WO2013046969A1 - 廃熱利用装置 - Google Patents
廃熱利用装置 Download PDFInfo
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- WO2013046969A1 WO2013046969A1 PCT/JP2012/070652 JP2012070652W WO2013046969A1 WO 2013046969 A1 WO2013046969 A1 WO 2013046969A1 JP 2012070652 W JP2012070652 W JP 2012070652W WO 2013046969 A1 WO2013046969 A1 WO 2013046969A1
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- WIPO (PCT)
- Prior art keywords
- expander
- refrigerant
- waste heat
- heat utilization
- engine
- Prior art date
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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
- F01K23/10—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 with exhaust fluid of one cycle heating the fluid in another cycle
- F01K23/101—Regulating means specially adapted therefor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
- F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
- F02G5/02—Profiting from waste heat of exhaust gases
- F02G5/04—Profiting from waste heat of exhaust gases in combination with other waste heat from combustion engines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
- F01D15/02—Adaptations for driving vehicles, e.g. locomotives
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
- F01D15/12—Combinations with mechanical gearing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
- F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
- F02G5/02—Profiting from waste heat of exhaust gases
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P2060/00—Cooling circuits using auxiliaries
- F01P2060/16—Outlet manifold
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P2060/00—Cooling circuits using auxiliaries
- F01P2060/18—Heater
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Definitions
- This invention relates to a waste heat utilization device, in particular, an integrated Rankine cycle and refrigeration cycle.
- a Rankine cycle system that reuses engine waste heat as energy is known.
- the engine waste heat is recovered, the Rankine cycle is operated by the waste heat, and rotational energy is obtained by an expander (turbine).
- a turbine driven by steam recovered from engine waste heat in a superheater, a first pulley connected to a turbine shaft by an electromagnetic clutch, a second pulley provided on a crankshaft, and Power recovery means for recovering power from the turbine to the crankshaft by a belt stretched between the first pulley and the second pulley, and when the turbine over-rotation is determined, the first pulley is connected to the turbine shaft by an electromagnetic clutch.
- a waste heat recovery device including an ECU for adjusting a load applied to a turbine shaft (JP2010-101283A).
- the present invention has been made in view of such problems, and an object of the present invention is to provide a waste heat utilization device that can detect an increase in friction of an expander in a waste heat utilization device that recovers waste heat of an engine. To do.
- a heat exchanger that recovers engine waste heat into a refrigerant, an expander that generates power using the refrigerant that has exited the heat exchanger, and condensing the refrigerant that has exited the expander
- a waste heat utilization apparatus comprising: a Rankine cycle including a condenser and a refrigerant pump that supplies refrigerant from the condenser to a heat exchanger; and a power transmission mechanism that transmits power regenerated by the expander to the engine.
- the power transmission mechanism includes intermittent means for intermittently transmitting power between the expander and the engine, and the expander includes rotational speed detection means for detecting the rotational speed of the expander, and intermittent means.
- Friction increase detection means for detecting an increase in friction of the expander is provided based on an increase in the rotation speed of the expander detected by the rotation speed detection means.
- FIG. 1 is a schematic configuration diagram of an integration cycle according to an embodiment of the present invention.
- FIG. 2A is a schematic cross-sectional view of an expander pump according to an embodiment of the present invention.
- FIG. 2B is a schematic cross-sectional view of the refrigerant pump according to the embodiment of the present invention.
- FIG. 2C is a schematic cross-sectional view of an expander according to an embodiment of the present invention.
- FIG. 3 is a schematic view showing the function of the refrigerant system valve according to the embodiment of the present invention.
- FIG. 4 is a schematic configuration diagram of a hybrid vehicle according to the embodiment of the present invention.
- FIG. 5 is a schematic perspective view of the engine according to the embodiment of the present invention.
- FIG. 6 is a schematic view of the hybrid vehicle according to the embodiment of the present invention as viewed from below.
- FIG. 7A is a characteristic diagram of the Rankine cycle operation region of the embodiment of the present invention.
- FIG. 7B is a characteristic diagram of the Rankine cycle operation region of the embodiment of the present invention.
- FIG. 8 is a timing chart showing a state in which the hybrid vehicle is accelerated while assisting the rotation of the engine output shaft by the expander torque according to the embodiment of the present invention.
- FIG. 9 is a timing chart showing a state of restart from stop of Rankine cycle operation according to the embodiment of the present invention.
- FIG. 10 is an explanatory diagram showing an operation for detecting an increase in friction of the expander.
- FIG. 11 is an explanatory diagram showing another example of the operation for detecting the increase in friction of the expander.
- FIG. 1 is a schematic configuration diagram showing the entire system of a Rankine cycle which is a premise of the present invention.
- the Rankine cycle 31 of FIG. 1 has a configuration in which the refrigerant and the condenser 38 are shared by the refrigeration cycle 51, and the cycle in which the Rankine cycle 31 and the refrigeration cycle 51 are integrated is hereinafter referred to as “integrated cycle 30”. It expresses.
- FIG. 4 is a schematic configuration diagram of the hybrid vehicle 1 on which the integrated cycle 30 is mounted.
- the integrated cycle 30 includes a circuit (passage) through which the refrigerant of the Rankine cycle 31 and the refrigeration cycle 51 circulates and components such as a pump, an expander, and a condenser provided in the middle of the circuit, and a circuit for cooling water and exhaust ( This refers to the entire system including the passages).
