WO2013002018A1 - Cycle de rankine - Google Patents

Cycle de rankine Download PDF

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Publication number
WO2013002018A1
WO2013002018A1 PCT/JP2012/064992 JP2012064992W WO2013002018A1 WO 2013002018 A1 WO2013002018 A1 WO 2013002018A1 JP 2012064992 W JP2012064992 W JP 2012064992W WO 2013002018 A1 WO2013002018 A1 WO 2013002018A1
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WO
WIPO (PCT)
Prior art keywords
pressure
refrigerant
temperature
cooling water
rankine cycle
Prior art date
Application number
PCT/JP2012/064992
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English (en)
Japanese (ja)
Inventor
榎島　史修
井口　雅夫
英文 森
Original Assignee
株式会社豊田自動織機
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Application filed by 株式会社豊田自動織機 filed Critical 株式会社豊田自動織機
Publication of WO2013002018A1 publication Critical patent/WO2013002018A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/065—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle the combustion taking place in an internal combustion piston engine, e.g. a diesel engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K15/00—Adaptations of plants for special use
    • F01K15/02—Adaptations of plants for special use for driving vehicles, e.g. locomotives
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting from exhaust energy
    • F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting from exhaust energy the devices using heat

Definitions

  • This invention relates to the Rankine cycle.
  • the Rankine cycle is a heat exchanger that superheats the working fluid by exchanging heat between the heat medium containing heat exhausted from the internal combustion engine and the working fluid, and obtains power by expanding the working fluid in the superheated steam state.
  • the expander rotates a rotating body such as a turbine by expanding the working fluid, thereby converting the energy at the time of expansion of the working fluid into a rotational driving force, and the converted rotational driving force is used as a generator or the like. To be transmitted as power.
  • Patent Document 1 a refrigerant pump and a first heat exchanger that exchange heat between the refrigerant and the cooling water (heat medium) of the internal combustion engine in the middle of a flow path for sending the refrigerant (working fluid) to the expander, and the refrigerant And the Rankine cycle which has arrange
  • the refrigerant pump is operated when the cooling water temperature reaches 90 ° C. or higher, and the refrigerant circulating through the Rankine cycle thereby exchanges heat with cooling water of about 90 to 100 ° C. in the first heat exchanger.
  • the second heat exchanger exchanges heat with the exhaust gas of 300 to 400 ° C. to become superheated steam of about 120 to 130 ° C. and flows into the expander.
  • the amount of heat absorbed by the refrigerant through heat exchange with the heat medium made of cooling water or exhaust gas varies greatly depending on the pressure of the refrigerant even if the temperature of the heat medium is constant. Furthermore, the amount of heat absorbed by the refrigerant in heat exchange varies depending on the temperature of the heat medium even if the pressure of the refrigerant is constant. Therefore, the amount of heat absorbed by the refrigerant through heat exchange with the heat medium is affected by the pressure of the refrigerant and the temperature of the heat medium.
  • This invention was made in order to solve such a problem, and Rankine cycle which aims at increase of the heat absorption amount of the refrigerant
  • the purpose is to provide.
  • a Rankine cycle includes a first heat exchanger that exchanges heat between a working fluid and a low-temperature side heat medium in a circulation path of the working fluid, Heat exchanger for exchanging heat, fluid expander for generating driving force by expanding the working fluid, condenser for condensing the working fluid, and fluid pumping device for transferring the working fluid to the first heat exchanger
  • the pressure detector that detects the pressure of the working fluid at the inlet of the fluid expander
  • the temperature detector that detects the temperature of the low-temperature heat medium flowing into the first heat exchanger
  • the fluid A pressure adjusting means for adjusting the pressure of the working fluid at the inlet of the expander; and a control device for controlling the pressure adjusting means.
  • the control device operates according to the temperature of the low temperature side heat medium detected by the temperature detector. Saturated steam of fluid Calculating a target pressure to be under pressure or, as the pressure detected by the pressure detector reaches the target pressure,
  • the heat absorption amount of the working fluid in the first heat exchanger can be increased by controlling the temperature of the heat medium in association with the pressure of the working fluid.
  • Rankine cycle 101 according to an embodiment of the present invention and the configuration around it will be described.
  • a vehicle (not shown) including an engine 10 includes a Rankine cycle 101.
  • the Rankine cycle 101 forms a circulation path that sequentially connects the pump 111, the cooling water boiler 112, the waste gas boiler 113, the expander 114, the condenser 115, the receiver 116, and the subcooler 117, and the refrigerant that is the working fluid flows. It is supposed to be.
  • the pump 111 is operated to pump a fluid, and in this embodiment, the liquid is pumped.
  • the pump 111 shares its drive shaft 119 with the expander 114.
  • a pulley 119b is coupled to the drive shaft 119 via an electromagnetic clutch 119a.
  • the pulley 119b is connected to an engine pulley 10b connected to an engine drive shaft 10a extending from the engine 10 by a drive belt 10c.
  • the electromagnetic clutch 119a can connect or disconnect the drive shaft 119 and the pulley 119b, and is electrically connected to the ECU 140, which is a vehicle control device, to control the connecting / disconnecting operation thereof. For this reason, the rotation speed of the pump 111 depends on the rotation speed of the engine 10 or the expander 114.
