JP2014231740A - Waste heat utilization device - Google Patents

Waste heat utilization device Download PDF

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Publication number
JP2014231740A
JP2014231740A JP2011209817A JP2011209817A JP2014231740A JP 2014231740 A JP2014231740 A JP 2014231740A JP 2011209817 A JP2011209817 A JP 2011209817A JP 2011209817 A JP2011209817 A JP 2011209817A JP 2014231740 A JP2014231740 A JP 2014231740A
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JP
Japan
Prior art keywords
working fluid
expander
pressurized air
flow rate
waste heat
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Application number
JP2011209817A
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Japanese (ja)
Inventor
英文 森
Hidefumi Mori
英文 森
井口 雅夫
Masao Iguchi
雅夫 井口
榎島 史修
Fuminobu Enoshima
史修 榎島
文彦 石黒
Fumihiko Ishiguro
文彦 石黒
Original Assignee
株式会社豊田自動織機
Toyota Industries Corp
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Priority to JP2011209817A priority Critical patent/JP2014231740A/en
Publication of JP2014231740A publication Critical patent/JP2014231740A/en
Withdrawn legal-status Critical Current

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01KSTEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/12Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engines being mechanically coupled
    • F01K23/14Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engines being mechanically coupled including at least one combustion engine
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01KSTEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02Plants 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
    • F01K23/06Plants 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
    • F01K23/065Plants 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01KSTEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02Plants 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
    • F01K23/06Plants 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
    • F01K23/10Plants 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02GHOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G5/00Profiting from waste heat of combustion engines, not otherwise provided for
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01NGAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N5/00Exhaust or silencing apparatus combined or associated with devices profiting from exhaust energy
    • F01N5/02Exhaust or silencing apparatus combined or associated with devices profiting from exhaust energy the devices using heat
    • YGENERAL 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
    • Y02TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02TCLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00Road transport of goods or passengers
    • Y02T10/10Internal combustion engine [ICE] based vehicles
    • Y02T10/16Energy recuperation from low temperature heat sources of the ICE to produce additional power
    • Y02T10/166Waste heat recovering cycles or thermoelectric systems

Abstract

PROBLEM TO BE SOLVED: To provide a waste heat utilization device ensuring low cost and high durability while achieving improved output power of an internal combustion engine.SOLUTION: A waste heat utilization device according to an embodiment comprises: a Rankine cycle 3 used for a drive system 1; a bypass passage 29; a flow regulation valve 31; a pressure sensor 35; and a controller 11. The drive system 1 includes an engine 5, and a turbocharger 7 supplying pressurized air to the engine 5. The Rankine cycle 3 includes an electric pump P1; a pressurized air boiler 19; an expansion machine 21; a condenser 23; and pipes 25 to 28. The electric pump P1 increases a discharge amount of a working fluid by excess of an output request from the drive system 1 over a predetermined value.The controller 11 regulates a flow volume of a moving fluid flowing into the expansion machine 21 by controlling a flow regulation valve 31 based on comparison of a set evaporation pressure with a detected pressure α detected by the pressure sensor 35.

Description

  The present invention relates to a waste heat utilization apparatus.

  Patent Document 1 discloses a conventional waste heat utilization device. This waste heat utilization device is used in a drive system and includes a Rankine cycle for circulating a working fluid. The drive system has an engine as an internal combustion engine and a turbocharger as a supercharger that supplies pressurized air to the engine. The Rankine cycle has a pump, a cooling water boiler, a pressurized air boiler, an expander, a condenser, and piping. In the cooling water boiler, the cooling water for the engine and the working fluid exchange heat. In the pressurized air boiler, the pressurized air and the working fluid exchange heat. Moreover, piping circulates a working fluid in order of a pump, a cooling water boiler, a pressurized air boiler, an expander, and a condenser.

  In such a waste heat utilization apparatus, since the working fluid can be heated by the cooling water boiler and the pressurized air boiler, it becomes possible to increase the pressure energy generated by the expansion and decompression of the working fluid. . For this reason, in this waste heat utilization apparatus, it is possible to increase the amount of energy that can be recovered in the Rankine cycle.

JP 2008-8224 A

  By the way, in a drive system having a supercharger such as a turbocharger, it is preferable to sufficiently cool the pressurized air before supplying it to an internal combustion engine such as an engine. This is because the density of the pressurized air is increased by cooling, and more pressurized air can be supplied to the engine. As a result, the output of the internal combustion engine can be further improved. .