- the engine 2 In the hybrid vehicle 1, the engine 2, the motor generator 81, and the automatic transmission 82 are connected in series, and the output of the automatic transmission 82 is transmitted to the drive wheels 85 via the propeller shaft 83 and the differential gear 84.
- a first drive shaft clutch 86 is provided between the engine 2 and the motor generator 81.
- One of the frictional engagement elements of the automatic transmission 82 is configured as a second drive shaft clutch 87.
- the first drive shaft clutch 86 and the second drive shaft clutch 87 are connected to the engine controller 71, and their connection / disconnection (connected state) is controlled according to the driving conditions of the hybrid vehicle.
- the engine 2 when the vehicle speed is in the EV traveling region where the efficiency of the engine 2 is poor, the engine 2 is stopped, the first drive shaft clutch 86 is disconnected, and the second drive shaft clutch 87 is connected. Thus, the hybrid vehicle 1 is caused to travel only with the driving force of the motor generator 81. On the other hand, when the vehicle speed deviates from the EV travel region and shifts to the Rankine cycle operation region, the engine 2 is operated to operate the Rankine cycle 31 (described later).
- the engine 2 includes an exhaust passage 3, and the exhaust passage 3 includes an exhaust manifold 4 and an exhaust pipe 5 connected to a collective portion of the exhaust manifold 4.
- the exhaust pipe 5 branches off from the bypass exhaust pipe 6 in the middle, and a waste heat recovery unit 22 for exchanging heat between the exhaust and the cooling water is provided in the exhaust pipe 5 in a section bypassed by the bypass exhaust pipe 6. Is provided.
- the waste heat recovery unit 22 and the bypass exhaust pipe 6 are disposed between the underfloor catalyst 88 and the sub-muffler 89 downstream thereof as a waste heat recovery unit 23 in which these are integrated.
- the cooling water at about 80 to 90 ° C. leaving the engine 2 flows separately into a cooling water passage 13 that passes through the radiator 11 and a bypass cooling water passage 14 that bypasses the radiator 11. Thereafter, the two flows are merged again by a thermostat valve 15 that determines the distribution of the flow rate of the cooling water flowing through both passages 13 and 14, and then returns to the engine 2 via the cooling water pump 16.
- the cooling water pump 16 is driven by the engine 2, and the rotation speed of the cooling water pump 16 is synchronized with the engine rotation speed.
- the thermostat valve 15 relatively increases the amount of cooling water passing through the radiator 11 by increasing the valve opening on the cooling water passage 13 side when the cooling water temperature is high, and on the cooling water passage 13 side when the cooling water temperature is low.
- the amount of cooling water passing through the radiator 11 is relatively reduced by reducing the valve opening.
- the coolant temperature is particularly low, such as before the engine 2 is warmed up, the radiator 11 is completely bypassed and the entire amount of coolant flows through the bypass coolant passage 14 side.
- the valve opening on the bypass cooling water passage 14 side is not fully closed, and when the flow rate of the cooling water flowing through the radiator 11 is increased, the flow rate of the cooling water flowing through the bypass cooling water passage 14 is
- the thermostat valve 15 is configured so that the flow does not stop completely.
- a bypass cooling water passage 14 that bypasses the radiator 11 is branched from the cooling water passage 13 and directly connected to a heat exchanger 36, which will be described later, and from the cooling water passage 13 to recover waste heat.
- the bypass cooling water passage 14 includes a heat exchanger 36 that exchanges heat between the cooling water and the refrigerant of the Rankine cycle 31.
- the heat exchanger 36 is an integrated evaporator and superheater.
- two cooling water passages 36a and 36b are arranged in almost one row, and a refrigerant passage 36c through which the refrigerant of the Rankine cycle 31 flows is adjacent to the cooling water passage so that heat can be exchanged between the refrigerant and the cooling water.
- the passages 36a, 36b, and 36c are configured such that the refrigerant and the cooling water in the Rankine cycle 31 are in opposite directions when viewed from the whole heat exchanger 36.
- one cooling water passage 36 a located on the upstream side (left side in FIG. 1) for the refrigerant of Rankine cycle 31 is interposed in the first bypass cooling water passage 24.
- a Rankine cycle 31 that flows through the refrigerant passage 36c is formed by directly introducing the cooling water from the engine 2 into the cooling water passage 36a in the left side portion of the heat exchanger including the cooling water passage 36a and the refrigerant passage portion adjacent to the cooling water passage. It is an evaporator for heating the refrigerant.
- Cooling water that has passed through the waste heat recovery device 22 is introduced into the other cooling water passage 36b located downstream (right in FIG. 1) for the refrigerant of the Rankine cycle 31 via the second bypass cooling water passage 25.
- the right side portion of the heat exchanger (downstream side for the refrigerant of Rankine cycle 31) composed of the cooling water passage 36b and the refrigerant passage portion adjacent to the cooling water passage 36b is the cooling water obtained by further heating the cooling water at the outlet of the engine 2 by exhaust.
- the superheater superheats the refrigerant flowing through the refrigerant passage 36c by being introduced into the cooling water passage 36b.
- the cooling water passage 22 a of the waste heat recovery unit 22 is provided adjacent to the exhaust pipe 5. By introducing the cooling water at the outlet of the engine 2 into the cooling water passage 22a of the waste heat recovery unit 22, the cooling water can be heated to, for example, about 110 to 115 ° C. by high-temperature exhaust.
