. The system also includes a refrigeration circuit to cool the working fluid at the exit of an expansion turbine of said fluid that obtains mechanical energy from the working fluid.
    Existing energy production systems, such as the one described in the aforementioned patent, have the disadvantage that they have low energy efficiency and, in addition, are complex to implement in a motor vehicle.
    Description of the invention
    The objective of the present invention is to provide an energy production system
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    for a car that solves the aforementioned problems and presents the advantages that will be described below.
    According to this objective, according to a first aspect, the present invention provides energy production system for a motor vehicle or for a mobile generator set provided with a combustion engine, characterized by the fact that it comprises a working circuit thermodynamic that uses carbon dioxide to obtain energy by means of an expansion turbine of said carbon dioxide, and by the fact that it comprises a refrigeration circuit provided with a heat exchanger, which is sized to condense a fraction of the dioxide by means of a cooling fluid of carbon expelled by the turbine, including the same refrigeration circuit a second exchanger sized to evaporate carbon dioxide already condensed by the same refrigerant fluid, once said refrigerant fluid has been compressed to be able to provide heat when condensed.
    Unlike the systems of the state of the art, which use the heat provided by the vehicle's exhaust gases to evaporate the working fluid entering the expansion turbine, the claimed system has the advantage that the working fluid, which is carbon dioxide, it is evaporated by the heat provided by the refrigerant fluid of the refrigeration circuit itself during the refrigeration cycle when the refrigerant gas condenses.
    In fact, it has been observed that the heat absorbed and generated by the refrigerant fluid in the refrigeration circuit is sufficient in excess to evaporate the carbon dioxide that has previously been condensed at a pressure of 30 bar during the evaporation cycle of the same fluid refrigerant. This is obtained, a very simple and high energy efficiency system that is also harmless.
    According to a preferred embodiment, the thermodynamic working circuit comprises a third heat exchanger sized to cool the temperature of the carbon dioxide expelled by the turbine before said carbon dioxide enters the exchanger where it will be condensed. In particular, said third heat exchanger is sized to cool the temperature of the carbon dioxide expelled by the turbine by carbon dioxide evaporated in the heat exchanger of the refrigeration circuit.
    This third exchanger has the advantage that it allows to recover the heat of the carbon dioxide gas that is expelled by the turbine to reduce the energy consumption of the
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    heat pump (compressor) of the refrigeration circuit. This recovered heat can be used to heat the carbon dioxide already evaporated from the work circuit.
    Preferably, the thermodynamic working circuit comprises a fourth heat exchanger sized to increase the temperature of the evaporated carbon dioxide to a temperature equal to or greater than 300 ° C by means of the heat from the exhaust gases of the combustion engine of said vehicle or generator set
    Unlike the systems of the state of the art, in the system of the present invention, the heat of the combustion engine exhaust gases is used to heat the already evaporated carbon dioxide, before entering the turbine.
    Advantageously, the thermodynamic working circuit comprises a fifth heat exchanger sized to increase the temperature of the evaporated carbon dioxide at the outlet of the heat exchanger of the refrigeration circuit by means of heat from a refrigeration circuit of the combustion engine of the vehicle or group electrogen
    This fifth heat exchanger allows to take advantage of a part of the heat of the system that is expelled through the conventional engine cooling circuit, to overheat the already evaporated carbon dioxide.
    Preferably, the refrigeration circuit includes a machine for mechanically compressing the refrigerant fluid and means for driving said machine by mechanical energy from the combustion engine of said vehicle or generator set.
    In this way, the compressor of the refrigeration circuit can be operated without any added energy cost.
    Advantageously, the combustion engine drives the turbine applied to the mechanical traction and the compressor of the refrigeration circuit, which allows to distribute the forces automatically independently as it suits the vehicle and thus, for example, in a retention or braking movement the compressor accumulates energizes refrigerant without consuming fuel, achieving an additional reduction in the average consumption of the vehicle in circulation, improving the calculated efficiency.