  • the pump 111 constitutes a fluid pressure feeding device
  • the engine drive shaft 10a, the engine pulley 10b, the drive belt 10c, the pulley 119b, the electromagnetic clutch 119a, and the drive shaft 119 constitute a power transmission mechanism.
  • the discharge port on the downstream side of the pump 111 communicates with the refrigerant inlet of the cooling water boiler 112 via the flow path portions 1a and 1b.
  • the cooling water for cooling the engine that flows through the cooling water circuit 20 of the engine 10 and the refrigerant flow and exchange heat with each other, whereby the refrigerant can be heated.
  • the cooling water constitutes a low temperature side heat medium
  • the cooling water boiler 112 constitutes a first heat exchanger.
  • the cooling water circuit 20 extends from the engine 10 and is connected to a water pump 21 integral with the engine 10 to form a circulation flow path, a return-side water flow path 20b and 20c, and a feed-side water flow path 20a. And a radiator 22 provided between the return side water flow path 20b and a branch water flow path 20d branched from the middle of the feed side water flow path 20a and connected to the connecting portion of the return side water flow paths 20b and 20c. . And the cooling water boiler 112 is provided in the middle of the branched water flow path 20d.
  • the water pump 21 sucks the cooling water from the return side water flow path 20 c and circulates the inside of the engine 10, and then flows out into the feed side water flow path 20 a to circulate the cooling water circuit 20.
  • the radiator 22 cools the cooling water by exchanging heat between the cooling water flowing inside and the surrounding air.
  • a thermostat 23 is provided at a connection portion between the branch water channel 20d and the return side water channels 20b and 20c.
  • the thermostat 23 operates corresponding to the temperature of the cooling water.
  • the return side water flow path 20b is used to raise the temperature of the low-temperature cooling water.
  • the branch water flow path 20d is communicated with the return-side water flow path 20c, and the cooling water is not circulated to the radiator 22.
  • the thermostat 23 communicates between the return-side water flow paths 20b and 20c and distributes the cooling water to the radiator 22 in order to cool the cooling water.
  • the thermostat 23 gives priority to cooling of the cooling water, and therefore between the branch water channel 20d and the return side water channel 20c.
  • the radiator 22 is circulated through all the cooling water.
  • the refrigerant outlet of the cooling water boiler 112 communicates with the refrigerant inlet of the waste gas boiler 113 via the flow path portion 1c.
  • the refrigerant flowing out of the cooling water boiler 112 and the exhaust gas of the exhaust system 30 of the engine 10 circulate and exchange heat with each other, whereby the refrigerant can be heated.
  • the waste gas boiler 113 is provided in the middle of the exhaust flow path 30a which connects the engine 10 in the exhaust system 30 to the muffler 30b.
  • the exhaust gas constitutes a high temperature side heat medium
  • the waste gas boiler 113 constitutes a second heat exchanger.
  • the refrigerant outlet of the waste gas boiler 113 communicates with the inlet of the expander 114 that is a fluid expander via the flow path portion 1d.
  • the expander 114 rotates the drive shaft 119 together with a rotating body such as a turbine by expanding the high-temperature and high-pressure refrigerant after being heated by the cooling water boiler 112 and the waste gas boiler 113, thereby rotating driving force. It is a fluid device that gets the work by.
  • an alternator 118 having a power generation function is provided between the expander 114 and the pump 111, and the alternator 118 shares a drive shaft 119.
  • the rotational driving force generated by the expander 114 can integrally drive the alternator 118 and the pump 111 via the driving shaft 119, and the driving force of the pump 111 applied by the engine 10 is the driving shaft.
  • the alternator 118 and the expander 114 can be integrally driven via 119.
  • the flow path portions 1a, 1b, 1c, and 1d constitute the first flow path 1 that is a high-pressure side flow path of the refrigerant.
  • the alternator 118 is electrically connected to the converter 120, and the converter 120 is electrically connected to the battery 121.
  • the alternator 118 When the expander 114 rotates and drives the drive shaft 119, the alternator 118 generates an alternating current and sends it to the converter 120.
  • the converter 120 converts the sent alternating current into a direct current and supplies it to the battery 121 for charging.
  • the outlet of the expander 114 communicates with the inlet of the capacitor 115 through the flow path portion 2a.
  • the refrigerant flows and exchanges heat with the air around the condenser 115, whereby the refrigerant can be cooled and condensed.
  • the capacitor 115 constitutes a condenser.
  • the outlet of the capacitor 115 communicates with the inlet of the receiver 116 via the flow path portion 2b, and further, the outlet of the receiver 116 communicates with the inlet of the subcooler 117 via the flow path portion 2c.
  • the receiver 116 is a gas-liquid separator that includes a liquid refrigerant therein, and removes vapor components, moisture, foreign matters, and the like of the refrigerant contained in the refrigerant. Inside the subcooler 117, the liquid refrigerant sent from the receiver 116 flows and exchanges heat with the air around the subcooler 117, whereby the refrigerant can be supercooled.
  • the outlet of the subcooler 117 communicates with the suction port of the pump 111 via the flow path portion 2d, and the refrigerant flowing out of the subcooler 117 is sucked by the pump 111 and pumped again to circulate through the Rankine cycle 101.
  • the flow path portions 2a, 2b, 2c, and 2d constitute the second flow path 2 that is a low pressure side flow path of the refrigerant.
  • the Rankine cycle 101 also includes a bypass channel 3 that communicates the channel portion 1 a of the first channel 1 with the second channel 2.