- the cooling water passage 22a is configured so that the exhaust and cooling water flow in opposite directions when the waste heat recovery device 22 is viewed from above.
- a control valve 26 is interposed in the second bypass cooling water passage 25 provided with the waste heat recovery unit 22.
- the control valve 26 prevents the engine water temperature indicating the temperature of the cooling water inside the engine 2 from exceeding an allowable temperature (for example, 100 ° C.) for preventing deterioration of the efficiency of the engine 2 and knocking.
- an allowable temperature for example, 100 ° C.
- the opening degree of the control valve 26 is decreased.
- the engine water temperature approaches the permissible temperature the amount of cooling water passing through the waste heat recovery device 22 is reduced, so that it is possible to reliably prevent the engine water temperature from exceeding the permissible temperature.
- a bypass exhaust pipe 6 that bypasses the waste heat recovery unit 22 and a thermostat valve 7 that controls the exhaust passage amount of the waste heat recovery unit 22 and the exhaust passage amount of the bypass exhaust pipe 6 are provided in the bypass exhaust pipe 6. Provide at the bifurcation. The thermostat valve 7 is based on the temperature of the cooling water exiting the waste heat recovery unit 22 so that the valve opening degree does not exceed a predetermined temperature (for example, a boiling temperature of 120 ° C.). Adjusted.
- the heat exchanger 36, the thermostat valve 7, and the waste heat recovery unit 22 are integrated as a waste heat recovery unit 23, and are disposed in the middle of the exhaust pipe under the floor in the center of the vehicle width direction.
- the cooling water passage 13 side of the thermostat valve 15 If the temperature of the cooling water from the bypass cooling water passage 14 toward the thermostat valve 15 is sufficiently lowered by exchanging heat with the refrigerant of the Rankine cycle 31 by the heat exchanger 36, for example, the cooling water passage 13 side of the thermostat valve 15 The amount of cooling water passing through the radiator 11 is relatively reduced. Conversely, when the temperature of the cooling water from the bypass cooling water passage 14 toward the thermostat valve 15 becomes high due to the Rankine cycle 31 not being operated, the valve opening of the thermostat valve 15 on the cooling water passage 13 side is increased. The amount of cooling water passing through the radiator 11 is relatively increased. Based on the operation of the thermostat valve 15, the cooling water temperature of the engine 2 is appropriately maintained, and heat is appropriately supplied (recovered) to the Rankine cycle 31.
- the Rankine cycle 31 is not a simple Rankine cycle, but is configured as a part of the integrated cycle 30 integrated with the refrigeration cycle 51.
- the basic Rankine cycle 31 will be described first, and then the refrigeration cycle will be referred to.
- Rankine cycle 31 is a system that recovers waste heat of engine 2 to a refrigerant via cooling water of engine 2 and regenerates the recovered waste heat as power.
- the Rankine cycle 31 includes a refrigerant pump 32, a heat exchanger 36 as a superheater, an expander 37, and a condenser (condenser) 38, and each component is connected by refrigerant passages 41 to 44 through which a refrigerant (R134a and the like) circulates.
- R134a and the like refrigerant
- the shaft of the refrigerant pump 32 is connected to the output shaft of the expander 37 on the same shaft, and the refrigerant pump 32 is driven by the output (power) generated by the expander 37 and the generated power is used as the output shaft of the engine 2 ( (Refer to FIG. 2A).
- the shaft of the refrigerant pump 32 and the output shaft of the expander 37 are arranged in parallel with the output shaft of the engine 2, and a belt 34 is hung between the pump pulley 33 provided at the tip of the shaft of the refrigerant pump 32 and the crank pulley 2a. Is turning (see FIG. 1).
- the refrigerant pump 32 of this embodiment employs a gear type pump, and the expander 37 employs a scroll type expander (see FIGS. 2B and 2C).
- the expander 37 is provided with a rotation speed sensor 37 a that detects an expander rotation speed that is the rotation speed of the expander 37.
- An electromagnetic clutch (hereinafter referred to as “expander clutch”) 35 is provided between the pump pulley 33 and the refrigerant pump 32 so that the refrigerant pump 32 and the expander 37 can be connected to and disconnected from the engine 2 (FIG. 2A). reference).
- the expander clutch 35 When the output generated by the expander 37 exceeds the driving force of the refrigerant pump 32 and the friction of the rotating body (when the predicted expander torque is positive), the expander clutch 35 is connected to generate the expander 37.
- the output can assist the rotation of the engine output shaft.
- fuel efficiency can be improved by assisting rotation of an engine output shaft using energy obtained by waste heat recovery.
- the energy for driving the refrigerant pump 32 that circulates the refrigerant can also be covered by the recovered waste heat.
- the expander clutch 35 may be provided anywhere in the middle of the power transmission path from the engine 2 to the refrigerant pump 32 and the expander 37.
- the refrigerant from the refrigerant pump 32 is supplied to the heat exchanger 36 through the refrigerant passage 41.
- the heat exchanger 36 is a heat exchanger that exchanges heat between the cooling water of the engine 2 and the refrigerant to vaporize and superheat the refrigerant.
- the refrigerant from the heat exchanger 36 is supplied to the expander 37 through the refrigerant passage 42.
- the expander 37 is a steam turbine that converts heat into rotational energy by expanding the vaporized and superheated refrigerant.
- the power recovered by the expander 37 drives the refrigerant pump 32 and is transmitted to the engine 2 via the belt transmission mechanism to assist the rotation of the engine 2.