    According to a preferred embodiment, the refrigeration circuit of the system is sized or
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    adapted to condense a fraction of the carbon dioxide at a temperature equal to or less than -6 ° C and at a pressure equal to or less than 30 bar, and to evaporate said condensed carbon dioxide at a temperature equal to or greater than 30 ° C and at a pressure equal to or greater than 65 bar.
    According to a second aspect, the present invention provides a motor vehicle provided with a combustion engine comprising the claimed energy production system, where the carbon dioxide expansion turbine is connected to the engine of said vehicle or generator set, being susceptible a fraction of the mechanical energy coming from the turbine to be used to drive the vehicle or generator set.
    In the present invention, refrigeration circuit will preferably be understood as a circuit that uses a refrigerant fluid and a machine or compressor to mechanically compress said fluid.
    Brief description of the figures
    To better understand how much has been exposed, a drawing or figure is attached in which, schematically and only by way of non-limiting example, a practical case of realization is represented.
    The figure shows a schematic diagram of the principle of operation of the system. Description of a preferred embodiment
    A preferred embodiment of the system is described below with reference to the only figure.
    The described embodiment includes a thermodynamic working circuit 1 that employs carbon dioxide and an expansion turbine T of said carbon dioxide. During the duty cycle, carbon dioxide acquires a pressure of 30 bar, at -6 ° C temperature in a liquid state, and a pressure of 65 bar, at a temperature of 400 ° C in a gaseous state, before its entry in the expansion turbine T.
    To acquire these working conditions, a refrigeration circuit 3 is used to condense and evaporate the carbon dioxide, and two circuits 4, 5 for overheating the carbon dioxide.
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    evaporated carbon that allow the carbon dioxide temperature to be increased to a working temperature of 400 ° C, before entering the expansion turbine T.
    The refrigeration circuit 3 is provided with a heat exchanger 6 adapted to condense a fraction of the carbon dioxide expelled by the expansion turbine T by means of a cooling fluid. At the exit of the heat exchanger 6, the carbon dioxide is in a liquid state and at a pressure of 30 bar, ready to be injected by means of a pump 7 to a second heat exchanger 8 where the carbon dioxide is evaporated using the same fluid refrigerant, once said fluid has been compressed to provide heat, in the condensation thereof.
    As mentioned in the description of the invention, it has been observed that the heat absorbed by the refrigerant fluid during the refrigeration cycle of carbon dioxide is excessively sufficient to evaporate the carbon dioxide by the heat provided with the compression and condensation of said refrigerant fluid by means of a machine or compressor C of said refrigerant fluid.
    At the exit of the second exchanger 8, the carbon dioxide evaporated at a pressure of 65 bar and a temperature of 30 ° C, is heated by a first circuit 4 which includes a heat exchanger 10 intended to take advantage of the heat from the flow fluid. cooling of the combustion engine M of the vehicle or generator set, and a second circuit 5 which includes a heat exchanger 11 intended to take advantage of the heat from the exhaust gases of the combustion engine M. At the exit of both heating circuits 4, 5, the carbon dioxide in the gaseous state has an adequate working temperature to enter the expansion turbine T which allows to obtain mechanical energy to drive the vehicle or generator set.
    In the embodiment described, the thermodynamic working circuit 1 has the particularity that it comprises a heat exchanger 12 sized to cool the temperature of the carbon dioxide expelled by the expansion turbine T in order to reduce the energy consumption of the machine or compressor C of the cooling fluid. This heat exchanger 12 has the advantage that it is adapted to recover the heat of the carbon dioxide gas that is expelled by the expansion turbine T and transfer it to the evaporated carbon dioxide of the working circuit 1, before said carbon dioxide enter the heat exchanger 11 of the circuit 5 of use of the residual heat of the exhaust gases of the combustion engine M of the vehicle or generator set.
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    Together, the claimed system allows obtaining a vehicle or generator with an overall energy efficiency of 55%, thereby reducing fuel consumption and therefore the air pollution generated by vehicles or generators that include internal combustion engines. In addition, the system is very safe, since carbon dioxide is a fluid that is harmless to the environment.
