• 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:
    An arrangement and a method for converting thermal energy to mechanical energy includes a circulation unit (4) a refrigerant in the a circuit (3), an evaporator (6) for the refrigerant, a turbine (9) driven by vaporised refrigerant, a condenser (12) cooling the refrigerant to condense, and an accumulator tank (14) for storage of the refrigerant is not being circulated in the line circuit (3). A control device estimates the degree of filling of the line circuit (3) with refrigerant at which the turbine (9) achieves a substantially optimum effect, and controls the flow of refrigerant between the line circuit (3) and the accumulator tank (14) to achieve the estimated degree of filling the line circuit (3) with refrigerant.
    公开号:SE1051269A1
    申请号:SE1051269
    申请日:2010-12-01
    公开日:2012-06-02
    发明作者:Ola Hall
    申请人:Scania Cv Ab；
    IPC主号:
    专利说明:

    output shaft of the internal combustion engine and / or to a generator that generates electrical energy.
    SUMMARY OF THE INVENTION The object of the present invention is to provide an arrangement capable of converting heat energy into mechanical energy in an efficient manner.
    This object is achieved with the arrangement of the kind mentioned in the introduction, which is characterized by the features stated in the characterizing part of claim 1. The arrangement includes the basic components that are part of a conventional WI-IR system. The efficiency of a WI-IR system varies with the amount of refrigerant in the wiring circuit. An optimal filling amount of the refrigerant in a WHR system is generally dimensioned for the operating condition when it is maximally loaded. During other operating conditions when the WHR system is not loaded to the maximum, a lower efficiency is obtained. According to the present invention, the filling amount of the refrigerant in the line circuit at which the turbine obtains a substantially optimal operation under prevailing operating conditions is estimated, after which the filling amount is adjusted to the estimated value if necessary. Thus, the line circuit will always have a filling amount which results in a substantially optimal operation of the turbine and a substantially optimal production of mechanical energy.
    According to a preferred embodiment of the invention, the control system is adapted to estimate the filling amount of the refrigerant in the line circuit at which the refrigerant which is led into the evaporator has substantially no subcooling. As this is the case, no heat energy needs to be wasted on first heating the refrigerant to the evaporation temperature before the evaporation process starts. All heat energy from the heat source can in this case be used to evaporate the refrigerant and to give it a possible overheating before it is led to the turbine. The evaporated refrigerant can thus give the turbine a substantially optimal operation and a substantially optimal production of mechanical energy under all operating conditions. According to a preferred embodiment of the present invention, said circulating means is a pump arranged between the condenser and the evaporator line.
    In order for the pump to function in a desired way, all refrigerant that is led to the pump must be in liquid form. To ensure this, it is appropriate that the refrigerant leaving the condenser has some subcooling. However, this subcooling should be as small as possible and can be of the order of 1 to 3 degrees. When this is the case, the refrigerant led to the evaporator may have the lowest possible subcooling. An undercooling of the above-mentioned size affects the efficiency only marginally and the turbine in this case obtains a substantially optimal operation. The arrangement may comprise a heat exchanger between the pump and the evaporator in the line circuit, in which the refrigerant is adapted to be heated before it is led into the evaporator. In this case, the refrigerant can obtain a heating in the heat exchanger which compensates for a possible subcooling in the condenser.
    In this case, the refrigerant can be led into the evaporator without any subcooling.
    According to a preferred embodiment of the present invention, said control means comprises a control unit adapted to receive information from at least one sensor which senses a parameter by means of which the control unit estimates the filling amount of the refrigerant at which the turbine obtains a substantially optimal power. The control unit may be a computer unit with suitable software for this purpose. Said sensor may be adapted to sense the temperature and / or pressure of the refrigerant in a position between the condenser and the evaporator in the line circuit. With knowledge of the refrigerant pressure and temperature, the size of the subcooling can be determined with the aid of, for example, a Mollier diagram. Alternatively, the control unit can receive information from sensors that sense a parameter with which the current load on the evaporator and / or the condenser can be estimated. In this case, the control unit may include stored information regarding the appropriate filling amount of the refrigerant as the evaporator and / or condenser at different loads.
    According to another preferred embodiment of the present invention, said control means comprise at least one line extending between the line system and the accumulator tank and means adapted to conduct refrigerant between the line circuit and the accumulator tank during times when the filling amount of the refrigerant needs to be adjusted in the line. With such a line, the filling amount of the refrigerant in the line circuit can be adjusted in a simple and efficient manner under different operating conditions.