- the refrigerant from the expander 37 is supplied to the condenser 38 via the refrigerant passage 43.
- the condenser 38 is a heat exchanger that exchanges heat between the outside air and the refrigerant to cool and liquefy the refrigerant.
- the condenser 38 is arranged in parallel with the radiator 11 and is cooled by the radiator fan 12.
- the refrigerant liquefied by the condenser 38 is returned to the refrigerant pump 32 through the refrigerant passage 44.
- the refrigerant returned to the refrigerant pump 32 is sent again to the heat exchanger 36 by the refrigerant pump 32 and circulates through each component of the Rankine cycle 31.
- the refrigerant passage 44 extends upward from the inlet of the refrigerant pump 32 as shown in FIG.
- the refrigeration cycle 51 Since the refrigerating cycle 51 shares the refrigerant circulating through the Rankine cycle 31, it is integrated with the Rankine cycle 31, and the configuration of the refrigerating cycle 51 itself is simplified.
- the refrigeration cycle 51 includes a compressor (compressor) 52, a condenser 38, and an evaporator (evaporator) 55.
- the compressor 52 is a fluid machine that compresses the refrigerant of the refrigeration cycle 51 to a high temperature and a high pressure, and is driven by the engine 2.
- the compressor pulley 53 is fixed to the drive shaft of the compressor 52, and the belt 34 is wound around the compressor pulley 53 and the crank pulley 2a.
- the driving force of the engine 2 is transmitted to the compressor pulley 53 via the belt 34, and the compressor 52 is driven.
- An electromagnetic clutch (hereinafter referred to as a “compressor clutch”) 54 is provided between the compressor pulley 53 and the compressor 52 so that the compressor 52 and the compressor pulley 53 can be connected and disconnected.
- the refrigerant from the compressor 52 joins the refrigerant passage 43 via the refrigerant passage 56 and is then supplied to the condenser 38.
- the condenser 38 is a heat exchanger that condenses and liquefies the refrigerant by heat exchange with the outside air.
- the liquid refrigerant from the condenser 38 is supplied to an evaporator (evaporator) 55 through a refrigerant passage 57 branched from the refrigerant passage 44.
- the evaporator 55 is disposed in the case of the air conditioner unit in the same manner as a heater core (not shown).
- the evaporator 55 is a heat exchanger that evaporates the liquid refrigerant from the condenser 38 and cools the conditioned air from the blower fan by the latent heat of evaporation at that time.
- the refrigerant evaporated by the evaporator 55 is returned to the compressor 52 through the refrigerant passage 58.
- the mixing ratio of the conditioned air cooled by the evaporator 55 and the conditioned air heated by the heater core is adjusted to the temperature set by the occupant according to the opening of the air mix door.
- the evaporator 55, a part of the refrigerant passage 44 that connects the condenser 38 and the evaporator 55, and the refrigerant passage 57 are arranged at a position higher than the inlet of the refrigerant pump 32.
- the refrigerant passage 44 branches at the refrigeration cycle branch point 45 and is connected to the refrigerant passage 57.
- various valves are appropriately provided in the circuit in order to control the refrigerant flowing in the cycle.
- the refrigerant passage 44 that connects the pump upstream valve 61, the heat exchanger 36, and the expander 37 to the refrigerant passage 44 that connects the refrigeration cycle branch point 45 and the refrigerant pump 32. 42 is provided with an expander upstream valve 62.
- the refrigerant passage 41 that connects the refrigerant pump 32 and the heat exchanger 36 is provided with a check valve 63 that prevents the refrigerant from flowing backward from the heat exchanger 36 to the refrigerant pump 32.
- the refrigerant passage 43 that connects the expander 37 and the refrigeration cycle junction 46 is also provided with a check valve 64 that prevents the refrigerant from flowing back from the refrigeration cycle junction 46 to the expander 37.
- a check valve 64 that prevents the refrigerant from flowing back from the refrigeration cycle junction 46 to the expander 37.
- an expander bypass passage 65 that bypasses the expander 37 from the upstream of the expander upstream valve 62 and merges upstream of the check valve 64 is provided, and the expander bypass valve 66 is provided in the expander bypass passage 65.
- a pressure regulating valve 68 is provided in the passage 67 that bypasses the expander bypass valve 66.
- an air conditioner circuit valve 69 is provided in the refrigerant passage 57 that connects the refrigeration cycle branch point 45 and the evaporator 55.
- the above four valves 61, 62, 66, 69 are all electromagnetic on-off valves.
- the engine controller includes an expander upstream pressure signal detected by the pressure sensor 72, a condenser outlet refrigerant pressure Pd signal detected by the pressure sensor 73, an expander rotation speed detection signal detected by the rotation speed sensor 37a, and the like. 71 is input.
- the engine controller 71 controls the compressor 52 of the refrigeration cycle 51 and the radiator fan 12 based on each of these input signals according to predetermined operating conditions, and the four electromagnetic on-off valves 61, 62, 66, The opening and closing of 69 is controlled.
- the engine controller 71 predicts the expander torque (regenerative power) based on the expander upstream pressure detected by the pressure sensor 72 and the expander rotation speed detected by the rotation speed sensor 37a, and the predicted expander torque. Is positive (when the rotation of the engine output shaft can be assisted), the expander clutch 35 is engaged, and when the predicted expander torque is zero or negative, the expander clutch 35 is released. Based on the sensor detection pressure and expander rotational speed, the expander torque can be predicted with higher accuracy than when the expander torque (regenerative power) is predicted from the exhaust temperature. Accordingly, the expander clutch 35 can be appropriately engaged and disengaged (refer to JP2010-190185A for details).