    Excess heat is expelled through a first radiator 14 of the refrigeration circuit 3 and a second radiator 13 of the cooling circuit 4 of the engine M.
    An example of realization of the system for a diesel generator set of 100 KW of power equivalent to a consumption of 8.6 kg of diesel per hour or 86000 Kcal / h is described below.
    Data and working conditions
    For a power consumption of 100 KW and a performance of 32%, the power achieved by the motor is 32 KW equivalent to 27,520 Kcal / h.
    The power of the alternator and auxiliary is 7 KW which is equivalent to 6020 Kcal / h.
    The useful mechanical power of the transmission system is 25 KW.
    Engine cooling heat is 20,000 Kcal / h which equals 23.25 KW.
    Heat exhaust gases is 34,000 Kcal / h which is equivalent to 40 KW.
    Heat recoverable from the exhaust gases is 34,000 x 0.85 (yield) = 28,900 Kcal / h, where 34,000 Kcal / h is the heat of the exhaust gases and where 0.85 is the performance of the heat exchanger.
    Carbon dioxide temperature at the turbine inlet is 400 ° C.
    Carbon dioxide pressure at the turbine inlet is 65 bar.
    Carbon dioxide pressure from the turbine exhaust is 30 bar.
    Temperature of the carbon dioxide at the inlet of the exchanger referenced with the number 8 is - 6 ° C.
    The necessary carbon dioxide flow is 680 Kg / h.
    Evaporation temperature in the heat exchanger referenced with the number 8 is 30 ° C.
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    Calculations
    - Heat of evaporation and heating of carbon dioxide (Q8) in the exchanger / evaporator with reference number 8 in the figure
    The evaporation of carbon dioxide takes place in the heat exchanger / evaporator with a heat input, according to calculation;
    Q8 = 680 (55 + 0.202 (30 - (-6)) = 42,346.6 Kcal / h, where 680 is the flow rate of carbon dioxide in kg / h, 55 is the heat of evaporation of carbon dioxide in Kcal / kg, where 0.202 is the specific heat of carbon dioxide in Kcal / kg ° C, where 30 is the temperature of carbon dioxide at the outlet of the heat exchanger 8 in ° C and where -6 is the temperature of carbon dioxide at the heat exchanger inlet 8 in ° C.
    - Heat of heating of the carbon dioxide (Q10) in the heat exchanger / recuperator with reference number 10 in the figure
    The gas evaporated to the temperature of 30 ° C leaving the heat exchanger / evaporator 8 is taken to the heat exchanger / recuperator 10 fed with the cooling circuit of the diesel engine reaching 90 ° C with the heat input according to calculation;
    Q10 = 680 x 0.202 (90-30) = 8,241.6 Kcal / h, where 680 is the flow rate of carbon dioxide in kg / h, where 0.202 is the specific heat of carbon dioxide in Kcal / kg ° C, where 90 is the temperature of the carbon dioxide at the outlet of the heat exchanger / recuperator 10 in ° C and where 30 is the temperature of the carbon dioxide at the entrance of the heat exchanger / recuperator 10 in ° C.
    - Heat of heating of the carbon dioxide (Q12) in the exchanger / recuperator with reference number 12
    Once the flow of carbon dioxide gas leaves the heat exchanger / recuperator 10 it is directed to the heat exchanger / recuperator 12 where it is reheated with the carbon dioxide gas from the turbine, which has an exhaust temperature of 265 ° C, reaching a temperature of 190 ° C with the heat input according to calculation;
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    Q12 = 680 x 0.202 (190-90) = 13.736 Kcal / h, where 680 is the flow rate of carbon dioxide in kg / h, where 0.202 is the specific heat of carbon dioxide in Kcal / kg ° C, where 190 is the temperature of the carbon dioxide at the outlet of the heat exchanger / recuperator 12 in ° C and where 90 is the temperature of the carbon dioxide at the entrance of the heat exchanger / recuperator 12 in ° C.
