JP2011140879A - Waste heat recovery system of supercharged engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a waste heat recovery system efficiently recovering waste heat from a supercharged engine. <P>SOLUTION: In the waste heat recovery system 1 of the supercharged engine, a supercharger 2 generating compressed air from outside air, an air cooler 10 cooling the compressed air, and an air supply port 3a of the internal combustion engine 3 are arranged in sequence along an air supply line L4. In the waste recovery system, an ebullient cooling device 31 of the internal combustion engine 3 generating water vapor from engine cooling water by ebullient cooling, a displacement type expander 20 outputting power by expanding the water vapor, and a condenser 8 liquefying the water vapor are arranged in sequence. The waste heat recovery system includes a water vapor heater 30 for heating the water vapor in the displacement type expander 20 by performing heat exchange between the compressed air before passing the air cooler 10 and the water vapor in the displacement type expander 20, and outputs power by expanding the heated water vapor in the displacement type expander 20. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a waste heat recovery system for a supercharged engine.

  An example of a waste heat recovery system that extracts power from waste heat escaped to exhaust gas is disclosed in Patent Document 1. The power recovery apparatus of Patent Document 1 includes a steam generator (3), an expander (5, 6), and a condenser (7) for performing the Rankine cycle. The steam generator (3) generates water vapor by utilizing the heat of the exhaust gas discharged from the internal combustion engine (1). A power generator (9) is connected to the expander (5, 6), and power is generated by driving the expander (5, 6). That is, the power recovery device of Patent Document 1 performs combined cycle power generation. The power recovery apparatus includes lubricating oil passages (31, 32, 33, 34) that pass through the two expanders (5, 6) in order. For this reason, part of the heat loss and engine loss of the high-pressure stage expander (5) is recovered as the output of the low-pressure stage expander (6) by heat exchange of the expander lubricating oil. That is, waste heat is recovered as power in both the expanders (5, 6).

JP 2008-175123 A

  In the non-supercharged engine, about 1/3 of the fuel energy escapes to the engine cooling water (jacket water), and about 1/3 of the fuel energy escapes to the exhaust gas. A power recovery device that recovers the amount of heat escaped to the engine cooling water and a power recovery device that recovers the amount of heat escaped to the exhaust gas (for example, Patent Document 1) are known.

  FIG. 6 shows a cooling system 901 of a general supercharged engine 902. The cooling system 901 includes an internal combustion engine 903, a turbine 905, a compressor 906, an engine cooling water pump 907, an engine cooling water cooler 908, a secondary cooling water pump 909, an air cooler 910, and a load 911. In the supercharged engine 902, the turbine 905 is driven by the exhaust gas of the internal combustion engine 903, and the compressor 906 is driven by the turbine 905. A supply gas to the internal combustion engine 903 is compressed by the compressor 906. Since the air supply gas heated by the compression heat by the air cooler 910 can be cooled, it is possible to prevent the supply air gas from expanding due to the compression heat. Since the compressed air is supplied to the internal combustion engine 903 without expanding, the output of the internal combustion engine 903 is improved. Further, since the power for generating the compressed air is obtained by the exhaust gas, a part of the fuel energy escaped to the exhaust gas moves to the supply gas in the form of compression heat and is recovered by the air cooler 910.

  In the supercharged engine 902, a new amount of heat is released to the air cooler 910. In a supercharged engine at a 500 kW level, about 1/6 of the fuel energy escapes from the water jacket 932 to the engine cooling water, and about 1/6 of the fuel energy escapes from the air cooler 910 to the engine cooling water. In the air cooler 910, the compressed air is cooled and the engine coolant is heated. The amount of heat that escapes from the water jacket 932 to the engine cooling water is halved, but the amount of heat that escapes from the air cooler 910 to the engine cooling water is newly generated.