    Said line may be connected to the line circuit in a position where the refrigerant has a different pressure than in the accumulator tank and that said means comprises a valve in the line which is adjustable in a closed position and at least an open position. In the case where the line is connected to the line circuit in a position where the refrigerant has a lower pressure than in the accumulator tank, a replenishment of refrigerant is provided in the line circuit when the valve opens. In the case where the line is connected to the line circuit in a position where the refrigerant has a higher pressure than in the accumulator tank, a discharge of refrigerant from the line circuit is provided when the valve is open. Alternatively, the said means comprises a pump which is arranged in the line between the line circuit and the accumulator tank. Advantageously, the pump is reversible so that it is possible to both supply refrigerant to the line circuit and drain refrigerant from the line circuit via one and the same line. According to an embodiment of the present invention, said heat source is a hot medium in a vehicle driven by an internal combustion engine. In vehicles, there are many media that can be a heat source for the above-mentioned arrangements. The exhaust gases of the internal combustion engine constitute such a heat source. Other possible heat sources are the coolant that circulates in the vehicle's cooling system. Additional possible heat sources are charge air and recirculating exhaust gases that are led to the internal combustion engine. The above-mentioned media receive varying flows and temperatures under different operating conditions of the internal combustion engine. With the arrangement defined above, the turbine can obtain a substantially optimal operation even when the fate and temperature of the above-mentioned media vary.
    The object mentioned in the introduction is also achieved with the method according to claim 11.
    The method comprises the steps of estimating the filling amount of the refrigerant at which the turbine obtains a substantially optimal power and controlling the flow of refrigerant between the line circuit and the accumulator tank in such a way that the estimated filling amount of the refrigerant is obtained in the line system.
    BRIEF DESCRIPTION OF THE DRAWINGS In the following, preferred examples of the invention are described by way of example with reference to the accompanying drawings, in which Fig. 1 shows an arrangement for converting heat energy to mechanical energy, Fig. 2 shows a fate diagram showing a method of operation of the arrangement in Fig. 1 and Fig. 3 shows an arrangement according to an alternative embodiment for converting heat energy into mechanical energy.
    DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS OF THE INVENTION Fig. 1 shows an arrangement comprising a plurality of components used in a conventional WHR (Waste Heat Recovery) system. WHR systems are used in various contexts to convert heat energy into mechanical energy. In this case, the arrangement is used to extract mechanical energy from heat energy in exhaust gases discharged from an internal combustion engine 2 in a schematically shown vehicle 1. The arrangement comprises a line circuit 3 with a circulating refrigerant. The refrigerant is in liquid form when it is pressurized in the line circuit 3 by means of a pump 4. The pump 4 conducts the refrigerant to a heat exchanger 5, which can be a so-called recuperator. The refrigerant is led from the heat exchanger 5 to an evaporator 6. The refrigerant is heated in the evaporator 6 by exhaust gases which are led in an exhaust line 7 of the internal combustion engine 2. The temperature and fate of the exhaust gas in the exhaust line 7 varies with the load of the internal combustion engine 2. If the internal combustion engine 2 is a diesel engine, the exhaust gases can have a temperature of up to about 600 - 700 ° C.
    The refrigerant is adapted to provide a heating in the evaporator 6 of the exhaust gases so that it evaporates. The formed gaseous refrigerant is led from the evaporator 6 to a superheater 8. If necessary, the refrigerant here can obtain an extra heating in the superheater 8 so that all the refrigerant is guaranteed to be in gaseous form when it reaches a turbine 9. The refrigerant then expands through the turbine 9 Some of the heat energy in the refrigerant is converted here into mechanical energy. The turbine 9 in this case drives a generator 10. Thus, the recovered mechanical energy is converted into electrical energy. The electrical energy is stored in an energy storage 11. The stored electrical energy can advantageously be used for operation of the vehicle 1 or for operation of any component in the vehicle. Alternatively, the turbine 9 may be connected to a flywheel or similar mechanical energy storage unit which is connectable to the driveline of the vehicle 1. When the flywheel is connected to the driveline, the vehicle 1 provides an extra driving force.