    - Heat of heating of the carbon dioxide (Q11) in the heat exchanger / recuperator with reference number 11
    Subsequently, the carbon dioxide is heated again in the exchanger 11 fed with the exhaust gases of the diesel engine until the maximum working temperature of 400 ° C is reached with the heat input as calculated;
    Q11 = 680 x 0.202 (400 - 190) = 28.845 Kcal / h, where 680 is the flow rate of carbon dioxide in kg / h, where 0.202 is the specific heat of carbon dioxide in Kcal / kg ° C, where 400 is the temperature of the carbon dioxide at the outlet of the heat exchanger / recuperator 11 in ° C and where 190 is the temperature of the carbon dioxide at the entrance of the heat exchanger / recuperator 11 in ° C.
    - Use in the turbine of the internal energy accumulated in the carbon dioxide gas of the circuit and conditions at the exit of the exchanger / recuperator with reference number 12
    The conditions of the carbon dioxide at the turbine inlet are 400 ° C temperature and 65 bar pressure. The carbon dioxide gas drives the turbine where it expands by performing work and consequently yields the internal energy achieved being finally at the exit of the turbine under the conditions of temperature 265 ° C and 52 bar pressure. Carbon dioxide from the turbine exhaust is cooled in the exchanger 12 with the flow of carbon dioxide gas from the heat exchanger / recuperator 10 to a temperature of 165 ° C.
    - Cooling heat of carbon dioxide (Q12a) in heat exchanger / recuperator with reference number 12
    The exhaust carbon dioxide gas from the turbine, which is at a temperature of 265 ° C and a pressure of 52 bar, is used in heat exchanger / recuperator 12 to
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    heating the carbon dioxide gas from the exchanger / recuperator 10, reaching a temperature of 190 ° C with the heat input according to calculation;
    Q12a = 680 x 0.202 (165 - 265) = - 13,736 Kcal / h, where 680 is the flow rate of carbon dioxide in kg / h, where 0.202 is the specific heat of carbon dioxide in Kcal / kg ° C, where 165 is the temperature of the carbon dioxide at the outlet of the heat exchanger / recuperator 12 in ° C and where 265 is the temperature of the carbon dioxide at the entrance of the heat exchanger / recuperator 12 in ° C.
    - Calculations prior to the calculation of the heat of liquefaction of carbon dioxide in the heat exchanger / condenser with reference number 6
    The cycle is concluded once the carbon dioxide gas returns to the initial conditions that are 30 bar of pressure and -6 ° C of temperature, for this fact it is necessary for the carbon dioxide gas to cool until it liquefies in the exchanger / reference numeric capacitor 6.
    The carbon dioxide gas will perform an expansion work (at a constant volume) by a pressure change from 52 bar to 30 bar, at the inlet of the exchanger / condenser 6. Said expansion work occurs when entering the exchanger / condenser 6, producing a refrigeration cooling of 165 ° C to -20.3 ° C, according to calculation;
    P1 / T1 = P2 / T2; where P1 is the bar pressure of carbon dioxide at the inlet of the exchanger / condenser 6, where T1 is the temperature in degrees Kelvin at the inlet of the condenser 6, where P2 is the bar pressure of carbon dioxide in the exchanger / condenser 6, where T2 is the Kelvin temperature of the carbon dioxide in the exchanger / condenser 6.
    By isolating T2, it is obtained that the temperature T2 of the carbon dioxide in the exchanger / condenser 6 is, according to calculation;
    T2 = (165 + 273) x 30/52 = 252.3 ° K = - 20.3 ° C, where 165 is the temperature of the carbon dioxide at the inlet of the exchanger / condenser 6 in ° C, where 273 is a factor to convert the temperature to degrees Kelvin, where 30 is the pressure of the carbon dioxide in the exchanger / condenser 6 in bar, and where 52 is the pressure of the carbon dioxide at the inlet of the exchanger / condenser 6 in bar.