  In order to recover the fuel energy that escapes to the air cooler 910, it is necessary to recover the amount of heat from the engine coolant that passes through the outlet of the air cooler 910. However, the temperature of the engine cooling water at the outlet of the air cooler 910 is lowered in order to optimize the temperature of the supply gas, and is about 55 ° C., for example. The temperature is too low to recover the waste heat escaped from the air cooler 910 to the engine coolant by the Rankine cycle.

  Therefore, the present invention provides a waste heat recovery system that can efficiently recover waste heat from a supercharged engine.

  The present invention relates to a supercharged engine in which a supercharger that generates compressed air from outside air, an air cooler that cools the compressed air, and an air supply port of an internal combustion engine are sequentially arranged along an air supply line. In a waste heat recovery system, a boiling cooling device for an internal combustion engine that generates steam from engine cooling water by boiling cooling along an engine cooling water line, a positive displacement expander that outputs power by expanding the steam, and A condenser for liquefying water vapor is arranged in order, and heat exchange is performed between the compressed air before passing through the air cooler and the water vapor in the positive displacement expander, thereby the positive displacement expansion. Provided is a waste heat recovery system for a supercharged engine provided with a steam heater for heating the steam in the machine.

  For this reason, the compressed air is cooled and the steam of the engine cooling water that operates the expander is heated. As a result, the output of the expander is improved and the amount of air taken into the internal combustion engine is increased. Therefore, the waste heat recovery system can efficiently recover the waste heat escaped to the exhaust gas and the engine cooling water.

  The present invention can preferably employ the following configurations (a) to (d).

(A) The water vapor heater includes a heating chamber provided in the positive displacement expander and allowing the compressed air to pass therethrough.

  For this reason, the waste heat recovery system can perform heat exchange between compressed air and water vapor with a simple configuration.

(B) A heating chamber in which the liquid medium is a medium for performing heat exchange between the compressed air and the water vapor, and the water vapor heater is provided in the positive displacement expander and allows the liquid medium to pass therethrough. And a liquid medium heater for performing heat exchange between the compressed air and the liquid medium.

  For this reason, even if it is a case where a heating chamber cannot be largely formed in an expander, the waste heat recovery system can heat the water vapor | steam in an expansion chamber favorably.

(C) A secondary cooling water line for circulating secondary cooling water used for heat exchange in the condenser and the air cooler is provided, and in the secondary cooling water line, the condenser is Arranged upstream of the air cooler.

  For this reason, compressed air can be cooled with a comparatively small air cooler. That is, the waste heat recovery system can reduce the cost of the air cooler.

(D) The waste heat recovery system performs heat exchange between the compressed air that has passed through the heating chamber and before passing through the air cooler, and the engine cooling water that has passed through the condenser. And a condensate preheater for cooling the compressed air and heating the engine coolant.

  For this reason, a part of the heat quantity escaped from the internal combustion engine to the compressed air moves to the engine cooling water. Therefore, even if the amount of heat that escapes from the internal combustion engine to the engine coolant does not change, the amount of evaporation from the engine coolant increases, and the output of the expander increases.

1 is an overall view showing a waste heat recovery system of a supercharged engine (first embodiment). It is side surface sectional drawing of a scroll type expander. It is a front view of a fixed scroll and a cover. It is a general view which shows the waste heat recovery system of a supercharged engine (2nd Embodiment). It is a general view which shows the waste heat recovery system of a supercharged engine (3rd Embodiment). It is a general view which shows the cooling system of a supercharged engine (conventional).

(First embodiment)
FIG. 1 is an overall view showing a waste heat recovery system 1 of a supercharged engine 2 in the first embodiment. The waste heat recovery system 1 is applied to a supercharged engine 2. The supercharged engine 2 includes an internal combustion engine 3 and a supercharger 4. The supercharger 4 includes a turbine 5 and a compressor 6. The waste heat recovery system 1 includes an internal combustion engine 3, a turbine 5, a compressor 6, an engine cooling water pump 7, an engine cooling water cooler 8, a secondary cooling water pump 9, an air cooler 10, an engine cooling water line L1, and a secondary. A cooling water line L2, an exhaust line L3, and an air supply line L4 are provided. The engine cooling water line L1, the secondary cooling water line L2, the exhaust line L3, and the air supply line L4 are respectively illustrated by a one-dot chain line, a two-dot chain line, a solid line, and a broken line. Reference numeral 11 denotes a load applied to the internal combustion engine 3. A power generator 12 is connected to the expander 20.