  In this regard, in the conventional waste heat utilization apparatus, the pressurized air can be cooled in the pressurized air boiler. For this reason, when the output demand of the internal combustion engine is large, for example, by changing the discharge amount of the working fluid by the pump and increasing the flow rate of the working fluid circulating in the piping, a large amount of working fluid flows into the pressurized air boiler It is possible to make it. As a result, heat exchange between the pressurized air and the working fluid is performed more suitably, the pressurized air can be sufficiently cooled, and the pressurized air according to the output request can be supplied to the internal combustion engine. It becomes.

  However, when the flow rate of the working fluid is increased in this way, the flow rate of the working fluid flowing into the expander via the pressurized air boiler increases, and the evaporation pressure (the working fluid from the downstream of the pump to the upstream of the expander is increased). Pressure) will increase. On the other hand, in the Rankine cycle, an evaporating pressure that can be allowed by components such as an expander is determined as a preset evaporating pressure in the design stage. For this reason, since the flow rate of the working fluid flowing into the expander increases as described above, a situation may occur in which the evaporation pressure exceeds the set evaporation pressure. In this case, there is a concern that the durability of the expander and the like, and in turn, the durability of the waste heat utilization device may be lowered. In particular, when the expander and the internal combustion engine are configured to be able to transmit power, the flow rate of the working fluid that can flow into the expander depends on the rotational speed of the internal combustion engine. For this reason, when the rotational speed of the internal combustion engine is small, the evaporation pressure can easily exceed the set evaporation pressure, and the durability of the expander is more significantly reduced.

  For such a problem, for example, it is conceivable to employ an expander having a large upper limit pressure. However, in this case, the manufacturing cost of the expander and the like increases, and the waste heat utilization device increases.

  The present invention has been made in view of the above-described conventional situation, and it is an issue to be solved to provide a low-cost and highly durable waste heat utilization device while realizing an improvement in the output of an internal combustion engine. Yes.

The waste heat utilization apparatus of the present invention is used in a drive system having an internal combustion engine and a supercharger that supplies pressurized air to the internal combustion engine, and includes a Rankine cycle that circulates a working fluid.
The Rankine cycle includes a pump, a pressurized air boiler that exchanges heat between the pressurized air and the working fluid, an expander, a condenser, the pump, the pressurized air boiler, and the expander. And a waste heat utilization device having a pipe for circulating the working fluid in the order of a condenser,
The pump can increase the discharge amount of the working fluid when the output request by the drive system exceeds a predetermined value,
Evaporation pressure suppression means is provided for suppressing an increase in the evaporation pressure of the Rankine cycle accompanying an increase in the discharge amount when the discharge amount of the working fluid by the pump increases. 1).

  The waste heat utilization apparatus of the present invention includes a Rankine cycle. This Rankine cycle is used for a drive system, and circulates a working fluid. The drive system includes an internal combustion engine and a supercharger that supplies pressurized air to the internal combustion engine. The Rankine cycle has a pump, a pressurized air boiler, an expander, a condenser, and piping. The pump can change the discharge amount of the working fluid in response to an output request from the drive system. In the pressurized air boiler, the pressurized air and the working fluid exchange heat. The piping circulates the working fluid in the order of a pump, a pressurized air boiler, an expander, and a condenser.

  According to the knowledge of the inventors, the pressurized air compressed by the supercharger has a temperature of about 150 ° C. For this reason, in this waste heat utilization apparatus, it becomes possible to fully heat a working fluid with a pressurized air boiler. For this reason, in this waste heat utilization apparatus, the pressure energy when the working fluid is expanded and depressurized by the expander can be increased, and the amount of energy that can be recovered in the Rankine cycle can be increased.

  Moreover, in this waste heat utilization apparatus, it is possible to cool pressurized air by heat exchange in a pressurized air boiler. For this reason, it becomes possible to supply much pressurized air to the internal combustion engine. Furthermore, in this waste heat utilization apparatus, when the output request by the drive system exceeds a predetermined value, the pump can increase the discharge amount of the working fluid. It is possible to increase the flow rate of the working fluid that circulates through a large amount of working fluid to flow into the pressurized air boiler. For this reason, in this waste heat utilization apparatus, it becomes possible to fully supply pressurized air to an internal combustion engine according to the output demand by a drive system.

  Furthermore, this waste heat utilization apparatus is provided with an evaporation pressure suppressing means for suppressing an increase in the evaporation pressure of the Rankine cycle accompanying an increase in the discharge amount when the discharge amount of the working fluid by the pump increases.

  For this reason, in this waste heat utilization apparatus, the discharge amount of the pump becomes large, the flow rate of the working fluid flowing into the pressurized air boiler increases, and the evaporation pressure of the Rankine cycle may increase beyond the set evaporation pressure as it is. Even when there is, it is possible to suppress the evaporation pressure of the Rankine cycle below the set evaporation pressure. Here, in the present invention, the evaporation pressure of the Rankine cycle refers to the pressure of the working fluid from the downstream of the pump to the upstream of the expander. For this reason, in this waste heat utilization apparatus, it is not necessary to provide components, such as an expander designed with the large upper limit pressure, in a Rankine cycle.