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    Upon cooling of the carbon dioxide gas from 165 ° C to -20.3 ° C, it makes an internal heat input at the entrance to the exchanger 6, which we will call heat of condensation, due to the fact that condensation occurs when acquiring the equilibrium temperature from -6 ° C to 30 bar, according to calculation;
    Q = 0.202 x Dt = 0.202 (-20.3 - (-6)) = 3 Kcal / kg C02, where 0.202 is the specific heat of carbon dioxide in Kcal / kg ° C, where - 20.3 ° C is the temperature of the carbon dioxide at the inlet of the exchanger / condenser 6, and where -6 ° C is the temperature of the carbon dioxide in the liquid state under the working conditions of 30 bar. .
    - Heat of liquefying the carbon dioxide in the heat exchanger / condenser with reference number 6
    The energy consumption for the condensation of the carbon dioxide gas in the exchanger / condenser 6 will result according to calculation;
    Q6 = 680 (55 - 3) = 35,360 Kcal / h, where 680 is the flow rate of carbon dioxide in kg / h, where 55 is the heat of condensation of carbon dioxide in Kcal / kg and - 3 is the heat of condensation already acquired when entering the exchanger / condenser 6 in Kcal / kg.
    In order for condensation to occur, the cooling provided by the heat pump C that consumes 11,787 Kcal / h (13.7 Kw) is required, which added to the heat Q6 gives us the thermal energy in excess of the exchanger / evaporator 8.
    - Heat evacuated from the system
    The heat that must be evacuated to the outside will be effected by the radiators 13, 14, according to calculation;
    Q13 = 20,000 - 8,241 = 11,759 Kcal / h, where 20,000 is the engine cooling heat in Kcal / h and where 8,241 is the heat exchanger heat 10 in Kcal / h.
    Q14 = Q6 + QC - Q8 = 4,801 Kcal / h, where Q6 is the heat in exchanger 6 in Kcal / h, where QC is the heat of the heat pump / compressor referenced with the letter C in Kcal / h and where Q8 is the heat in heat exchanger 8 in Kcal / h.
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    - Useful system heat
    The useful heat of the system is, according to calculation;
     Q = Q8 + Q10 + Q11 + Q12 + Q12a - Q6 - QC =  ■ 32,286.2 Kcal / h (37.5 Kw), where Q8 is the
     heat in the exchanger / evaporator 8 in  Kcal / h, where Q10 is the heat in the
     exchanger / recuperator  of heat 10 in Kcal / h, where Q11 is the heat in the
     exchanger / recuperator  11 in Kcal / h, where Q12 is the heat in the
     exchanger / recuperator  12 in Kcal / h, where Q12a is the heat in the
    exchanger / recuperator 12, where Q6 is the heat in the exchanger / condenser 6 in Kcal / h and where QC is the heat of the heat pump / compressor referenced with the letter C in the figure in Kcal / h.
    Yields
    - Resulting system performance
    The resulting yield is, according to calculation; (32,286.2 - 11,787) / (34,000 + 20,000) = 0.38 which is equivalent to 38%, where 32,286.2 is the useful heat of the system in Kcal / h, where 11,787 is the power of the heat pump in Kcal / h and where the sum of 34,000 and 20,000 is the energy used in the Kcal / h system.
    - Global system performance
    Overall performance is, according to calculation; (20,499.2 + 27,520) / 86,000 = 0.558 which equals 55.8%, where 20,499.2 is the difference between 32,286.2 which is the useful heat in Kcal / h and 11,787 is the power of the heat pump in Kcal / h, where 27,520 is the power achieved by the engine in Kcal / h and where 86,000 is the heat produced by a 100 KW generator with a consumption of 8.6 kg of diesel per hour in Kcal / h.
    System thermal balance
    27,520 Kcal / h provided by the engine
    6,020 Kcal / h provided by the alternator and auxiliary
    32,286.2 Kcal / h of useful heat in the turbine
    16,560 Kcal / h of heat exchangers / evacuators 13 and 14
    If it is taken into account that the heat produced by a 100 KW generator with an consumption of 8.6 kg of diesel per hour is 86,000 Kcal / h, a difference of 3,613 Kcal / h is deducted, which corresponds to radiation losses of the system.