- the four on-off valves 61, 62, 66 and 69 and the two check valves 63 and 64 are refrigerant valves. The functions of these refrigerant valves are shown again in FIG.
- the pump upstream valve 61 is provided at the inlet of the refrigerant pump 32 (see FIG. 8).
- the pump upstream valve 61 prevents the refrigerant (including the lubricating component) from being biased to the Rankine cycle 31 by closing the pump upstream valve 61 under a predetermined condition that makes the refrigerant easily biased to the Rankine cycle 31 circuit as compared to the refrigeration cycle 51 circuit. Therefore, as will be described later, the circuit of the Rankine cycle 31 is closed in cooperation with the check valve 64 downstream of the expander 37.
- the expander upstream valve 62 can block the refrigerant passage 42 when the refrigerant pressure from the heat exchanger 36 is relatively low, and can hold the refrigerant until the refrigerant from the heat exchanger 36 has a high pressure. Thereby, even when the expander torque cannot be obtained sufficiently, the heating of the refrigerant is promoted, and for example, the time until Rankine cycle 31 is restarted (regeneration can actually be performed) can be shortened.
- the expander bypass valve 66 is opened so as to operate the refrigerant pump 32 after bypassing the expander 37 when the amount of refrigerant existing on the Rankine cycle 31 side is insufficient at the time of starting the Rankine cycle 31 or the like. In order to shorten the startup time of the Rankine cycle 31.
- the refrigerant temperature at the outlet of the condenser 38 or the inlet of the refrigerant pump 32 has a predetermined temperature difference (subcool degree SC) from the boiling point considering the pressure at that portion. ) If the state lowered as described above is realized, the Rankine cycle 31 is ready to supply a sufficient liquid refrigerant.
- the check valve 63 upstream of the heat exchanger 36 is for maintaining the refrigerant supplied to the expander 37 at a high pressure in cooperation with the expander bypass valve 66, the pressure adjusting valve 68, and the expander upstream valve 62. is there.
- the Rankine cycle operation is stopped, the circuit is closed over the front and rear sections of the heat exchanger, the refrigerant pressure during the stop is increased, and the high-pressure refrigerant is used. Allow the Rankine cycle to restart quickly.
- the pressure regulating valve 68 functions as a relief valve that opens when the pressure of the refrigerant supplied to the expander 37 becomes too high and releases the refrigerant that has become too high.
- the check valve 64 downstream of the expander 37 is for preventing the bias of the refrigerant to the Rankine cycle 31 in cooperation with the pump upstream valve 61 described above. If the engine 2 is not warmed immediately after the start of the operation of the hybrid vehicle 1, the Rankine cycle 31 becomes cooler than the refrigeration cycle 51, and the refrigerant may be biased toward the Rankine cycle 31 side. Although the probability of being biased toward the Rankine cycle 31 is not so high, for example, immediately after the start of vehicle operation in summer, the cooling capacity is most demanded in the situation where it is desired to cool the interior quickly, so the slight uneven distribution of refrigerant is also eliminated. Therefore, there is a demand for securing the refrigerant for the refrigeration cycle 51. Therefore, a check valve 64 is provided to prevent uneven distribution of refrigerant to the Rankine cycle 31 side.
- the compressor 52 does not have a structure in which the refrigerant can freely pass when driving is stopped, and can prevent the refrigerant from being biased to the refrigeration cycle 51 in cooperation with the air conditioner circuit valve 69. This will be described.
- the refrigerant may move from the relatively high temperature Rankine cycle 31 side to the refrigeration cycle 51 side during steady operation, and the refrigerant circulating through the Rankine cycle 31 may be insufficient.
- the temperature of the evaporator 55 is low immediately after the cooling is stopped, and the refrigerant tends to accumulate in the evaporator 55 having a relatively large volume and a low temperature.
- the movement of the refrigerant from the condenser 38 to the evaporator 55 is interrupted by stopping the driving of the compressor 52, and the air conditioner circuit valve 69 is closed to prevent the refrigerant from being biased to the refrigeration cycle 51.
- FIG. 5 is a schematic perspective view of the engine 2 showing a package of the entire engine. 5 is characterized in that the heat exchanger 36 is arranged vertically above the exhaust manifold 4. By placing the heat exchanger 36 in the space vertically above the exhaust manifold 4, the mountability of the Rankine cycle 31 to the engine 2 is improved.
- the engine 2 is provided with a tensioner pulley 8.
- FIGS. 7A and 7B are operation region diagrams of Rankine cycle 31.
- FIG. 7A shows the Rankine cycle operating range when the horizontal axis is the outside air temperature and the vertical axis is the engine water temperature (cooling water temperature).
- FIG. 7B is the engine rotational speed and the vertical axis is the engine torque (engine load). The operating range of Rankine cycle 31 is shown.
- the Rankine cycle 31 is operated when a predetermined condition is satisfied, and the Rankine cycle 31 is operated when both of these conditions are satisfied.
- FIG. 7A the operation of the Rankine cycle 31 is stopped in a region on the low water temperature side where priority is given to warm-up of the engine 2 and a region on the high outside air temperature side where the load on the compressor 52 increases.