  Therefore, according to the waste heat utilization apparatus of the present invention, the durability can be increased at low cost while realizing the improvement of the output of the internal combustion engine.

  As the internal combustion engine, various types of engines can be employed in addition to a gasoline engine, a diesel engine, and the like. These engines may be hybrid engines combining motors. Furthermore, these engines may be air-cooled or water-cooled. On the other hand, a turbocharger, a supercharger, or the like can be employed as the supercharger. There may be a plurality of internal combustion engines and superchargers.

  Moreover, the waste heat utilization apparatus of this invention can be equipped with the pressure detection means which detects the evaporation pressure downstream of a pressurized air boiler as detection pressure. Then, it is preferable to compare the preset evaporation pressure and the detected pressure, and suppress the increase in the evaporation pressure by the evaporation pressure suppression means (claim 2).

  In this case, the flow rate of the working fluid flowing into the expander is more preferably suppressed while maintaining the evaporation pressure of the Rankine cycle within the set evaporation pressure. For this reason, in this waste heat utilization apparatus, the situation where an evaporating pressure exceeds a preset evaporating pressure is avoided suitably, and durability of an expander can be made high. Furthermore, in this case, since the pressure energy when the working fluid is expanded and depressurized by the expander can be increased as much as possible, the amount of energy that can be recovered in the Rankine cycle can be further increased.

  In the waste heat utilization apparatus of the present invention, the evaporating pressure suppression means is branched from the pipe downstream of the pressurized air boiler, bypasses the expander and joins the pipe, and the flow rate of the working fluid flowing into the expander And a flow rate adjusting valve capable of adjusting the flow rate of the working fluid flowing into the bypass passage.

  In this case, the flow rate adjustment valve can adjust the flow rate of the working fluid flowing into the expander and the flow rate of the working fluid flowing into the bypass passage among the working fluids that have passed through the pressurized air boiler. For this reason, the working fluid that has flowed out of the pressurized air boiler flows into the bypass passage and the expander, respectively. At this time, the working fluid flowing into the bypass passage bypasses the expander and reaches the condenser. For this reason, when there is a possibility that the evaporation pressure may increase beyond the set evaporation pressure due to an increase in the flow rate of the working fluid discharged from the pump, the evaporation pressure is reduced by allowing a part of the working fluid to flow into the bypass path. It is possible to suppress the rise of

  In the waste heat utilization apparatus of the present invention, the evaporating pressure suppressing means may be a flow rate ratio changing means for changing a ratio between a flow rate of the working fluid flowing into the expander and a flow rate of the working fluid discharged from the pump ( Claim 4). The flow rate ratio changing means may be a capacity control means capable of changing a suction capacity per unit rotation number of the expander (claim 5). Further, the flow rate ratio changing means may be a speed change means capable of changing the rotation speed of the expander. These also make it possible to suppress the evaporation pressure of the Rankine cycle below the set evaporation pressure.

  In the waste heat utilization apparatus of the present invention, it is preferable that the expander and the internal combustion engine are configured to be able to transmit power (claim 7). In this case, the expander can be operated by the power of the internal combustion engine, and the expander can be operated by the energy recovered in the Rankine cycle to regenerate power to the internal combustion engine.

  According to the waste heat utilization apparatus of the present invention, the durability can be increased at low cost while improving the output of the internal combustion engine.

It is a schematic structure figure which shows the waste heat utilization apparatus of an Example. It is a schematic structure figure which shows the state in operation regarding the waste heat utilization apparatus of an Example. FIG. 4 is a schematic structural diagram showing an operating state when the output request of the drive system exceeds a predetermined value, according to the waste heat utilization apparatus of the example.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments embodying the present invention will be described below with reference to the drawings.

(Example)
The waste heat utilization apparatus of the embodiment is mounted on a vehicle and is used in a drive system 1 of the vehicle as shown in FIG. The waste heat utilization apparatus includes a Rankine cycle 3, a bypass 29, a flow rate adjustment valve 31, a pressure sensor 35, and a control device 11. The bypass passage 29 and the flow rate adjusting valve 31 correspond to the evaporation pressure suppressing means. The pressure sensor 35 corresponds to a pressure detection unit.

  The drive system 1 has an engine 5 as an internal combustion engine, a turbocharger 7 as a supercharger, and a radiator (not shown). The engine 5 is a known water-cooled gasoline engine. A water jacket (not shown) through which cooling water can flow is formed inside the engine 5. The engine 5 is formed with an outlet and an inlet (both not shown) communicating with the water jacket. Further, the engine 5 is formed with an exhaust port 5a for exhausting exhaust gas and an intake port 5b for sucking in pressurized air described later.