    After the refrigerant has expanded in the turbine 9, it provides a lower pressure and a lower temperature. The gaseous refrigerant is then passed through the above-mentioned heat exchanger 5 where it provides a smaller cooling. The gaseous refrigerant is then passed to a condenser 12 where it is cooled to a temperature at which it condenses. In the example shown, the refrigerant in the condenser 12 is cooled by means of air with ambient temperature. An air-tight 13 sucks in the ambient air which is led through the condenser 12. The gaseous refrigerant thus changes to liquid in the condenser 12. If cold coolant is available, the gaseous refrigerant can alternatively be cooled by coolant in the condenser. The liquid refrigerant is sucked from the condenser 12 to the pump 4. The liquid refrigerant which reaches the heat exchanger 5 has a lower temperature than the gaseous refrigerant which is passed through the heat exchanger in a position upstream of the condenser 12. The liquid refrigerant thus provides a smaller the heat exchanger 5 before it reaches the evaporator 6. The circulating refrigerant provides a pressure drop in the turbine 9. The pump 4 supplies a corresponding increase in pressure of the refrigerant. The refrigerant thus has a higher pressure in the part of the line circuit 3 extending from the pump 4 to the turbine 9 than in the part of the line circuit 3 extending from the turbine 9 to the pump 4 with respect to the intended direction of circulation of the refrigerant in the line circuit 3. With With the help of the turbine 9, the heat energy from the exhaust gases in the exhaust line 7 can be recovered and converted into mechanical energy. The mechanical energy is in this case converted into electrical energy in the generator 11. The mechanical or electrical energy is used to advantage for the operation of the vehicle 1. The vehicle 1 can thus obtain an increased capacity without supply of extra fuel to the internal combustion engine 2.
    The arrangement also comprises an accumulator tank 14 which stores refrigerant which is not used in the line circuit 3. The accumulator tank 14 is adapted to store the refrigerant at a temperature and a pressure so that the refrigerant is present in suitable amounts in liquid phase and in gas phase in the accumulator tank 14. The arrangement comprises a first line The first line 15 extends from an upper portion of the accumulator tank 14 to an area of the line circuit 3 where the refrigerant has a lower pressure than in the accumulator tank 14. When the valve 16 is opened, gaseous refrigerant is led from the accumulator tank 14 , via the first line 15, to the line circuit 3, The arrangement comprises a second line 17 with a valve 18. The second line 17 extends from a lower portion of the accumulator tank 14 to an area of the line circuit 3 where the refrigerant has a higher pressure than in the accumulator tank. 14. When the valve 17 is opened, liquid refrigerant is led from the line circuit 3 to the accumulator tank 14, via the second line 17. A temperature sensor 19 and a pressure sensor 20 are arranged in the line circuit 3 in a position downstream of the condenser 12 and upstream of the pump 4. A control unit 21 is adapted to receive information from the temperature sensor 19 and the pressure sensor 20. during operation. The control unit 21 is adapted to open one of the valves 16, 18 when the filling amount of the refrigerant is to be adjusted in the line circuit 3.
    When the load of the internal combustion engine 2 changes, the exhaust gases in the exhaust line 7 receive a varying flow and a varying temperature. During operating conditions when the internal combustion engine 2 is heavily loaded, a large flow of exhaust gases with a high temperature is obtained through the exhaust line 7. During such operating conditions, the turbine 9 can recover relatively much heat energy from the exhaust gases. When the internal combustion engine 2 is under low load, a considerably smaller flow of exhaust gases with a lower temperature is obtained through the exhaust line 7. During such operating fi standstill, the turbine 9 can recover significantly less heat energy from the exhaust gases.
    However, it is desirable to recover as much heat energy as possible from the exhaust gases under all operating conditions. An optimal recovery of heat energy is obtained during the times when the liquid refrigerant which is led into the evaporator 6 has no subcooling. When this is the case, essentially no heat energy from the exhaust gases need be used to heat the refrigerant in the evaporator 6 to the evaporation temperature, but essentially all heat energy from the exhaust gases can be used for the evaporation work of the refrigerant in the evaporator 6. In this case an optimal amount of heat energy can be converted to mechanical energy. in the turbine 9.