- the Rankine cycle 31 is not operated, so that the coolant temperature is quickly raised.
- the Rankine cycle 31 is stopped at a high outside air temperature where high cooling capacity is required, and sufficient refrigerant and cooling capacity of the condenser 38 are provided to the refrigeration cycle 51.
- FIG. 7A the operation of the Rankine cycle 31 is stopped in a region on the low water temperature side where priority is given to warm-up of the engine 2 and a region on the high outside air temperature side where the load on the compressor 52 increases.
- the Rankine cycle 31 is not operated, so that the coolant temperature is quickly raised.
- the Rankine cycle 31 is stopped
- the operation of the Rankine cycle 31 is stopped in the EV traveling region and the region on the high rotational speed side where the friction of the expander 37 increases. Since it is difficult to make the expander 37 have a high-efficiency structure with little friction at all rotation speeds, in the case of FIG. 7, the expansion is performed so that the friction is small and the efficiency is high in the engine rotation speed range where the operation frequency is high.
- the machine is configured (the dimensions of each part of the expander are set).
- FIG. 8 is a timing chart showing a model when the hybrid vehicle 1 is accelerated while assisting the rotation of the engine output shaft by the expander torque.
- the state in which the operating state of the expander 37 changes is shown on the expander torque map.
- the expander torque is the highest in the portion where the expander rotational speed is low and the expander upstream pressure is high (upper left), the expander rotational speed is high, and the expander upstream pressure is low.
- the expander torque tends to be smaller as it goes (lower right).
- the shaded area represents a region where the expander torque becomes negative on the premise of driving the refrigerant pump and becomes a load on the engine.
- the rotation speed of the expander 37 that is, the rotation speed of the pump 32 increases in proportion to the engine rotation speed, but the increase in the exhaust gas temperature or the coolant temperature has a delay with respect to the increase in the engine rotation speed. Therefore, the ratio of the recoverable heat amount to the refrigerant amount increased by the increase in the rotational speed of the pump 32 is reduced.
- the expander 37 and the refrigerant pump 32 are rotated by the driving force of the engine, and rather become an engine load. Therefore, when the expander torque becomes a predetermined value or less, the expander clutch 35 To avoid the drag phenomenon of the expander 37 (turned by the engine to be an engine load instead).
- the expander upstream valve 62 is closed at the timing t2 prior to t3 when the expander clutch 35 is disconnected, and the expander upstream pressure is almost the same as the expander downstream pressure at the timing t3. .
- the expander upstream valve 62 is closed to sufficiently reduce the pressure of the refrigerant upstream of the expander (the refrigerant flowing into the expander), and the expansion when the expander clutch 35 is disconnected. The machine 37 is prevented from over-rotating.
- the expander upstream pressure rises again due to the increase in the heat radiation amount of the engine 2, and at the timing t4, the expander upstream valve 62 is switched from the closed state to the open state, so that the refrigerant is supplied to the expander 37. Resumed. Further, the expander clutch 35 is connected again at t4. By reconnecting the expander clutch 35, rotation assist of the engine output shaft by the expander torque is resumed.
- FIG. 9 is a model showing how the Rankine cycle restarts in a manner different from that in FIG. 8 (control of t4) from the stoppage of the Rankine cycle in a state where the expander upstream valve 62 is closed and the expander clutch 35 is disconnected. It is the timing chart shown.
- the temperature of the coolant flowing into the heat exchanger 36 increases due to the increase in the amount of released heat, and the temperature of the refrigerant in the heat exchanger 36 increases.
- the expander upstream valve 62 is closed, the refrigerant pressure upstream of the expander upstream valve 62, that is, the expander upstream pressure increases as the refrigerant temperature rises by the heat exchanger 36 (t11 to t12).
- the expander 37 can be operated (driven) at the timing t12 when the differential pressure between the expander upstream pressure and the expander downstream pressure becomes greater than or equal to a predetermined pressure, and the expander upstream valve 62 is moved from the closed state. Switch to the open state. By switching the expander upstream valve 62 to the open state, a predetermined pressure of refrigerant is supplied to the expander 37, and the expander rotational speed quickly increases from zero.
- the expander clutch 35 is switched from disconnection to connection. If the expander clutch 35 is connected before the expander 37 sufficiently increases the rotational speed, the expander 37 becomes an engine load and torque shock may occur. On the other hand, when the expander clutch 35 is connected at t13 at which the rotational speed difference from the engine output shaft disappears, the expander 37 becomes an engine load, and the torque shock associated with the engagement of the expander clutch 35. Can also be prevented.
- FIG. 10 is an explanatory diagram showing a detection operation for detecting whether the friction of the expander 37 is increasing.
- the engine controller 71 releases the expander clutch 35 and opens the expander bypass valve 66 to freely rotate the expander 37 in a state where the Rankine cycle 31 is in the Rankine cycle operation region. By detecting the rotation speed. An increase in friction of the expander 37 is detected.
- the expander clutch 35 is connected, and the rotation of the expander 37 assists the rotation of the engine output shaft.
- the engine controller 71 disconnects the expander clutch 35 and opens the expander bypass valve 66 to bypass the refrigerant flow to the expander 37.
- the expander 37 enters a no-load state, and the pressure of the refrigerant supplied to the expander 37 decreases, so that the expander 37 freely rotates due to inertia.