  The turbocharger 7 uses public goods. The turbocharger 7 is operated by exhaust generated from the engine 5 and supplies the engine 5 with pressurized air obtained by pressurizing air outside the vehicle.

  The engine 5 and the turbocharger 7 are connected by pipes 9 to 11. In addition, a pressurized air boiler 19 described later is connected to the pipe 10 and the pipe 11. The pipe 9 is capable of circulating exhaust gas and is connected to the exhaust port 5 a of the engine 5 and the turbocharger 7. On the other hand, the piping 10 and the piping 11 are capable of circulating pressurized air. The pipe 10 is connected to the turbocharger 7 and the first inlet 19 a of the pressurized air boiler 19. The pipe 11 is connected to the first outlet 19 b of the pressurized air boiler 19 and the inlet 5 b of the engine 5.

  Further, the turbocharger 7 is connected to one end sides of the pipes 12 and 13. The other end side of the pipe 12 is connected to a muffler (not shown). The other end of the pipe 13 is open to an air intake of a vehicle (not shown). The pipe 12 communicates with the pipe 9 via the turbocharger 7. Similarly, the pipe 13 communicates with the pipe 10 via the turbocharger 7.

  The engine 5 is connected to a known pulley 17 via a crankshaft 15. The pulley 17 includes first and second pulley drums 17a and 17b, and a pulley belt 17c that connects the first pulley drum 17a and the second pulley drum 17b so that power can be transmitted. The crankshaft 15 is connected to the first pulley drum 17a, and the pulley drum 17a can be rotated by the power of the engine 5.

  The Rankine cycle 3 includes an electric pump P1, a pressurized air boiler 19, an expander 21, a condenser 23, and pipes 25 to 28. The Rankine cycle 3 is integrally assembled with a bypass passage 29 and a flow rate adjustment valve 31. An HFC 134a as a working fluid can be circulated through the pipes 25 to 28 and the bypass path 29.

  The pressurized air boiler 19 is formed with a first inlet 19a and a first outlet 19b, and a second inlet 19c and a second outlet 19d. Further, in the pressurized air boiler 19, a first passage 19e communicating with the first inflow port 19a and the first outflow port 19b at both ends, respectively, and a second inflow port 19c and a second outflow port 19d at both ends, respectively. A second passage 19f communicating with the second passage 19f is provided. The pressurized air boiler 19 cools the pressurized air and heats the working fluid by exchanging heat between the pressurized air in the first passage 19e and the working fluid in the second passage 19f.

  The expander 21 generates a rotational driving force by expanding the working fluid heated through the pressurized air boiler 19. In the expander 21 and the like, an allowable predetermined evaporation pressure is determined in advance as a preset evaporation pressure.

  The expander 21 is formed with an inlet 21a through which a working fluid flows and an outlet 21b through which the working fluid flows out. Further, one end side of a drive shaft 33 is connected to the expander 21. The other end side of the drive shaft 33 is connected to the second pulley drum 17b. The expander 21 and the engine 5 can transmit power by the crankshaft 15, the pulley 17, and the drive shaft 33. A one-way clutch (not shown) that allows rotation only in the direction in which the expander 21 drives the engine 5 is provided at an appropriate location of the drive shaft 33.

  The condenser 23 is formed with an inlet 23a through which the working fluid flows and an outlet 23b through which the working fluid flows out. The condenser 23 exchanges heat between the working fluid that circulates inside and air outside the vehicle, and cools and liquefies the working fluid that has been decompressed by the expansion in the expander 21. An electric fan 23 c is provided in the vicinity of the condenser 23. The electric fan 23 c is electrically connected to the control device 11.

  The bypass path 29 causes the working fluid to bypass the expander 21 by circulating the working fluid therein. The flow rate adjusting valve 31 can adjust the flow rate of the working fluid flowing into the expander 21 and the flow rate of the working fluid flowing into the bypass passage 29. The flow rate adjustment valve 31 is electrically connected to the control device 11.

  The pressurized air boiler 19, the expander 21, the condenser 23, the bypass passage 39 and the flow rate adjustment valve 31 are connected by pipes 25 to 28. Specifically, the outlet 23 b of the condenser 23 and the second inlet 19 c of the pressurized air boiler 19 are connected by a pipe 25. The second outlet 19 d of the pressurized air boiler 19 and the flow rate adjustment valve 31 are connected by a pipe 26. The flow rate adjusting valve 31 and the inflow port 21 a of the expander 21 are connected by a pipe 27. The outlet 21 b of the expander 21 and the inlet 23 a of the condenser 23 are connected by a pipe 28. In addition, one end side of the bypass path 33 is connected to the flow rate adjustment valve 31, and the other end side is connected to the pipe 28.

