WO2002025077A1 - Dispositif de recuperation de la chaleur perdue d'un moteur thermique - Google Patents
Dispositif de recuperation de la chaleur perdue d'un moteur thermique Download PDFInfo
- Publication number
- WO2002025077A1 WO2002025077A1 PCT/JP2001/008258 JP0108258W WO0225077A1 WO 2002025077 A1 WO2002025077 A1 WO 2002025077A1 JP 0108258 W JP0108258 W JP 0108258W WO 0225077 A1 WO0225077 A1 WO 0225077A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- heat exchanger
- exhaust gas
- stage
- exhaust
- combustion engine
- Prior art date
Links
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 35
- 239000002918 waste heat Substances 0.000 title claims abstract description 17
- 238000011084 recovery Methods 0.000 title claims abstract description 13
- 239000007789 gas Substances 0.000 claims abstract description 86
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 13
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 abstract description 30
- 238000012546 transfer Methods 0.000 description 49
- 239000002184 metal Substances 0.000 description 36
- 229910052751 metal Inorganic materials 0.000 description 36
- 239000003054 catalyst Substances 0.000 description 31
- 230000000694 effects Effects 0.000 description 6
- 239000000969 carrier Substances 0.000 description 5
- 238000001816 cooling Methods 0.000 description 5
- 239000007791 liquid phase Substances 0.000 description 5
- 230000007423 decrease Effects 0.000 description 4
- 230000002093 peripheral effect Effects 0.000 description 4
- 239000000463 material Substances 0.000 description 3
- 239000010935 stainless steel Substances 0.000 description 3
- 229910001220 stainless steel Inorganic materials 0.000 description 3
- PXHVJJICTQNCMI-UHFFFAOYSA-N Nickel Chemical compound [Ni] PXHVJJICTQNCMI-UHFFFAOYSA-N 0.000 description 2
- 229910045601 alloy Inorganic materials 0.000 description 2
- 239000000956 alloy Substances 0.000 description 2
- 238000004891 communication Methods 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000012071 phase Substances 0.000 description 2
- 238000000746 purification Methods 0.000 description 2
- 239000002699 waste material Substances 0.000 description 2
- 229910000859 α-Fe Inorganic materials 0.000 description 2
- 238000013459 approach Methods 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 238000005219 brazing Methods 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000011888 foil Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 229910052759 nickel Inorganic materials 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
- 239000013585 weight reducing agent Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/0066—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
- F28D7/0075—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids with particular circuits for the same heat exchange medium, e.g. with the same heat exchange medium flowing through sections having different heat exchange capacities or for heating or cooling the same heat exchange medium at different temperatures
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
- F01N3/02—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust
- F01N3/04—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust using liquids
- F01N3/043—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust using liquids without contact between liquid and exhaust gases
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy
- F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using heat
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D21/0001—Recuperative heat exchangers
- F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
- F28D21/001—Recuperative heat exchangers the heat being recuperated from exhaust gases for thermal power plants or industrial processes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/02—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled
- F28D7/024—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled the conduits of only one medium being helically coiled tubes, the coils having a cylindrical configuration
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
- F02B2275/20—SOHC [Single overhead camshaft]
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/24—Cylinder heads
- F02F2001/244—Arrangement of valve stems in cylinder heads
- F02F2001/245—Arrangement of valve stems in cylinder heads the valve stems being orientated at an angle with the cylinder axis
-
- 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
- the present invention relates to a waste heat recovery device for an internal combustion engine located immediately downstream.
- the evaporator that heats the liquid-phase working medium with the exhaust gas of the internal combustion engine to generate steam and the steam driven by the steam generated by the evaporator Expander, a condenser that cools the vapor that has passed through the expander and returns it to the liquid phase working medium, and a supply pump that pressurizes the liquid phase working medium from the condenser and supplies it to the evaporator.
- a Rankine cycle device is described.
- water as a liquid-phase working medium is passed not only through an evaporator provided in an exhaust pipe of an internal combustion engine but also through a cooling passage formed in a cylinder head and a cylinder block. It heats up, so that the waste heat of the internal combustion engine can be used more effectively, and the cylinder head and the cylinder block are cooled with a liquid-phase working medium to eliminate the conventional Lager system. ing.
- the working medium whose temperature has risen through the cooling passages of the cylinder head and the cylinder block is supplied to the evaporator, so that the temperature difference between the working medium and the exhaust gas becomes small.
- the working medium passing through the evaporator cannot sufficiently recover the heat energy of the exhaust gas, and the heat energy of the exhaust gas that can still be recovered is discharged as it is, thereby increasing the waste heat recovery efficiency of the internal combustion engine as a whole. May decrease.