- the expander clutch 35 When the expander clutch 35 is disconnected in the Rankine cycle operation region, if the expander upstream pressure is equal to or greater than a predetermined value or the difference between the expander upstream pressure and the expander downstream pressure is equal to or greater than a predetermined difference, the rotation of the expander 37 In this state, the engine rotation is assisted, and when this is immediately put into a no-load state, the residual pressure of the refrigerant is received, and the rotational speed of the expander 37 is temporarily increased by free rotation for the assist torque.
- the engine controller 71 detects an increase in the expander rotational speed when the expander 37 is unloaded, and determines whether or not an increase in the friction of the expander 37 has occurred.
- the engine controller 71 determines that the increase in the expander rotational speed is higher than a predetermined value, and determines that it is normal. If the increase in the expander rotational speed is less than the predetermined value, the friction of the expander 37 increases. It is determined that As described above, when the increase in the friction of the expander 37 is detected based on the increase in the rotation speed of the expander 37 when the expander clutch 35 is disconnected, high diagnostic accuracy can be obtained for the following reason.
- the refrigerant pump 32 is a pump driven by the power regenerated by the expander 37, when the rotation speed of the expander is increased, it is difficult to cause over-rotation, and an increase in friction is detected based on the increase in rotation speed. It is the structure which is easy to do.
- the engine controller 71 can notify the driver of a warning and prompt an inspection at the service center. For example, when the predetermined value of the increase in the rotation speed of the expander is reduced to 90% of the increase in the design value, it is determined that the friction is increased.
- the expansion speed of the expander 37 is set in advance.
- the engine controller 71 detects in advance the refrigerant pressure in a range where the expander rotation speed does not exceed the permissible rotation speed when the expander clutch 35 is disconnected and the expander rotation speed increases, and detects an increase in friction. Sometimes, it is desirable to set the refrigerant pressure of the expander 37 to a pressure that has been previously grasped.
- an upper limit pressure within a range where the expander 37 does not reach the allowable rotational speed is obtained in advance by experiments or the like, and the engine controller 71 detects the detected expander upstream pressure.
- the expander clutch 35 may be disconnected when the pressure is lower than or equal to the upper limit pressure (when the pressure falls below the upper limit pressure).
- an upper limit pressure difference between the upstream pressure and the downstream pressure of the expander within a range where the expander 37 does not reach the permissible rotational speed is obtained in advance by experiments or the like.
- the controller 71 may disconnect the expander clutch 35 when the detected difference between the expander upstream pressure and the expander downstream pressure is equal to or less than the upper limit pressure difference (when the difference is decreased to the upper limit pressure difference or less).
- FIG. 11 is an explanatory diagram showing another example of the detection operation for detecting whether the friction of the expander 37 is increasing.
- the engine controller 71 connects the expander clutch 35 and assists the rotation of the engine output shaft by the rotation of the expander 37 in the Rankine cycle operation region.
- the engine controller 71 disconnects the expander clutch 35.
- the expander 37 is in a no-load state, and the expander rotation speed is increased by the refrigerant in the Rankine cycle 31.
- the engine controller 71 detects the increase in the rotational speed of the expander 37 at this time, and determines whether or not the friction of the expander 37 has increased.
- the engine controller 71 detects the expander rotation speed and determines whether or not the expander rotation speed is equal to or higher than a predetermined rotation speed with a margin with respect to a preset allowable rotation speed. When the rotational speed exceeds a predetermined rotational speed, the engine controller 71 opens the expander bypass valve 66 to stop the supply of refrigerant to the expander 37 in order to prevent the expander 37 from reaching the allowable rotational speed. To do. Since the expander 37 is not given driving force by the refrigerant after the expander bypass valve 66 is opened, the rotation of the expander 37 gradually decreases due to its own friction.
- the rotation of the expander is compared with the case where the disconnection of the expander clutch 35 and the opening of the expander bypass valve 66 are performed simultaneously. Since the increase in speed increases, it is easy to determine the increase in the expander rotation speed, and it is easy to determine the increase in the friction of the expander 37.
- the engine controller 71 controls the expander clutch 35 to be disconnected when the expander torque becomes equal to or less than a predetermined value so as to avoid the drag phenomenon of the expander 37.
- the expander bypass valve 66 can be opened at the timing t2 before t3 when the expander clutch 35 is disconnected.
- the expander bypass valve 66 is opened before the expander clutch 35 is disconnected, thereby sufficiently reducing the refrigerant pressure difference between the expander upstream and the expander downstream. It is possible to prevent the expander 37 from over-rotating when the expander clutch 35 is disconnected.
- the embodiment of the present invention is configured to detect an increase in the expander rotational speed when the expander clutch 35 is disconnected and the expander 37 is unloaded in the Rankine cycle operation region.
- the expander bypass valve 66 is opened to drive the expander 37 so that the expander rotation speed of the expander 37 does not exceed the allowable rotation speed of the expander 37. Reduce the pressure of the refrigerant. As a result, no driving force is applied to the expander 37 in a no-load state, and the overexpansion of the expander 37 is prevented to prevent a failure.
- the expander clutch 35 when the expander clutch 35 is disengaged, the expander upstream pressure of the expander 37 or the difference between the expander upstream pressure and the expander downstream pressure is detected, and the expander upstream pressure is equal to or lower than a predetermined pressure, or the pressure difference is Since the expander clutch 35 is disconnected when the pressure difference is equal to or less than the predetermined pressure difference, an excessive driving force is not applied when the expander 37 is in a no-load state, and over-rotation of the expander 37 is prevented to prevent a failure. To prevent.