  On the engine cooling water line L1, the boiling cooling device 31, the expander 20, the condenser 8, the engine cooling water pump 7, and the water jacket 32 of the internal combustion engine 3 are arranged in this order. An engine cooling water cooler 8, a secondary cooling water pump 9, and an air cooler 10 are arranged on the secondary cooling water line L2. The exhaust port 3b and the turbine 5 of the internal combustion engine 3 are disposed on the exhaust line L3. On the air supply line L4, the compressor 6, the expander 20, the condensate preheater 13, the air cooler 10, and the air supply port 3a of the internal combustion engine 3 are arranged.

  The waste heat recovery system 1 operates as follows. First, the internal combustion engine 3, the engine cooling water pump 7, and the secondary cooling water pump 9 are activated.

  The engine cooling water circulates along the engine cooling water line L1. The engine cooling water evaporates by passing through the boiling cooling device 31, and water vapor is generated. On the outlet side of the internal combustion engine 3, the temperature of the water vapor (engine cooling water) is about 80 to 120 ° C. Water vapor loses pressure and heat in the expansion chamber R1 provided in the expander 20. The temperature of the water vapor on the outlet side of the expansion chamber R1 is about 50 ° C. Instead, the expander 20 is driven. Electric power is generated in the generator 12 by the output of the expander 20. As a result, a part of the heat quantity escaped to the engine cooling water is recovered by the waste heat recovery system 1. The water vapor that has passed through the expander 20 is liquefied in the condenser 8 to generate engine cooling water. The engine cooling water in the condenser 8 is sent to the water jacket 32 in the internal combustion engine 3 by the engine cooling water pump 7.

  The exhaust gas is discharged from the exhaust port 3b of the internal combustion engine 3 along the exhaust line L3. As the exhaust gas passes through the turbine 5, the turbine 5 is driven. The exhaust gas that has passed through the turbine 5 is discharged to the outside air.

  The supply gas is sucked from outside air along the supply line L4. The compressor 6 is driven by the turbine 5, and the supply gas is compressed in the compressor 6 to generate compressed air. The compressed air loses heat in the heating chamber R <b> 2 provided in the expansion chamber 20. The temperature of the compressed air is about 160 ° C. on the inlet side of the heating chamber R2 and about 80 ° C. on the outlet side of the heating chamber R2. Instead, the water vapor in the expansion chamber R1 adjacent to the heating chamber R2 in the expander 20 is heated. Since the amount of heat is supplemented to the steam that loses the amount of heat due to expansion in the expansion chamber R1, the output of the expander 20 is improved. The compressed air that has passed through the expander 20 is further cooled in the air cooler 10. The temperature of the compressed air on the outlet side of the air cooler 10 is about 60 ° C. The compressed air that has passed through the air cooler 10 is sucked into the air supply port 3 a of the internal combustion engine 3.

  The secondary cooling water circulates along the secondary cooling water line L <b> 2 by the operation of the secondary cooling water pump 9. In the condenser 8, heat exchange is performed between the secondary cooling water and the steam of the engine cooling water, and the secondary cooling water is heated. In the air cooler 10, heat exchange is performed between the secondary cooling water and the compressed air, and the secondary cooling water is heated. The secondary cooling water that has passed through the air cooler 10 is sent to the secondary cooling water pump 9.