  The electric pump P <b> 1 is provided in the pipe 25. The electric pump P1 can change the discharge amount of the working fluid like a first discharge amount and a second discharge amount described later. The electric pump P1 is electrically connected to the control device 11.

  By operating this electric pump P1, the working fluid flows from the electric pump P1 to the condenser 23 through the pressurized air boiler 19, the bypass passage 29 or the expander 21 as shown in FIGS. It circulates in the piping 25-38. That is, in the flow direction of the working fluid in the Rankine cycle 3, the bypass path 29 branches from the pipe 26 downstream of the pressurized air boiler 19 and joins the pipe 28 upstream of the inlet 23 a of the condenser 23.

  As shown in FIG. 1, the pressure sensor 35 is provided in the pipe 27. This pressure sensor 35 is based on the pressure of the working fluid flowing through the pipe 27, of the pressure of the working fluid from the downstream of the electric pump P 1 to the upstream of the expander 21 (evaporation pressure of Rankine cycle 3). The pressure of the working fluid downstream of the boiler 19 is detected as a detection pressure α. The pressure sensor 35 is electrically connected to the control device 11 and transmits the detected pressure α to the control device 11. The pressure sensor 35 is a public article. Further, the pressure sensor 35 may be provided in the pipes 25 and 26.

  The control device 11 functions as a control unit for the electric pump P1, the flow rate adjustment valve 31, and the like. Specifically, the control device 11 transmits the control signals C1, C2, etc. to the electric pump P1 based on the output request from the drive system 1, thereby controlling the operation of the electric pump P1, that is, the working fluid by the electric pump P1. The discharge amount is controlled. The control device 11 determines the magnitude of the output request from the drive system 1 based on the accelerator opening.

  Further, the control device 11 stores the preset evaporation pressure set in advance. This set evaporation pressure is set to a value having a certain margin with respect to the upper limit pressure of the expander 21 and the like. The control device 11 compares the stored set evaporation pressure with the detected pressure α received from the pressure sensor 35, transmits control signals C 3, C 4, etc. to the flow rate adjustment valve 31, and causes the flow rate adjustment valve 31 to Perform flow control. Furthermore, the control device 11 adjusts the amount of heat that the working fluid radiates to the outside air by controlling the operation of the electric fan 23c. The control signals C1 to C4 (see the broken line arrows in FIGS. 2 and 3) will be described later.

  The waste heat utilization apparatus configured as described above operates as follows by driving the vehicle.

  As shown in FIG. 2, the engine 5 operates in the drive system 1 by driving the vehicle. As a result, the exhaust discharged from the exhaust port 5a is discharged from the muffler to the outside of the vehicle through the pipe 9, the turbocharger 7 and the pipe 12 (see the one-dot chain line arrow in the figure). At this time, the turbocharger 7 is operated by the exhaust. Thereby, the air outside the vehicle is sucked into the turbocharger 7 from the pipe 13 and compressed. This air is sucked as pressurized air into the engine 5 from the intake port 5b of the engine 5 through the pipe 10, the first passage 19e of the pressurized air boiler 19 and the pipe 11 (see the two-dot chain line arrow in the figure). . In addition, although illustration is abbreviate | omitted, a cooling water circulates between the engine 5 (outflow port and inflow port) and a radiator, and the engine 5 is also cooled.

  In addition, the control device 11 transmits a control signal C1 to the electric pump P1. Thereby, the electric pump P1 discharges the working fluid at a predetermined first discharge amount. In addition, the control device 11 controls the flow rate adjusting valve 31 so that the piping 26 and the piping 27 are communicated, and the piping 26 and 27 and the bypass passage 29 are not communicated.

  As a result, in Rankine cycle 3, as shown by the solid line arrow in the figure, the working fluid discharged by the electric pump P1 passes through the pipe 25 to the second passage 19f from the second inlet 19c of the pressurized air boiler 19. It reaches. The working fluid exchanges heat with the pressurized air in the pressurized air boiler 19. At this time, since the pressurized air flowing through the first passage 19e has a heat of about 150 ° C., the working fluid flowing through the second passage 19f is suitably heated. On the other hand, the pressurized air that circulates through the first passage 19e radiates heat to the working fluid that circulates through the second passage 19f, and therefore reaches the engine 5 from the suction port 5b while being cooled to a certain degree. .