- the expander bypass valve 66 is opened in advance.
- the pressure of the refrigerant that drives the expander is prevented to prevent failure.
- the present invention is also applicable to a vehicle equipped with only the engine 2.
- the engine 2 may be a gasoline engine or a diesel engine.
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Abstract
Description
Claims (8)
- エンジン(2)の廃熱を冷媒に回収する熱交換器(36)と、前記熱交換器(36)を出た冷媒を用いて動力を発生させる膨張機(37)と、前記膨張機(37)を出た冷媒を凝縮させる凝縮器(38)と、前記凝縮器(38)を出た冷媒を前記熱交換器(36)に供給する冷媒ポンプ(32)と、を備えるランキンサイクル(31)と、
前記膨張機(37)により回生された動力を前記エンジン(2)に伝達する動力伝達機構(34)と、
を備える廃熱利用装置において、
前記動力伝達機構(34)は、前記膨張機から前記エンジンへの動力の伝達を断続する断続手段(35)を備え、
前記膨張機(37)は、前記膨張機(37)の回転速度を検出する回転速度検出手段(73a)を備え、
前記断続手段(35)を切断したときに、前記回転速度検出手段(37a)により検出された前記膨張機(37)の回転速度の上昇に基づいて、前記膨張機(37)のフリクションの増大を検出するフリクション増大検出手段(71)を備える廃熱利用装置。 - 請求項1に記載の廃熱利用装置であって、
前記ランキンサイクル(31)は、前記膨張機(37)に導入する冷媒をバイパスさせるバイパス通路(65)と、前記パイパス通路(65)への冷媒の導通を断続するバイパス弁(66)と、を備え、
前記フリクション増大検出手段(71)は、前記断続手段(35)を切断したとき、前記バイパス弁(66)を制御して前記バイパス通路(65)を導通させる廃熱利用装置。 - 請求項2に記載の廃熱利用装置であって、
前記フリクション増大検出手段(71)は、前記断続手段(35)を切断したのと同時に、前記バイパス弁(65)を制御して前記バイパス通路(66)を導通させる廃熱利用装置。 - 請求項1に記載の廃熱利用装置であって、
前記ランキンサイクル(31)は、前記膨張機(37)に導入する冷媒をバイパスさせるバイパス通路(65)と、前記パイパス通路(65)への冷媒の導通を断続するバイパス弁(66)と、を備え、
前記フリクション増大検出手段(71)は、前記断続手段(35)を切断したとき、前記膨張機(37)の回転速度が前記膨張機(37)の許容回転速度以下となるように、前記バイパス弁(66)を制御して前記バイパス通路(65)を導通させる廃熱利用装置。 - 請求項1から4のいずれかに記載の廃熱利用装置であって、
前記膨張機(37)の上流側の冷媒圧力を検出する圧力検出手段(72)を備え、
前記フリクション増大検出手段(71)は、前記圧力検出手段(72)によって検出された前記膨張機(37)の上流側の冷媒圧力が所定圧力以下である場合に、前記断続手段(35)を切断する廃熱利用装置。 - 請求項1から4のいずれかに記載の廃熱利用装置であって、
前記膨張機(37)の上流側の冷媒圧力と下流側の冷媒圧力との差を検出する圧力差検出手段(72、73)を備え、
前記フリクション増大検出手段(71)は、前記圧力差検出手段(72、73)によって検出された前記膨張機(37)の上流側の冷媒圧力と下流側の冷媒圧力との差が所定圧力差以下である場合に、前記断続手段(35)を切断する廃熱利用装置。 - 請求項2から4のいずれかに記載の廃熱利用装置であって、
前記膨張機(37)のフリクション増大の検出を行なわないときは、前記膨張機(37)が動力を回生しているときに、前記バイパス通路(65)を導通させた後に、前記断続手段(35)を切断する廃熱利用装置。 - 請求項1から7のいずれかに記載の廃熱利用装置であって、
前記冷媒ポンプ(32)は、前記膨張機(37)により回生された動力で駆動されるポンプである廃熱利用装置。
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- 2012-08-14 CN CN201280048004.6A patent/CN103987923B/zh active Active
- 2012-08-14 DE DE112012004058.9T patent/DE112012004058B4/de active Active
- 2012-08-14 US US14/348,395 patent/US9441503B2/en active Active
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JP2015218636A (ja) * | 2014-05-15 | 2015-12-07 | 日産自動車株式会社 | エンジンの廃熱利用装置 |
CN106460725A (zh) * | 2014-05-15 | 2017-02-22 | 三电控股株式会社 | 发动机的废热利用装置 |
US20170082061A1 (en) * | 2014-05-15 | 2017-03-23 | Sanden Holdings Corporation | Engine Waste-Heat Utilization Device |
US9988945B2 (en) | 2014-05-15 | 2018-06-05 | Sanden Holdings Corporation | Apparatus for utilizing heat wasted from engine |
Also Published As
Publication number | Publication date |
---|---|
CN103987923A (zh) | 2014-08-13 |
US20150047351A1 (en) | 2015-02-19 |
DE112012004058B4 (de) | 2022-05-12 |
CN103987923B (zh) | 2015-11-25 |
US9441503B2 (en) | 2016-09-13 |
DE112012004058T5 (de) | 2014-07-10 |
JP5804879B2 (ja) | 2015-11-04 |
JP2013076370A (ja) | 2013-04-25 |
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