  • a bypass channel 3 that communicates the channel portion 1 a of the first channel 1 with the second channel 2.
  • one end of the bypass channel 3 is connected to the connecting portion of the channel 1a and the channel 1b of the first channel 1, and the other end of the bypass channel 3 is The second channel 2 is connected to the channel 2b.
  • the Rankine cycle 101 includes a flow rate adjustment valve 130 that can open or close the bypass flow path 3 and adjust the cross-sectional area of the bypass flow path 3 in the middle of the bypass flow path 3. Yes.
  • the flow rate adjusting valve 130 is electrically connected to the ECU 140 and its operation is controlled.
  • the bypass flow path 3 and the flow rate adjusting valve 130 constitute a pressure adjusting means.
  • the Rankine cycle 101 includes a pressure sensor 131 that detects the pressure of the refrigerant flowing through the flow path portion 1d in the vicinity of the inlet of the expander 114 in the flow path portion 1d of the first flow path 1.
  • the pressure sensor 131 detects the pressure of the refrigerant at the inlet of the expander 114, that is, the pressure of the refrigerant flowing into the expander 114, and sends the detected refrigerant pressure information to the electrically connected ECU 140.
  • the pressure of the refrigerant is the same between the flow path portions regardless of whether the flow rate adjustment valve 130 is opened or closed. It may be provided in any of 1a to 1c.
  • the pressure sensor 131 constitutes a pressure detector.
  • the Rankine cycle 101 includes a cooling water temperature sensor 132 that detects the temperature of the circulating cooling water between the engine 10 and the branch water passage 20d in the feed water passage 20a of the cooling water circuit 20.
  • the cooling water temperature sensor 132 detects the temperature of the cooling water that is sent out from the engine 10 and before the heat exchange action is received by the cooling water boiler 112 or the radiator 22, and the temperature of the cooling water detected by the electrically connected ECU 140. Send information.
  • the cooling water temperature sensor 132 constitutes a temperature detector.
  • the water pump 21 is also operated to pump the cooling water.
  • the cooling water pumped out from the engine 10 circulates through the cooling water circuit 20 and returns to the engine 10 again.
  • the thermostat 23 shuts off the communication between the return side water flow paths 20b and 20c so that the cooling water is not cooled by the radiator 22 until the cooling water reaches the first operating temperature (90 ° C.) or higher.
  • the branch water channel 20d is communicated with the return side water channel 20c.
  • the cooling water exchanges heat with the refrigerant in the cooling water boiler 112.
  • exhaust gas is discharged from the started engine 10 to the exhaust system 30.
  • the discharged exhaust gas flows through the waste gas boiler 113 during the distribution process, and is then discharged from the muffler 30b to the outside of the vehicle.
  • the exhaust gas exchanges heat with the refrigerant in the waste gas boiler 113.
  • ECU 140 connects electromagnetic clutch 119a.
  • the rotational driving force of the engine 10 is transmitted to the drive shaft 119 via the engine drive shaft 10a, the engine pulley 10b, the drive belt 10c, the pulley 119b, and the electromagnetic clutch 119a, whereby the drive shaft 119 is pumped.
  • 111, the alternator 118, and the expander 114 are driven integrally.
  • the driven pump 111 pumps the refrigerant in the liquid state toward the cooling water boiler 112, and the driven expander 114 rotates the rotating body such as a turbine, thereby causing the flow path of the first flow path 1 to flow.
  • the refrigerant in the part 1 d is depressurized and sent to the flow path part 2 a of the second flow path 2.
  • the refrigerant is subjected to adiabatic pressurization by being pumped by the pump 111.
  • the temperature of the cooling water is assumed to be a temperature Tw1 (in this embodiment, 80 ° C.).
  • Tw1 in this embodiment, 80 ° C.
  • FIG. 2 the state change of the refrigerant in the circulation process of the Rankine cycle 101 is shown on the ph diagram of the refrigerant.
  • the ph diagram has an orthogonal coordinate system in which the vertical axis represents the refrigerant pressure (unit: MPa) and the horizontal axis represents the refrigerant enthalpy (unit: kJ / kg). Further, the region where the refrigerant is in the supercooled liquid state is indicated by the supercooled liquid region SL, the region where the refrigerant is in the wet steam state is indicated by the wet steam region WS, and the region where the refrigerant is in the superheated steam state is the superheated steam region. It is indicated by SS. A saturated liquid line ⁇ is shown at the boundary between the supercooled liquid region SL and the wet steam region WS, and a dry saturated vapor line ⁇ is shown at the boundary between the wet steam region WS and the superheated steam region SS.
  • the refrigerant state changes along the first cycle S1 having a trapezoidal shape with the points A1, B1, C1, and D1 as vertices. proceed.
  • the refrigerant raises its pressure from pressure P 1 to pressure P 2 and increases its temperature, and changes from the point A1 to the point B1.
  • the refrigerant increases its enthalpy from ha to hb.
  • the state of the refrigerant between point A1 and point B1 maintains a liquid state (supercooled liquid state) in the supercooled liquid region SL.
  • the refrigerant changes from a point B1 to a point P 2 Te (a point between the point B1 and the point C1 in the first cycle S1), and increases its enthalpy to he.
  • the point P 2 Te is an intersection of the isobaric line of the pressure P 2 and the isotherm of the temperature Te.
  • the refrigerant in the state between point B1 of the point P 2 Te will remain liquid in the supercooled liquid region SL (supercooled liquid state).