  Thus, the working fluid heated by the pressurized air boiler 19 flows out of the second outlet 19d in a high temperature and high pressure state, and flows into the pipe 27 from the pipe 26. At this time, the pressure sensor 35 detects the evaporation pressure downstream of the pressurized air boiler 19 as the detected pressure α based on the pressure of the working fluid flowing through the pipe 27, and transmits the detected pressure α to the control device 11. Then, the control device 11 compares the stored set evaporation pressure with the detected pressure α received from the pressure sensor 35. Here, when the detected pressure α is equal to the set evaporating pressure, or when the detected pressure α is within a predetermined deviation from the set evaporating pressure, the control device 11 sends a control signal C3 to the flow rate adjusting valve 31. Send. As a result, the flow rate adjusting valve 31 has a flow rate of working fluid flowing into the expander 21 (flow rate of working fluid flowing into the piping 27 from the piping 26) and a flow rate of working fluid flowing into the bypass passage 29 (bypassing from the piping 26). The flow rate of the working fluid flowing into the passage 29). Then, as described above, the pipe 26 and the pipe 27 are communicated, and the pipes 26 and 27 and the bypass path 29 are not communicated, and the entire amount of the working fluid heated by the pressurized air boiler 19 is expanded. To flow into.

  The working fluid flowing through the pipe 27 reaches the inside of the expander 21 from the inlet 21 a of the expander 21. The high-temperature and high-pressure working fluid expands in the expander 21 and is depressurized. The rotational energy is generated in the expander 21 by the pressure energy at this time. This rotational driving force is regenerated to the engine 5 via the drive shaft 33, the pulley 17 and the crankshaft 15.

  The working fluid depressurized in the expander 21 flows out from the outlet 21 b and reaches the condenser 23 from the inlet 23 a of the condenser 23. The working fluid of the condenser 23 dissipates heat to the air around the condenser 23 and is cooled. At this time, the control device 11 appropriately changes the operating amount of the electric fan 23c to suitably dissipate the working fluid and liquefy it. The cooled working fluid flows out from the outflow port 23 b and reaches the pressurized air boiler 19 again through the pipe 25.

  The control device 11 can determine the magnitude of the output request of the drive system 1 based on the accelerator opening. Therefore, when the accelerator opening increases and the control device 11 determines that the output request of the drive system 1 is greater than a predetermined value, the control device 11 controls the electric pump P1 as shown in FIG. A control signal C2 is transmitted. As a result, the electric pump P1 discharges the working fluid with a second discharge amount larger than the first discharge amount.

  Thereby, the flow rate of the working fluid circulating through the pipes 25 to 28 is increased, and the flow rate of the working fluid flowing into the pressurized air boiler 19 is increased. For this reason, in heat exchange in the pressurized air boiler 19, the working fluid receives more heat radiation from the pressurized air. As a result, the pressurized air can be further cooled.

  In this case as well, the pressure sensor 35 detects the pressure of the working fluid flowing through the pipe 27 and transmits the detected pressure α to the control device 11. Then, the control device 11 compares the stored set evaporation pressure with the detected pressure α received from the pressure sensor 35.

  As described above, in the state shown in FIG. 3, since the flow rate of the working fluid discharged from the electric pump P1 is large, the detected pressure α detected by the pressure sensor 35 is larger than that shown in FIG. For this reason, when the control device 11 determines that the detected pressure α exceeds the set evaporation pressure, the control device 11 transmits a control signal C4 to the flow rate adjustment valve 31.

  The flow rate adjustment valve 31 that has received the control signal C4 communicates the pipe 26 with the pipe 27 and the bypass passage 29, respectively, and the flow rate of the working fluid flowing into the expander 21 and the working fluid flowing into the bypass passage 29 are communicated. Adjust the flow rate. Accordingly, a part of the working fluid flowing through the pipe 26 is caused to flow into the bypass passage 29, thereby suppressing the flow rate of the working fluid flowing into the expander 21. Note that the flow rate of the working fluid flowing into the bypass passage 29 is appropriately adjusted based on the deviation amount between the detected pressure α and the set evaporation pressure.

  Thereby, the evaporation pressure of the working fluid acting on the expander 21 is adjusted, and the expander 21 can appropriately expand and depressurize the working fluid. The working fluid that has passed through the expander 21 merges with the working fluid that has passed through the bypass passage 29 and is then radiated by the condenser 23.

  Thus, in this waste heat utilization apparatus, the working fluid can be sufficiently heated by the pressurized air boiler 19. For this reason, in this waste heat utilization apparatus, the pressure energy when the working fluid is expanded and depressurized by the expander 21 can be increased. Thereby, in this waste heat utilization apparatus, the amount of energy recoverable in the Rankine cycle 3, that is, the rotational driving force regenerated in the engine 5 can be increased.