  In the waste heat recovery system 1, the expander 20 is driven by steam of engine cooling water. Therefore, the waste heat recovery system 1 performs a Rankine cycle using the engine cooling water as a working medium in the engine cooling water line L1. Further, the steam of the engine cooling water is generated by the amount of heat generated by the internal combustion engine 3. That is, the Rankine cycle is performed by the waste heat of the internal combustion engine. For this reason, the waste heat recovery system 1 is performing steam power generation with the exhaust heat of internal combustion power generation, and can implement a combined cycle.

  With reference to FIG. 2, FIG. 3, the structure of the expander 20 provided with expansion chamber R1 and heating chamber R2 is demonstrated. FIG. 2 is a side sectional view of the scroll type expander 20. The scroll type expander 20 is one of positive displacement type expanders. The scroll expander 20 includes a fixed scroll 21, an orbiting scroll 22, a crankshaft 23, a bearing 24, a cover 25, and a bearing 26. The orbiting scroll 22 is supported by the eccentric portion 23 a of the crankshaft 23 via a bearing 24. A main body portion 23 b of the crankshaft 23 is supported by the fixed scroll 21 via a bearing 26. The shaft center A24 of the bearing 24 is different from the shaft center A26 of the bearing. The shaft center A24 of the bearing 24 is equal to the shaft center of the eccentric portion 23a, and the shaft center A26 of the bearing is equal to the shaft center of the main body portion 23b of the crankshaft 23. Therefore, the orbiting scroll 22 rotates around the axis A23 and revolves around the axis A26.

  The fixed scroll 21 includes an end plate 21a, a scroll wall 21b, and a second scroll wall 21c. The orbiting scroll 22 includes an end plate 22a and a scroll wall 22b. The end plate 21a of the fixed scroll 21 and the end plate 22a of the swing scroll 22 are disk-shaped plate members. In the fixed scroll 21, the scroll wall 21b and the second scroll wall 21c are arranged on the opposite side to the end plate 21a. The scroll wall 21b and the second scroll wall 21c are plate members which are perpendicular to the end plate 21a and spiral. In the orbiting scroll 22, the scroll wall 22b is a plate-like member that is perpendicular and spiral to the end plate 22a. The cover 25 is fixed to the fixed scroll 21 so as to cover the inside of the second scroll wall 21c. The cover 25 is an annular plate member.

  The expansion chamber R1 is a space surrounded by the end plates 21a and 21b and the scroll walls 21b and 22b. Since the scroll walls 21b and 22b are in contact with each other, the space between the scroll walls 21b and 22b is divided into a plurality of locations. For this reason, a plurality of expansion chambers R <b> 1 are formed between the fixed scroll 21 and the swing scroll 22. The inlet 21d of the expansion chamber R1 is formed at the center of the end plate 21a. The outlet 21e of the expansion chamber R1 is formed on the outer peripheral portion of the scroll wall 21b. The steam of the engine cooling water is supplied from the inlet 21d into the expansion chamber R1, and is discharged from the expansion chamber R1 via the outlet 21e.

  FIG. 3 is a front view of the fixed scroll 21 and the cover 25. The heating chamber R2 is a space surrounded by the end plate 21a, the scroll wall 21b, and the cover 25. The heating chamber R2 is a spiral space. The inlet 21f of the heating chamber R2 is formed on the outer periphery of the second scroll wall 21c. The outlet 21g of the heating chamber R2 is formed in the center of the cover 25. The compressed air is supplied from the inlet 21f into the heating chamber R2, and is discharged from the heating chamber R2 via the outlet 21g. The compressed air moves along a spiral path formed by the second scroll wall 21c in the heating chamber R2.

  In the expansion chamber R1 and the heating chamber R2, the positions of the inlet and the outlet are set on the opposite sides. The inlet 21d of the expansion chamber R1 is disposed on the center side (axis A26 side), while the inlet 21f of the heating chamber R2 is disposed on the outer peripheral side. The outlet 21e of the expansion chamber R1 is disposed on the outer peripheral side, while the outlet 21g of the heating chamber R2 is disposed on the center side. For this reason, the water vapor having the lowest temperature is heated by the compressed air having the highest temperature.