  • the refrigerant that has flowed out of the cooling water boiler 112 passes through the flow path portion 1c, flows into the waste gas boiler 113, is heated at an equal pressure by exchanging heat with the exhaust gas that circulates therein, and rises in temperature. It flows out as high-temperature and high-pressure superheated steam.
  • the refrigerant is further raised the temperature to maintain the pressure in the pressure P 2.
  • the refrigerant changes from the point P 2 Te to the state of the point C1, and increases its enthalpy to hc. Note that the state of the refrigerant between point P 2 Te and point C1 changes from the liquid state in the supercooled liquid region SL to the superheated steam state in the superheated steam region SS.
  • the high-temperature and high-pressure refrigerant in the superheated steam state that has flowed out of the waste gas boiler 113 passes through the flow path portion 1 d and flows into the expander 114.
  • the refrigerant adiabatically expands using the refrigerant pressure difference between the upstream-side channel portion 1 d and the downstream-side channel portion 2 a, and then flows out in a high-temperature and low-pressure superheated steam state.
  • the expansion energy of the refrigerant is converted into rotational energy as regenerative energy and transmitted to the drive shaft 119.
  • the refrigerant expands to reduce the pressure from the pressure P 2 to the pressure P 1 and to decrease the temperature. At this time, the refrigerant changes from the point C1 to the point D1, and reduces its enthalpy to hd. In addition, the state of the refrigerant
  • the regenerative energy transmitted to the drive shaft 119 is not only applied as a rotational drive force to the alternator 118 and the pump 111 but also transmitted to the engine 10 to assist the rotational drive.
  • Alternator 118 is operated by an applied rotational driving force to generate an alternating current, and the generated alternating current is converted into a direct current by converter 120 and then charged to battery 121.
  • the superheated vapor refrigerant flowing out of the expander 114 passes through the flow path portion 2a and flows into the condenser 115, where it is cooled at an equal pressure by exchanging heat with the surrounding air, that is, outside air, and condensed. And flows out in a liquid state.
  • the isobaric cooling step by the capacitor 115 the refrigerant lowers its temperature, to maintain the pressure in the pressure P 1.
  • the refrigerant changes from a point D1 to a point F1 (a point between the point D1 and the point A1 in the first cycle S1), and reduces the enthalpy to hf. Note that the state of the refrigerant between the point D1 and the point F1 changes from the superheated steam state in the superheated steam region SS to the saturated liquid state.
  • the liquid refrigerant flowing out of the condenser 115 passes through the flow path portion 2b and flows into the receiver 116, passes through the liquid refrigerant stored inside the receiver 116, and flows out into the flow path portion 2c.
  • the refrigerant passes through the receiver 116, the vapor component, moisture, foreign matter, and the like of the refrigerant contained are removed.
  • the refrigerant flowing out of the receiver 116 passes through the flow path portion 2c and flows into the subcooler 117, where it is further cooled at the same pressure (supercooled) by exchanging heat with the outside air in the subcooler 117. And flows out to the flow path portion 2d. Further, the refrigerant in the flow path portion 2d is sucked into the pump 111 and pumped again, and circulates through the Rankine cycle 101.
  • the refrigerant In the isobaric cooling step by the sub-cooler 117, the refrigerant, the temperature further lowers, the pressure is maintained at the pressure P 1.
  • the refrigerant changes from the point F1 to the state of the point A1, and reduces the enthalpy to ha.
  • the state of the refrigerant between point F1 and point A1 changes from the saturated liquid state to the supercooled liquid state in the supercooled liquid region SL.
  • the refrigerant increases the pressure from the pressure P 1 to the pressure P 3 and increases the temperature, and further increases the enthalpy from ha to hb2,
  • the state changes from point A1 to point B2.
  • the state of the refrigerant between point A1 and point B2 maintains a liquid state (supercooled liquid state).
  • the refrigerant temperature is raised to a temperature Te by heat exchange with the cooling water temperature Tw1, to maintain the pressure in the pressure P 3.
  • the refrigerant, from the point B2, and change in the state of (a point between point B2 and point C2 in the second cycle S2) P 3 Te point of the pressure P 3 and the temperature Te, the enthalpy in he2 increase.
  • the pressure P 3 has a saturated vapor pressure less than Pse of the refrigerant in the temperature Te, thereby, the point P 3 Te, is located within the superheated steam region SS. For this reason, the state of the refrigerant between point B2 and point P 3 Te changes from the liquid state to the superheated vapor state through the wet vapor state, and the refrigerant includes latent heat of vaporization.
  • the amount of heat absorbed by the refrigerant from the cooling water in the cooling water boiler 112 is obtained by multiplying the flow rate of the refrigerant in the cooling water boiler 112 by the amount of change in the enthalpy of the refrigerant before and after heat exchange. It is proportional to the pressure of the refrigerant in the boiler 112 multiplied by the amount of change in the enthalpy of the refrigerant before and after heat exchange. For this reason, the heat absorption amount of the refrigerant in the cooling water boiler 112 is also greatly increased in the second cycle S2 as compared with the first cycle S1.
  • the refrigerant flowing out from the cooling water boiler 112 performs exhaust gas heat exchanger in the waste gas boiler 113, the refrigerant, the point P to maintain the pressure with further raise its temperature to a pressure P 3 3 Change from Te to point C2 and increase its enthalpy to hc2.