  Moreover, in this waste heat utilization apparatus, it is possible to cool pressurized air by heat exchange in the pressurized air boiler 19. For this reason, a lot of pressurized air can be supplied to the engine 5. Furthermore, in this waste heat utilization apparatus, when the output request by the drive system 1 exceeds a predetermined value, the electric pump P1 can increase the discharge amount of the working fluid. For this reason, when the output request by the drive system 1 exceeds a predetermined value, the electric pump P1 changes from the first discharge amount to the second discharge amount, and increases the flow rate of the working fluid circulating through the pipes 25 to 28, Many working fluids can flow into the pressurized air boiler 19. Thereby, in this waste heat utilization apparatus, it is possible to sufficiently supply pressurized air to the engine 5 in response to an output request from the drive system 1.

  Further, the waste heat utilization device includes a bypass passage 29, a flow rate adjustment valve 31, and a control device 11. The flow rate adjusting valve 31 can adjust the flow rate of the working fluid that flows into the expander 21 and the flow rate of the working fluid that flows into the bypass passage 29 among the working fluid that has passed through the pressurized air boiler 19. Yes.

  For this reason, in this waste heat utilization apparatus, the discharge amount of the electric pump P1 becomes a second discharge amount that is larger than the first discharge amount corresponding to the set evaporation pressure, and the flow rate of the working fluid flowing into the pressurized air boiler 19 is large. Even in this case, the flow rate of the working fluid flowing into the expander 21 can be suppressed, and the evaporation pressure can be maintained below the set evaporation pressure. At this time, the control device 11 controls the flow rate adjustment valve 31 by comparing the set evaporating pressure with the detected pressure α detected by the pressure sensor 35, and therefore acts on the expander 21 out of the evaporating pressure of the Rankine cycle 3. A situation where the evaporation pressure exceeds the set evaporation pressure can be suitably avoided. For this reason, in this waste heat utilization apparatus, it is not necessary to provide the Rankine cycle 3 with the expander etc. with which the upper limit pressure was designed large.

  Therefore, according to the waste heat utilization apparatus of the present invention, the durability can be increased at low cost while improving the output of the engine 5.

  In particular, in this waste heat utilization device, the control device 11 controls the flow rate adjustment valve 31 based on the comparison between the set evaporation pressure stored in the control device 11 and the detected pressure α detected by the pressure sensor 35. The flow rate of the working fluid flowing into the expander 21 is suppressed. For this reason, in this waste heat utilization apparatus, the flow rate of the working fluid flowing into the expander 21 is suitably suppressed while maintaining the evaporation pressure of the Rankine cycle 3 within the range of the set pressure of the expander 21. For this reason, in this waste heat utilization apparatus, the rotational driving force when the working fluid is expanded and depressurized by the expander 21 while avoiding the situation where the evaporation pressure acting on the expander 21 exceeds the set pressure of the expander 21. Can be made as large as possible. For this reason, in this waste heat utilization apparatus, it is possible to increase the power that can be regenerated in the engine 5.

  While the present invention has been described with reference to the embodiments, it is needless to say that the present invention is not limited to the above-described embodiments and can be appropriately modified and applied without departing from the spirit thereof.

  For example, a clutch may be provided between the pulley 17 and the drive shaft 33. In this case, an electromagnetic clutch or a multi-plate clutch can be employed.

  Further, in addition to the pressurized air boiler 19, a boiler capable of exchanging heat between the cooling water and the working fluid may be provided. In this case, since the working fluid can be heated also by the heat of the cooling water, that is, the waste heat of the engine 5, etc., the working fluid can be heated more suitably, and the power that can be regenerated in the engine 5 can be increased. It becomes possible. Further, since the cooling water can be cooled by heat exchange with the working fluid, the engine 5 can be suitably cooled even if the radiator or the like is downsized.

  Furthermore, you may provide a well-known receiver in the upstream of the electric pump P1 in the piping 25. FIG. In this case, since the working fluid is suitably liquefied by the receiver, the working fluid that has passed through the condenser 23 is suitably discharged by the electric pump P <b> 1 and is preferably circulated through the pipes 25 to 28 and the bypass path 29. . In particular, in this waste heat utilization apparatus, since the working fluid flowing through the bypass passage 29 is not decompressed by the expander 21, the effect of providing a receiver is increased.

  In addition, instead of the bypass passage 29 and the flow rate adjustment valve 31, the flow rate ratio for changing the ratio of the flow rate of the working fluid flowing into the expander 21 and the flow rate of the working fluid discharged from the electric pump P1 as the evaporation pressure suppressing means. Changing means may be adopted. As the flow rate ratio changing means, the evaporating pressure can be reduced by increasing the rotational speed of the expander 21 by a speed change means capable of changing the rotational speed of the expander 21. Further, the evaporation pressure can be lowered by increasing the suction capacity of the expander by the capacity control means capable of changing the suction capacity per unit rotation number of the expander 21.

  The present invention is applicable to vehicles and the like.