    Fig. 2 shows a flow chart describing a method of operating the arrangement of Fig. 1. At 22 the process starts. The control unit 20 receives, at 23, during operation information regarding the temperature t and pressure p from the temperature sensor 15 and the pressure sensor 16. The temperature sensor 15 and the pressure sensor 16 are placed in a position in the line circuit 3 downstream of the condenser 12 and upstream of the pump 4 with respect to on the intended flow direction of the refrigerant in the line system3. With this information, the control unit can estimate the subcooling At in the condenser 12 by means of, for example, a Mollier diagram for the refrigerant in question. To ensure that no refrigerant in liquid form reaches the pump 4, a subcooling in the form of a reference value Atmf of some degrees can be accepted. The reference value of subcooling The Atmfi condenser advantageously corresponds to the temperature increase which the refrigerant receives in the heat exchanger 5. Thus, liquid refrigerant without subcooling can be led into the evaporator 6. The control unit 21 compares, at 25, whether the actual subcooling At of the refrigerant corresponds to the reference value. If this is the case, the control unit 21 states that the amount of refrigerant in the line circuit 3 is correct. The process then restarts at 22.
    In cases where the control unit 21 states that the subcooling At is not equal to the reference value Atmf. continues procedure at 26. The control unit 21 determines here whether the subcooling At is too small or too large in relation to the reference value Atæf. If the subcooling At of the refrigerant in the condenser 12 is too great, the control unit 21, at 27, opens the valve 16 in the first line 15. The first line 15 is thus connected to a portion of the line circuit 3 where there is a lower pressure than in the accumulator tank 14. Thus, gaseous refrigerant is sucked into the line circuit 3 when the valve 16 is open. The control unit 21 can, at 27, also estimate how much refrigerant needs to be added to eliminate the difference between the actual subcooling At and the reference value Atwf.
    The control unit 21 can keep the first valve 16 open for a period of time so that the estimated amount of the refrigerant is added. The process then restarts at 22. As the amount of refrigerant increases in the line circuit 3, more refrigerant accumulates in the condenser 12 and the subcooling of the refrigerant which imparts the condenser 12 decreases.
    If the subcooling At of the refrigerant in the condenser 12 is too small, the control unit 21, at 28, opens the valve 18 in the second line 17. The second line 17 is thus connected to a portion of the line circuit 3 where there is a higher pressure than in the accumulator - the tank 14. Thus, liquid refrigerant is pushed into the accumulator tank 14 from the line circuit 3 when the valve 18 is open. The control unit 21 can, at 28, also estimate the amount of refrigerant that needs to be led out of the line circuit 3 in order to eliminate the difference between the actual subcooling At and the reference value Atwf. The control unit 21 can keep the valve 18 open for a period of time so that the estimated amount of refrigerant is led out of the line circuit 3. The process then starts again at 22. As the amount of refrigerant decreases in the line circuit 3, less refrigerant accumulates in the condenser 12 and the subcooling of that refrigerant leaving the capacitor 12 increases. The procedure then restarts at 22.
    Fig. 3 shows an alternative embodiment of the arrangement. In this case, the accumulator tank 14 is connected to the line circuit 3 by a line 29. A reversible pump 30 is arranged in the line 29. The control unit 14 can here control the pump 30 so that the filling amount of the refrigerant can both be increased and decreased in the line circuit 3. In this case, the Control Unit 21 receives information from a temperature sensor 19 and a pressure sensor 20 arranged in the line circuit 3 in a position downstream of the heat exchanger 5 and upstream of the evaporator 6. In this case, the Control Unit 21 can directly determine whether the liquid refrigerant is led to the evaporator has subcooling or not.
    The invention is in no way limited to the embodiment described in the drawing but can be varied freely within the scope of the claims. In the embodiments shown, the heat in the exhaust gases is used as a heat source to evaporate the refrigerant and drive the turbine. However, it is possible to use arbitrary heat sources to evaporate the refrigerant in the evaporator and in particular heat sources that have a varying heat output and need to be cooled.
    Such heat sources can be coolant in the vehicle's cooling system, charge air that is led to supercharged combustion engines and recirculating exhaust gases.
    权利要求:
    Claims (11)
    [1]
    Arrangement for converting heat energy into mechanical energy, the arrangement comprising a line circuit (3), circulating means (4) for circulating a refrigerant in the line circuit (3), an evaporator (6) in which the refrigerant is adapted to evaporate by a heat source (7), a turbine (9) adapted to be driven by the evaporated refrigerant, a condenser (12) in which the refrigerant is adapted to be cooled so that it condenses and an accumulator tank (14 ) for storing the refrigerant which is not circulated in the line circuit (3), characterized in that the arrangement comprises control means adapted to estimate the filling amount of the refrigerant in the line circuit (3) at which the turbine (9) obtains a substantially optimal power under prevailing operating conditions and that control fl the fate of the refrigerant between the line circuit (3) and the accumulator tank (14) in such a way that the estimated amount of filling of the refrigerant is obtained in the line system (3).