  • the state of the refrigerant between point P 3 Te and point C2 maintains the superheated steam state.
  • the adiabatic expansion process in which the refrigerant flowing out from the waste gas boiler 113 is expanded in expander 114, the refrigerant, from the point C2 to lower the temperature with decreasing pressure P 1 of the pressure from the pressure P 3 of the point D2 state And the enthalpy is reduced to hd2.
  • coolant between the point C2 and the point D2 maintains a superheated steam state.
  • the refrigerant pressure point F1 (first from point D2 and maintained at a pressure P 1 along with lowering the temperature
  • the state changes to the state between the point D2 and the point A1 in the two cycles S2, and the enthalpy is reduced to hf.
  • the state of the refrigerant between point D2 and point F1 changes from the superheated steam state to the saturated liquid state.
  • the isobaric cooling step in which the refrigerant flowing out from the capacitor 115 performs outside air exchanges heat with sub-cooler 117 after passing through the receiver 116, the refrigerant in the point to maintain pressure in the pressure P 1 with further lowering the temperature
  • the state changes from F1 to the state of point A1, and the enthalpy is reduced to ha.
  • the state of the refrigerant between point F1 and point A1 changes from the saturated liquid state to the supercooled liquid state.
  • the enthalpy ⁇ he2 obtained from the coolant by the cooling water boiler 112 in the second cycle S2 is significantly increased with respect to the enthalpy ⁇ he obtained from the coolant by the cooling water boiler 112 in the first cycle S1.
  • the amount of heat absorbed by the coolant in the cooling water boiler 112 is also greatly increased in the second cycle S2 than in the first cycle S1.
  • the increase in the amount of heat absorbed by the cooling water boiler 112 is caused by changing the refrigerant pressure in the cooling water boiler 112 (that is, the refrigerant pressure in the flow path portions 1a to 1d of the first flow path 1) and the refrigerant pressure at the temperature Te. This can be achieved by controlling the saturated vapor pressure Pse or less.
  • the pressure of the refrigerant in the cooling water boiler 112 to a high pressure so as to be as close as possible to the saturated vapor pressure Pse, the upstream side flow passage portion 1d and the downstream side flow passage portion 2a. It is possible to ensure a high differential pressure of the refrigerant between the two and the amount of regenerative energy obtained in the expander 114.
  • the ECU 140 sets the pressure of the refrigerant in the cooling water boiler 112, that is, the first pressure.
  • the target pressure of the refrigerant pressure in the flow path portions 1a to 1d of the single flow path 1 is set based on the saturation vapor pressure Pse of the refrigerant at the temperature Te, and the flow pressure adjusting valve 130 is controlled so that the refrigerant pressure is changed to the target pressure.
  • the ECU 140 sets the target pressure of the refrigerant based on the temperature Tw of the cooling water before heat exchange and the saturated vapor pressure Pse indicated by the refrigerant that has reached the temperature Te by exchanging heat with the cooling water. .
  • the ECU 140 uses the coolant temperature detected by the coolant temperature sensor 132 and the refrigerant temperature and saturated vapor pressure stored in advance to make the detected coolant temperature the coolant temperature.
  • the refrigerant that is, the saturated vapor pressure of the refrigerant corresponding to the cooling water temperature. Further, the ECU 140 sets a pressure obtained by reducing a predetermined amount of pressure ⁇ p from the calculated saturated vapor pressure as the target pressure of the refrigerant in the flow path portions 1a to 1d of the first flow path 1.
  • This pressure ⁇ p is caused by heat loss due to the heat exchange capacity of the cooling water boiler 112, the thermal conductivity of the material, etc., and the cooling water temperature Tw before the heat exchange in the cooling water boiler 112 and the refrigerant temperature Te after the heat exchange. (Refer to FIG. 2) and preset in correspondence with the temperature difference ⁇ Te between them and stored in the ECU 140.
  • ECU140 controls the opening degree of the flow regulating valve 130, The flow rate of the refrigerant flowing into the cooling water boiler 112 is changed, and control is performed so that the detected pressure of the pressure sensor 131 in the flow path portion 1d becomes the target pressure. That is, when the detected pressure of the pressure sensor 131 is lower than the target pressure, the ECU 140 decreases the opening degree of the flow rate adjustment valve 130 and increases the refrigerant flow rate of the flow path unit 1d, thereby increasing the flow rate of the flow path unit 1d. Increase refrigerant pressure.
  • the ECU 140 increases the opening of the flow rate adjustment valve 130 to decrease the refrigerant flow rate of the flow path unit 1d, thereby reducing the flow rate of the flow path unit 1d. Reduce refrigerant pressure.
  • the target pressure calculation method is changed depending on the temperature region of the cooling water, and the relationship between the target pressure and the cooling water temperature detected by the cooling water temperature sensor 132 in this case is shown in the graph of FIG. Is shown in FIG.
  • the graph of FIG. 3 has an orthogonal coordinate system in which the vertical axis is the refrigerant pressure (unit is MPa) and the horizontal axis is the cooling water temperature (unit is ° C.).
  • the relationship between the target pressure and the cooling water temperature is shown by a target pressure graph Pt which is a solid line graph, and the relationship between the saturated vapor pressure of the refrigerant corresponding to the cooling water temperature and the cooling water temperature is indicated by a one-dot chain line.
  • the target saturated vapor pressure graph Pst is shown.