DESCRIPTION OF SYMBOLS 1 ... Drive system 3 ... Rankine cycle 5 ... Engine (internal combustion engine)
7 ... Turbocharger (supercharger)
DESCRIPTION OF SYMBOLS 19 ... Pressurized air boiler 21 ... Expander 23 ... Condenser 25-28 ... Pipe 29 ... Bypass path (evaporation pressure suppression means)
31 ... Flow rate adjusting valve (evaporation pressure suppression means)
35 ... Pressure sensor (pressure detection means)
P1 ... Electric pump (pump)
α… Detection pressure

Claims (7)

  1. Used in a drive system having an internal combustion engine and a supercharger that supplies pressurized air to the internal combustion engine, and provided with a Rankine cycle for circulating a working fluid,
    The Rankine cycle includes a pump, a pressurized air boiler that exchanges heat between the pressurized air and the working fluid, an expander, a condenser, the pump, the pressurized air boiler, and the expander. And a waste heat utilization device having a pipe for circulating the working fluid in the order of a condenser,
    The pump can increase the discharge amount of the working fluid when the output request by the drive system exceeds a predetermined value,
    Use of waste heat characterized by comprising evaporation pressure suppression means for suppressing an increase in evaporation pressure of the Rankine cycle accompanying an increase in the discharge amount when the discharge amount of the working fluid by the pump increases apparatus.
  2. Pressure detecting means for detecting the evaporation pressure downstream of the pressurized air boiler as a detection pressure;
    The waste heat utilization apparatus according to claim 1, wherein a predetermined set evaporation pressure is compared with the detected pressure, and an increase in the evaporation pressure is suppressed by the evaporation pressure suppression unit.
  3. The evaporating pressure suppression means branches from the pipe downstream of the pressurized air boiler, bypasses the expander and joins the pipe, the flow rate of the working fluid flowing into the expander, and the The waste heat utilization apparatus according to claim 1 or 2, further comprising a flow rate adjustment valve capable of adjusting a flow rate of the working fluid flowing into the bypass passage.
  4.   The waste according to claim 1 or 2, wherein the evaporating pressure suppressing means is a flow rate ratio changing means for changing a ratio between a flow rate of the working fluid flowing into the expander and a flow rate of the working fluid discharged from the pump. Heat utilization device.
  5.   The waste heat utilization apparatus according to claim 4, wherein the flow rate ratio changing means is a capacity control means capable of changing a suction capacity per unit rotation number of the expander.
  6.   The waste heat utilization apparatus according to claim 4, wherein the flow rate ratio changing means is a speed change means capable of changing a rotation speed of the expander.
  7.   The waste heat utilization apparatus according to any one of claims 1 to 5, wherein the expander and the internal combustion engine are configured to be able to transmit power.
JP2011209817A 2011-09-26 2011-09-26 Waste heat utilization device Withdrawn JP2014231740A (en)

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JP2011209817A JP2014231740A (en) 2011-09-26 2011-09-26 Waste heat utilization device
PCT/JP2012/062028 WO2013046791A1 (en) 2011-09-26 2012-05-10 Waste heat utilization apparatus

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2017066917A (en) * 2015-09-29 2017-04-06 株式会社神戸製鋼所 Thermal energy recovery system
US10550730B2 (en) 2017-04-28 2020-02-04 Toyota Jidosha Kabushiki Kaisha Waste heat recovery system

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Publication number Priority date Publication date Assignee Title
CA2888115A1 (en) * 2012-10-17 2014-04-24 Norgren Limited Vehicle waste heat recovery system
JP6060040B2 (en) * 2013-06-07 2017-01-11 株式会社神戸製鋼所 Waste heat recovery device and operation control method of waste heat recovery device
AT517913B1 (en) * 2015-07-10 2018-03-15 Avl List Gmbh Method for controlling a heat exchange system for a motor vehicle

Family Cites Families (4)

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FR2449780B1 (en) * 1979-02-22 1983-01-21 Semt
JP4855105B2 (en) * 2006-03-06 2012-01-18 日野自動車株式会社 Auxiliary equipment for supercharger using exhaust heat energy of EGR gas
JP2011106302A (en) * 2009-11-13 2011-06-02 Mitsubishi Heavy Ind Ltd Engine waste heat recovery power-generating turbo system and reciprocating engine system including the same
JP5481737B2 (en) * 2010-09-30 2014-04-23 サンデン株式会社 Waste heat utilization device for internal combustion engine

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2017066917A (en) * 2015-09-29 2017-04-06 株式会社神戸製鋼所 Thermal energy recovery system
US10550730B2 (en) 2017-04-28 2020-02-04 Toyota Jidosha Kabushiki Kaisha Waste heat recovery system

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