    [2]
    Arrangement according to claim 1, characterized in that said control means is adapted to estimate the filling amount of the refrigerant in the line circuit (3) at which the refrigerant which is led into the evaporator (6) has substantially no subcooling.
    [3]
    Arrangement according to claim 1 or 2, characterized in that said circulating means is a pump arranged between the condenser (12) and the evaporator (6) in the line circuit (3) -
    [4]
    Arrangement according to claim 3, characterized in that the arrangement comprises a heat exchanger (5) between the pump (4) and the evaporator (6) in the line circuit (3), in which the refrigerant is adapted to be heated before it is led into the evaporator. (6).
    [5]
    Arrangement according to any one of the preceding claims, characterized in that said control means comprises a control unit (21) adapted to receive information from at least one sensor (19, 20) which senses a parameter by means of which the control unit (21) estimates the amount of filling of the refrigerant at which the turbine (9) obtains a substantially optimal effect.
    [6]
    Arrangement according to claim 5, characterized in that said sensor is adapted to sense the temperature and / or pressure of the refrigerant in a position between the condenser (12) and the evaporator (6) in the line circuit (3). 10 15 20 25 30 11
    [7]
    Arrangement according to any one of the preceding claims, characterized in that said control means comprise at least one conduit (15, 17, 29) extending between the conduit system (3) and the accumulator tank (14) and adapted means (16, 18, 30) to direct the refrigerant between the line circuit (3) and the accumulator tank (14) at times when the filling amount of the refrigerant needs to be adjusted in the line circuit (3).
    [8]
    Arrangement according to claim 7, characterized in that the line (15, 17) is connected to the line circuit (3) in a position where the refrigerant has a different pressure than in the accumulator tank and that said flow means comprises a valve (16, 18) in the conduit (15, 17) which is adjustable in a closed position and at least one open position.
    [9]
    Arrangement according to claim 7, characterized in that said means comprises a pump (30) arranged in the line (29) between the line circuit (3) and the accumulator tank (14).
    [10]
    Arrangement according to any one of the preceding claims, characterized in that said heat source consists of a hot medium in a vehicle driven by an internal combustion engine (2).
    [11]
    A method for converting heat energy into mechanical energy by means of a line circuit (3) comprising a pump (4) for circulating the refrigerant in the line circuit (3), an evaporator (6) in which the refrigerant is adapted to evaporate in contact with a heat source (7), a turbine (9) adapted to be driven by the evaporated refrigerant, a condenser (12) in which the refrigerant is adapted to be cooled so that it condenses and an accumulator tank (14) for storing refrigerant not circulated in the line circuit (3), characterized in that the method comprises the steps of estimating the filling amount of the refrigerant in the line circuit (3) at which the turbine (9) obtains a substantially optimum power under prevailing operating conditions and controlling the fate of the refrigerant between the line circuit (3) and the accumulator tank (14) in such a way that the estimated amount of refrigerant is obtained in the line system (3).
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    SE1051269A|SE535453C2|2010-12-01|2010-12-01|Arrangement and method for converting thermal energy into mechanical energy|SE1051269A| SE535453C2|2010-12-01|2010-12-01|Arrangement and method for converting thermal energy into mechanical energy|
    RU2013129757/06A| RU2544621C2|2010-12-01|2011-11-22|Design and method of heat energy conversion to mechanical energy|
    KR1020137017102A| KR101782075B1|2010-12-01|2011-11-22|Arrangement and method for converting thermal energy to mechanical energy|
    BR112013012575A| BR112013012575A2|2010-12-01|2011-11-22|arrangement and method for converting thermal energy to mechanical energy|
    US13/990,073| US9127573B2|2010-12-01|2011-11-22|Arrangement and method for converting thermal energy to mechanical energy|
    JP2013541956A| JP2014501874A|2010-12-01|2011-11-22|Apparatus and method for converting thermal energy into mechanical energy|
    PCT/SE2011/051399| WO2012074457A1|2010-12-01|2011-11-22|Arrangement and method for converting thermal energy to mechanical energy|
    EP11845430.5A| EP2646671B1|2010-12-01|2011-11-22|Arrangement and method for converting thermal energy to mechanical energy|
    CN201180057787.XA| CN103249938B|2010-12-01|2011-11-22|Arrangement and method for converting thermal energy to mechanical energy|
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