  • the target pressure graph Pt the portion Pta corresponding to the range of the coolant temperature TwL1 to TwH is equal to the target saturation vapor pressure graph Pst in the negative direction of the refrigerant pressure (vertical axis negative direction).
  • the target saturated vapor pressure graph Pst is translated by the temperature ⁇ Te in the positive direction of the cooling water temperature (the positive direction of the horizontal axis) in the present embodiment. Identical. Therefore, the target pressure of the part Pta is set by the above-described calculation method.
  • the target pressure at the part Pta is lower than the saturated vapor pressure of the refrigerant corresponding to the cooling water temperature by a predetermined pressure ⁇ p, and increases with an increase in the cooling water temperature and decreases in the cooling water temperature. It decreases with this, and is proportional to the cooling water temperature.
  • the ECU 140 adjusts the flow rate so that the detected pressure of the pressure sensor 131 becomes the target pressure on the target pressure graph Pt when the coolant temperature detected by the coolant temperature sensor 132 is in the range of the temperature TwL1 to TwH.
  • the valve 130 is controlled.
  • the temperature TwL1 constitutes a first predetermined temperature
  • the temperature TwH constitutes a second predetermined temperature.
  • a portion Ptb corresponding to a range lower than the cooling water temperature TwL1 is a horizontal straight line with the target pressure being constant, with the saturated vapor pressure PsL of the refrigerant at the temperature TwL as the target pressure. is there.
  • the temperature TwL is a temperature set in advance as a low cooling water temperature that reduces the efficiency of the engine 10 when the temperature is lower than the temperature TwL, and is set to 60 ° C. in the present embodiment.
  • temperature TwL1 is the cooling water temperature which hits the intersection of the site
  • the temperature TwL1 is also a temperature obtained by adding the temperature ⁇ Te to the temperature TwL.
  • the ECU 140 controls the flow rate adjustment valve 130 so that the pressure detected by the pressure sensor 131 does not become less than the saturated vapor pressure PsL of the refrigerant at the temperature TwL.
  • the refrigerant having a pressure equal to or higher than the saturated vapor pressure PsL of the refrigerant at the temperature TwL (60 ° C.) always does not include latent heat of vaporization even if heat exchange is performed with the cooling water below the temperature TwL.
  • the amount of heat absorbed from can be kept low. Therefore, the cooling water can be controlled so as not to be lower than the temperature TwL.
  • the cooling water temperature varies as follows. .
  • the cooling water temperature decreases and falls below the saturation temperature TwL of the refrigerant, the amount of heat that the refrigerant can absorb from the cooling water at the moment when the cooling water falls is greatly reduced, so that the cooling water reduces the amount of heat released to the refrigerant.
  • the temperature drop stops and the temperature rises.
  • the cooling water temperature exceeds the refrigerant saturation temperature TwL due to the temperature rise, the amount of heat absorbed by the refrigerant increases and the cooling water temperature decreases again.
  • the cooling water is controlled so as not to drop below the refrigerant saturation temperature TwL.
  • a part Ptc corresponding to the range exceeding the cooling water temperature TwH is a horizontal straight line that keeps the target pressure constant at the refrigerant target pressure PH corresponding to the cooling water temperature TwH.
  • the cooling water temperature TwH is the temperature of the cooling water whose saturation vapor pressure corresponds to the upper limit pressure PH set for the piping of the first flow path 1 and the expander 114, and in this embodiment, the thermostat 23 starts to open. It is the same as the first operating temperature (90 ° C.).
  • the ECU 140 controls the flow rate adjustment valve 130 so that the pressure detected by the pressure sensor 131 becomes the target pressure PH. Thereby, it can prevent that the 1st flow path 1 and the expander 114 are exposed to abnormally high pressure.
  • the ECU 140 is described so as to calculate the target pressure by calculation.
  • the graph of FIG. 3 may be stored as a map, and the target pressure may be calculated based on the stored map.
  • the cooling water boiler 112 that exchanges heat between the refrigerant and the cooling water
  • the waste gas boiler 113 that exchanges heat between the refrigerant and the exhaust gas.
  • An expander 114 that generates a driving force by expanding the refrigerant, a condenser 115 that condenses the refrigerant, and a pump 111 that transfers the refrigerant to the cooling water boiler 112 are sequentially provided.
  • the Rankine cycle 101 includes a pressure sensor 131 that detects the pressure of the refrigerant at the inlet of the expander 114, a cooling water temperature sensor 132 that detects the temperature of the cooling water flowing into the cooling water boiler 112, and a refrigerant at the inlet of the expander 114.
  • the bypass flow path 3 and the flow rate adjusting valve 130 for adjusting the pressure of the ECU and the ECU 140 for controlling the flow rate adjusting valve 130 are provided.
  • the ECU 140 calculates a target pressure that is equal to or lower than the saturated vapor pressure of the refrigerant corresponding to the temperature of the cooling water detected by the cooling water temperature sensor 132, and the flow rate so that the pressure detected by the pressure sensor 131 becomes the target pressure.
  • the regulating valve 130 is controlled.
  • the bypass flow path 3 and the flow rate adjustment valve 130 adjust the refrigerant pressure at the inlet of the expander 114 by adjusting the amount of refrigerant flowing into the cooling water boiler 112.
  • the pressure of the refrigerant that exchanges heat with the cooling water in the cooling water boiler 112 is controlled to be a target pressure that is equal to or lower than the saturated vapor pressure of the refrigerant corresponding to the temperature of the cooling water.