  The first embodiment has the following actions and effects.

  The waste heat recovery system 1 includes a steam heater 30 that heats the steam in the expander 20 by exchanging heat between compressed air and steam. The steam heater 30 is configured by a part (the fixed scroll 21 and the cover 25) of the expander 20 that forms the heating chamber R2. For this reason, the compressed air is cooled and the steam of the engine cooling water that operates the expander is heated. As a result, the output of the expander 20 is improved and the amount of air sucked into the internal combustion engine 3 is increased. Therefore, the waste heat recovery system 1 can efficiently recover the waste heat escaped to the exhaust gas and the engine cooling water.

  For example, the waste heat recovery system 1 (this embodiment) having the air cooler 10 can increase the output of the expander 20 by about 80% compared to the waste heat recovery system not having the air cooler 10.

  Further, the water vapor heater 30 includes a heating chamber R2 provided in the expander 20 and allowing compressed air to pass therethrough. For this reason, the waste heat recovery system 1 can perform heat exchange between compressed air and water vapor with a simple configuration.

  Further, a heating fin (second scroll wall 21c) is disposed in the heating chamber R2. For this reason, heat exchange between compressed air and water vapor is promoted.

  Furthermore, the condenser 8 is arrange | positioned in the upstream of the air cooler 10 in the secondary cooling water line L2. Since the compressed air that passes through the air cooler 10 is cooled in the expander 20, the amount of heat that the air cooler 10 needs to take away from the compressed air is small. For this reason, the compressed air can be cooled by the relatively small air cooler 10. That is, the waste heat recovery system 1 can reduce the cost of the air cooler 10.

(Second Embodiment)
FIG. 4 is an overall view showing the waste heat recovery system 1 of the supercharged engine 2 in the second embodiment. The second embodiment further includes a condensate preheater 13 in addition to the configuration of the first embodiment. In the configuration other than the condensate preheater 13, the configurations of the first and second embodiments are the same. The description of the configuration common to the first and second embodiments is omitted as appropriate.

  The condensate preheater 13 (air cooler) is disposed between the condenser 8 and the water jacket 32 of the internal combustion engine 3 in the engine cooling water line L1. The condensate preheater 13 is disposed between the expander 20 (heating chamber R2) and the air cooler 10 in the air supply line L4. The condensate preheater 13 is an air cooler.

  In the condensate preheater 13, heat exchange is performed between the compressed air between the heating chamber R <b> 2 and the air cooler 10 and the engine cooling water between the condenser 8 and the water jacket 32. As a result, the compressed air is cooled and the engine cooling water is heated.

  The second embodiment has the following operations and effects.

  The second embodiment further includes a condensate preheater 13 in addition to the configuration of the first embodiment. For this reason, a part of the heat quantity escaped from the internal combustion engine 3 to the compressed air moves to the engine cooling water. Therefore, even if the amount of heat that escapes from the internal combustion engine 3 to the engine coolant does not change, the amount of evaporation from the engine coolant increases, and the output of the expander 20 increases.

  The second embodiment includes a condensate preheater 13 in addition to the air cooler 10 as means for cooling the compressed air. For this reason, 2nd Embodiment may be provided with the switching path which switches the bypass path | route which bypasses the air cooler 10, and the main path | route and bypass path which pass the air cooler 10 in the air supply line L4. . The embodiment including the bypass path and the switching valve may bypass the air cooler 10 when the internal combustion engine 3 is in a steady operation state.

(Third embodiment)
FIG. 5 is an overall view showing the waste heat recovery system 1 of the supercharged engine 2 in the third embodiment. The third embodiment is the same as the second embodiment except for the configuration of the steam heater. The reference numeral of the steam heater in the first and second embodiments is 30, and the reference numeral of the steam heater in the third embodiment is 130. The description of the configuration common to the first to third embodiments is omitted as appropriate.