    5 Although reference has been made to a specific embodiment of the invention, it is clear to one skilled in the art that the described system is susceptible to numerous variations and modifications, and that all the mentioned details can be substituted by other technically equivalent ones. , without departing from the scope of protection defined by the appended claims.
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    权利要求:
    Claims (8)
    [1]
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    1. Energy production system for a motor vehicle or for a mobile generator set equipped with a combustion engine (M), characterized in that it comprises a thermodynamic working circuit (1) that uses carbon dioxide to obtain energy by means of an expansion turbine (T) of said carbon dioxide, and by the fact that it comprises a refrigeration circuit (3) provided with a heat exchanger (6) sized to condense a fraction of the ejected carbon dioxide by means of a refrigerant fluid by the turbine (T), including the same refrigeration circuit (3) a second exchanger (8) sized to evaporate carbon dioxide already condensed by the same refrigerant fluid, once said refrigerant fluid has been compressed to provide heat.
    [2]
    2. System according to revindication 1, wherein said thermodynamic working circuit (1) comprises a heat exchanger (12) sized to cool the temperature of the carbon dioxide expelled by the turbine (T) before said carbon dioxide enters the exchanger (6) where it will be condensed.
    [3]
    3. System according to revindication 2, where said heat exchanger (12) is sized to cool the temperature of the carbon dioxide expelled by the turbine by carbon dioxide evaporated in the refrigeration circuit exchanger (8) (3).
    [4]
    4. System according to any of claims 2 or 3, wherein said thermodynamic working circuit (1) comprises a heat exchanger (11) sized to increase the temperature of the evaporated carbon dioxide to a temperature equal to or greater than 300 ° C by the heat from the exhaust gases of the combustion engine M of said vehicle or generator set.
    [5]
    5. System according to revindication 1, wherein said thermodynamic working circuit (1) comprises a heat exchanger (10) sized to increase the temperature of the carbon dioxide previously evaporated in the refrigeration circuit (3) by means of heat from a circuit (4) Refrigeration of the combustion engine of the vehicle or generator set.
    [6]
    6. System according to claim 1, wherein said refrigeration circuit (3) includes a machine for mechanically compressing the refrigerant fluid and means for actuating
    5 said machine by mechanical energy from the combustion engine (M)
    of said vehicle or generator set.
    [7]
    7. System according to claim 1, wherein said refrigeration circuit (3) is sized to condense a fraction of the carbon dioxide at a temperature
    10 equal to or less than -6 ° C and at a pressure equal to or less than 30 bar, and to evaporate said
    condensed carbon dioxide at a temperature equal to or greater than 30 ° C and at a pressure equal to or greater than 65 bar.
    [8]
    8. Automobile vehicle or generator set provided with a combustion engine (M) comprising said energy production system according to any of the
    claims 1 to 7, wherein said carbon dioxide expansion turbine (T) is connected to the engine (M) of said vehicle or generator set, a fraction of the mechanical energy coming from the turbine (T) being susceptible to being used for drive the vehicle or generator set.
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    同族专利:
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    ES2643860B1|2018-09-05|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US3324652A|1964-07-08|1967-06-13|Commissariat Energie Atomique|Process and apparatus for power production|
    DE3032921A1|1980-09-02|1982-04-15|Bernhard Dipl.-Ing. 5223 Nümbrecht Drescher|Combined thermal engine and heat pump circuit - uses low temp. heat source to input heat to pump circuit|
    DE19632019C1|1996-08-08|1997-11-20|Thomas Sturm|Heat engine operation method|
    WO2007121603A1|2006-04-20|2007-11-01|Heig-Vd|Method for generating and/or accumulating and restoring cold and device for implementing said method|
    US20150033737A1|2011-12-02|2015-02-05|Mikhael Mitri|Device and method for utilizing the waste heat of an internal combustion engine, in particular for utilizing the waste heat of a vehicle engine|
    GB2523264A|2015-03-24|2015-08-19|Daimler Ag|Thermal management system for a vehicle, in particular a commercial vehicle|
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