  • the amount of heat of the refrigerant after heat exchange with the cooling water is a large amount of heat including the latent heat of evaporation.
  • the pressure of the refrigerant is controlled to be larger than the saturated vapor pressure of the refrigerant corresponding to the temperature of the cooling water, the amount of heat of the refrigerant after heat exchange with the cooling water becomes a small amount of heat not including the latent heat of evaporation. . Therefore, Rankine cycle 101 makes it possible to increase the amount of heat absorbed by the refrigerant from the cooling water in cooling water boiler 112 by controlling the temperature of the cooling water and the pressure of the refrigerant in association with each other as described above.
  • the target pressure of the refrigerant is set to increase in accordance with the saturated vapor pressure of the refrigerant corresponding to the cooling water temperature, which rises as the cooling water temperature rises. Therefore, the coolant flow rate of the cooling water boiler 112 can be increased as the cooling water temperature increases. Therefore, in the cooling water boiler 112, the heat absorption amount of the refrigerant from the cooling water can be increased in accordance with the increase in the cooling water temperature, and the temperature increase of the cooling water can be suppressed.
  • the bypass flow path 3 communicates the flow path portion 1 a of the refrigerant from the pump 111 to the cooling water boiler 112 to the second flow path 2 of the refrigerant from the expander 114 to the pump 111.
  • the Rankine cycle 101 makes it possible to efficiently use the thermal energy acquired by the cooling water boiler 112 and the waste gas boiler 113.
  • the bypass flow path 3 through which the refrigerant having a high density before being heated flows the necessary flow rate of the refrigerant can be secured even if the diameter and the flow rate adjustment valve 130 are small.
  • the adjustment valve 130 can be downsized.
  • the bypass flow path 3 connects the flow path section 1 a to the flow path section 2 b between the condenser 115 and the pump 111 in the second flow path 2 of the refrigerant from the expander 114 toward the pump 111. To do. As a result, the refrigerant flowing through the bypass flow path 3 flows downstream of the condenser 115, so that the pressure loss in the condenser 115 is not increased, and the refrigerant pressure in the flow path portion 2a between the expander 114 and the condenser 115 is increased. Can be suppressed.
  • the differential pressure of the refrigerant between the upstream-side channel portion 1d and the downstream-side channel portion 2a of the expander 114 can be ensured high, sufficient regenerative energy obtained by the expander 114 is ensured. It becomes possible to do.
  • the bypass flow path 3 connected between the condenser 115 and the subcooler 117 is pump cavitation (refrigeration of refrigerant) that occurs when the flow path section 1a is bypassed to the flow path section 2d between the subcooler 117 and the pump 111. ) Can be prevented.
  • the bypass flow path 3 connected between the condenser 115 and the pump 111 is a refrigerant flowing into the condenser 115 that occurs when the flow path section 1a is bypassed to the flow path section 2a between the expander 114 and the condenser 115. It is possible to prevent a decrease in the amount of heat released from the capacitor 115 due to a decrease in the temperature of the inflowing refrigerant. This decrease in the heat dissipation amount in the capacitor 115 increases the pressure of the second flow path 2, and causes the refrigerant differential pressure between the upstream flow path section 1 d and the downstream flow path section 2 a of the expander 114. Therefore, the regenerative energy obtained by the expander 114 is reduced.
  • PsL saturated vapor pressure of refrigerant at temperature TwL
  • TwL1 TwL [60 ° C. at the cooling water temperature at which the efficiency of the engine 10 decreases) + ⁇ Te)
  • TwL1 TwL [60 ° C. at the cooling water temperature at which the efficiency of the engine 10 decreases) + ⁇ Te
  • the ECU 140 sets the target pressure to the temperature TwL ( The flow rate adjustment valve 130 is controlled so that the saturated vapor pressure PsL of the refrigerant at 60 ° C. and the detected pressure of the pressure sensor 131 is equal to or higher than the saturated vapor pressure PsL or the saturated vapor pressure PsL. It is not something.
  • the ECU 140 sets the target pressure so as to increase from the saturated vapor pressure PsL of the refrigerant at the temperature TwL as the cooling water temperature decreases.
  • the flow rate adjustment valve 130 may be controlled so that the detected pressure becomes the target pressure. Even with such control, the refrigerant has a pressure larger than the saturated vapor pressure of the refrigerant corresponding to the cooling water temperature, so that the latent heat of vaporization is converted into the amount of heat absorbed from the cooling water by heat exchange in the cooling water boiler 112. It can be excluded.
  • the ECU 140 does not include control for changing the setting of the target pressure related to the cooling water temperature with the first predetermined temperature TwL1 as a boundary, and the target pressure of the part Ptb of the target pressure graph Pt is changed to the part Pta.
  • the target pressure based on the saturated vapor pressure of the refrigerant corresponding to the cooling water temperature may be used.
  • the ECU 140 includes the refrigerant saturated vapor pressure PsL corresponding to the coolant temperature TwL as a lower limit value of the target pressure, and adjusts the flow rate so that the pressure detected by the pressure sensor 131 does not fall below the saturated vapor pressure PsL.
  • the valve 130 may be controlled.
  • the refrigerant has a pressure larger than the saturated vapor pressure of the refrigerant corresponding to the cooling water temperature, the amount of heat absorbed from the cooling water by heat exchange in the cooling water boiler 112 is reduced to the latent heat of evaporation. Can be kept low.