  The steam heater 130 includes a heating chamber R2, a liquid medium heater 14, a liquid medium pump 15, and a liquid medium line L5. On the liquid medium line L5, the liquid medium heater 14, the heating chamber R2, and the liquid medium pump 15 are arranged in this order. The liquid medium is a medium for performing heat exchange between compressed air and water vapor. As the liquid medium, a medium that is in a liquid state in a temperature range to be used is selected.

  As described above, the heating chamber R2 is a space surrounded by a part of the expander 20 (the fixed scroll 21 and the cover 25). The heating chamber R2 is formed by a part of the expander 20 (the fixed scroll 21 and the cover 25). In the first and second embodiments, the heating chamber R2 is filled with compressed air, but in the third embodiment, the heating chamber R2 is filled with a liquid medium. The liquid medium heater 14 is disposed between the compressor 6 and the condensate preheater 13 in the air supply line L4.

  The liquid medium circulates along the liquid medium line L5 by the operation of the liquid medium pump 15. In the liquid medium heater 14, heat exchange is performed between the liquid medium and the compressed air. In the heating chamber R2, heat exchange is performed between the liquid medium and water vapor. As a result, heat exchange is performed between the compressed air and water vapor.

  The third embodiment has the following operations and effects.

  In the third embodiment, the water vapor heater 130 includes a heating chamber R2 and a liquid medium heating chamber 14. The liquid medium has higher heat transfer efficiency than the gaseous medium. For this reason, even if it is a case where heating chamber R2 cannot be largely formed in the expander 20, the waste heat recovery system 1 can heat the water vapor | steam in the expansion chamber R1 favorably.

DESCRIPTION OF SYMBOLS 1 Waste heat recovery system 2 Supercharged engine 3 Internal combustion engine 3a Air inlet 4 Supercharger 8 Condenser 10 Air cooler 14 Liquid medium heater 20 Scroll type expansion machine (volumetric type expansion machine)
30, 130 Steam heater 31 Boiling cooler L1 Engine cooling water line L2 Secondary cooling water line L4 Supply air line R1 Expansion chamber R2 Heating chamber

Claims (5)

A superheater waste heat recovery system in which a supercharger that generates compressed air from outside air, an air cooler that cools the compressed air, and an air supply port of the internal combustion engine are arranged in this order along the air supply line In
A boiling cooling device for an internal combustion engine that generates steam from engine cooling water by boiling cooling along the engine cooling water line, a positive displacement expander that outputs power by expanding the steam, and a condenser that liquefies the steam Are arranged in order,
A steam heater for heating the water vapor in the positive displacement expander by performing heat exchange between the compressed air before passing through the air cooler and the steam in the positive displacement expander; Yes,
A waste heat recovery system for a supercharged engine. The water vapor heater is provided in the positive displacement expander and includes a heating chamber through which the compressed air passes.
The waste heat recovery system for a supercharged engine according to claim 1. The liquid medium is a medium for performing heat exchange between the compressed air and the water vapor,
The water vapor heater includes a heating chamber provided in the positive displacement expander and allowing the liquid medium to pass therethrough, and a liquid medium heater for performing heat exchange between the compressed air and the liquid medium. ing,
The waste heat recovery system for a supercharged engine according to claim 1. A secondary cooling water line for circulating secondary cooling water used for heat exchange in the condenser and the air cooler is provided;
In the secondary cooling water line, the condenser is disposed upstream of the air cooler.
The waste heat recovery system for a supercharged engine according to any one of claims 1 to 3. Heat exchange is performed between the compressed air that has passed through the heating chamber and before passing through the air cooler, and the engine cooling water that has passed through the condenser, thereby cooling the compressed air and It has a condensate preheater that heats engine cooling water.
The waste heat recovery system for a supercharged engine according to any one of claims 1 to 4.

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