  • the ECU 140 determines the saturation vapor pressure PsL of the refrigerant at the temperature TwL (60 ° C.).
  • the flow rate adjustment valve 130 may be controlled so that a constant pressure larger than the target pressure is set as the target pressure and the detected pressure of the pressure sensor 131 becomes the target pressure. Even with such control, the refrigerant can keep the amount of heat absorbed from the cooling water through heat exchange in the cooling water boiler 112 low without including latent heat of evaporation.
  • the ECU 140 does not include control for changing the setting of the target pressure related to the cooling water temperature with the second predetermined temperature TwH (90 ° C.) as a boundary, and the target pressure of the part Ptc of the target pressure graph Pt. May be set as the target pressure based on the saturated vapor pressure of the refrigerant corresponding to the cooling water temperature in the same manner as the portion Pta.
  • the ECU 140 uses the flow rate adjustment valve 130 to adjust the cross-sectional area of the bypass flow path 3, thereby detecting the pressure detected by the pressure sensor 131 (the pressure of the refrigerant flowing into the cooling water boiler 112). ) Is adjusted, but is not limited to this.
  • the alternator 118 of the embodiment may be a motor generator 218 having functions of a motor and a generator.
  • the ECU 140 may adjust the number of rotations of the pump 111 and the expander 114 by controlling the number of rotations of the drive shaft 119 driven by the motor generator 218 to adjust the detected pressure of the pressure sensor 131.
  • FIG. 6 the alternator 118 of the embodiment may be a motor generator 218 having functions of a motor and a generator.
  • the pump 111 may be driven by the motor 322 without being connected to the engine 10.
  • the ECU 140 can adjust the rotational speed of the pump 111 and the detected pressure of the pressure sensor 131 by controlling the rotational speed of the motor 322.
  • the expander 114 connects the drive shaft 114a and the pulley 119b that is rotationally driven by the engine 10 via the electromagnetic clutch 119a, and the alternator 118 shares the drive shaft 114a.
  • the pump 111 is not connected to the alternator 118 and the expander 114, but is connected only to the pulley 119b, and the expander 114 and the alternator 118 are connected to each other by the drive shaft 114a. It may be.
  • the ECU 140 can adjust the rotation speed of the expander 114 and adjust the detected pressure of the pressure sensor 131 by changing the load of the alternator 118.
  • the expander 114 may be capable of arbitrarily changing the suction volume. By changing the suction volume, the flow rate (volume flow rate) of the refrigerant transferred by the expander 114 is changed, and accordingly, the refrigerant pressure in the upstream flow path of the expander 114 is changed. The pressure can be adjusted.
  • the bypass flow path 3 communicates the flow path portion 1a of the first flow path 1 with the flow path portion 2b of the second flow path 2, but is not limited thereto. Not.
  • the bypass flow path 3 may be connected to any of the flow path portions 2a, 2c, and 2d with respect to the second flow path 2.
  • the Rankine cycle 101 of the embodiment includes the two heat exchangers of the cooling water boiler 112 and the waste gas boiler 113, but is not limited thereto, and may include three or more.
  • the Rankine cycle 101 may include a heat exchanger between the refrigerant of the air conditioner and the refrigerant of the Rankine cycle 101.
  • the heat exchanger between the cooling water of the motor used in the hybrid car and the refrigerant of the Rankine cycle 101 is provided. You may have.
  • a target pressure that is equal to or lower than the saturated vapor pressure of the refrigerant corresponding to the temperature of the heat medium of the heat exchanger selected from the heat exchanger and the cooling water boiler 112 is set, and the first flow path is set based on the target pressure.
  • the pressure of one refrigerant By controlling the pressure of one refrigerant, the heat absorption amount of the refrigerant in the selected heat exchanger can be increased.

Abstract

L'invention concerne un cycle de Rankine (101) dans lequel sont agencés, dans l'ordre, sur un trajet de circulation de frigorigène, une chaudière à eau de refroidissement (112), une chaudière à gaz résiduaire (113), un appareil d'extension (114), un condensateur (115) et une pompe (111). Ce cycle de Rankine (101) est équipé : d'un capteur de pression (131) qui détecte la pression d'un frigorigène à l'entrée de l'appareil d'extension (114); d'un capteur de température d'eau de refroidissement (132) qui détecte la température de l'eau de refroidissement introduite dans la chaudière à eau de refroidissement (112); d'un trajet de contournement (3) ainsi que d'une valve régulatrice de débit (130) destinés à ajuster la pression du frigorigène à l'entrée de l'appareil d'extension (114); et d'un bloc de commande électronique (140) qui commande la valve régulatrice de débit (130). Le bloc de commande électronique (140) calcule une pression cible inférieure ou égale à la pression de vapeur saturante du frigorigène par rapport à la température de l'eau de refroidissement détectée par le capteur de température d'eau de refroidissement (132), et assure la commande de la valve régulatrice de débit (130) afin que la pression détectée par le capteur de pression (131) atteigne la pression cible.
PCT/JP2012/064992 2011-06-30 2012-06-12 Cycle de rankine WO2013002018A1 (fr)

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FR3022496A1 (fr) * 2014-06-19 2015-12-25 Renault Sas Systeme de propulsion pour vehicule automobile hybride comprenant des moyens de recuperation de l'energie thermique perdue

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