- the present invention has been made in view of the above circumstances, and has an object to effectively cool a high-temperature exhaust passage immediately downstream of an exhaust valve while securing the efficiency of recovering waste heat from exhaust gas of an internal combustion engine. I do.
- At least three stages of heat exchangers through which a working medium that exchanges heat with exhaust gas flows are provided on an exhaust passage, and the heat exchanger in the exhaust gas flow direction is provided with at least three stages.
- a working medium is first supplied to a heat exchanger arranged most downstream in a flow direction of exhaust gas.
- a waste heat recovery device for an internal combustion engine which is configured to be supplied to a heat exchanger arranged at an uppermost stream in a flow direction of exhaust gas.
- the working medium is first supplied to the heat exchanger arranged at the most downstream in the flow direction of the exhaust gas, and then the exhaust gas is exhausted. Since it is supplied to the heat exchanger arranged at the uppermost stream in the gas flow direction, a relatively low-temperature working medium is supplied to the heat exchanger arranged at the uppermost stream in the exhaust gas flow direction, so that the internal combustion engine is cooled.
- the high-temperature portion immediately downstream of the exhaust valve can be effectively cooled, and the durability of the high-temperature exhaust passage and the peripheral devices can be increased.
- the coldest working medium is supplied to the heat exchanger located at the most downstream in the flow direction of the exhaust gas to which the relatively low-temperature exhaust gas is supplied, a temperature difference between the exhaust gas and the working medium is secured.
- the thermal energy of the exhaust gas that can still be recovered can be recovered without waste, and the heat exchange efficiency can be improved.
- first-stage heat exchanger H1 of the embodiment corresponds to the heat exchanger disposed at the most downstream in the exhaust gas flow direction of the present invention
- second-stage heat exchanger H2 of the embodiment is Invented exhaust gas Corresponds to the heat exchanger located at the most upstream in the flow direction.
- FIG. 1 is a longitudinal sectional view of a cylinder head portion of an internal combustion engine
- FIG. 2 is an enlarged sectional view of a main part of FIG. 1
- FIG. Fig. 4 is a sectional view taken along the line 4-4 in Fig. 2
- Fig. 5 is a sectional view taken along the line 5-5 in Fig. 2
- Fig. 6 is an enlarged view of a main part of Fig. 2
- Fig. Fig. 7 is an enlarged view of part 7 of Fig. 4
- Fig. 8 is a sectional view taken along line 8-8 in Fig. 3
- Figs. 9A to 9C are diagrams showing heat transfer tubes of the fifth stage heat exchanger
- Fig. 9A to 9C are diagrams showing heat transfer tubes of the fifth stage heat exchanger
- FIG. 10 is a metal catalyst unit and Exploded perspective view of a four-stage heat exchanger
- Fig. 11 is a schematic diagram showing the water supply path of the evaporator
- Fig. 12 A shows changes in exhaust gas temperature and steam temperature with respect to the integrated heat transfer area of a conventional heat exchanger
- FIG. 12B is a graph showing changes in the exhaust gas temperature and the steam temperature with respect to the integrated heat transfer area of the heat exchanger of the present embodiment.
- FIGS. 1 to 12B An embodiment of the present invention will be described with reference to FIGS. 1 to 12B.
- the internal combustion engine E includes a cylinder block 11, a cylinder head 12, and a head force bar 13, which are vertically stacked, and a cylinder bore 1 formed in a cylinder block 11.
- Piston 15 is slidably fitted to 4.
- the intake port 17 and exhaust port 18 connected to the combustion chamber 16 formed in the cylinder head 12 the intake port 1 ⁇ is bored inside the cylinder head 12 as before.
- the exhaust port 18 is formed of a separate member and connected to the cylinder head 12.
- the upper end of the stem 26 of the exhaust valve 25 comes into contact with one end of an exhaust rocker arm 28 pivotally supported by an exhaust rocker arm shaft 27.
- the other end of the intake rocker arm 23 and the other end of the exhaust rocker arm 28 correspond to an intake cam 30 and an exhaust cam 31 provided on a camshaft 29 that rotates in conjunction with a crank shaft (not shown). The contact causes the intake valve 20 and the exhaust valve 25 to open and close.
- An exhaust gas purifying device C integrated with an evaporator is provided on the side of the cylinder head 12 on the exhaust side.
- an exhaust gas purifying apparatus C integrated with an evaporator will be described. The structure of will be described.
- the evaporator uses the exhaust gas of the internal combustion engine E as a heat source to generate steam whose temperature and pressure have been increased.
- the evaporator has an exhaust port 18 as a base end and an exhaust passage 33 connected to an exhaust pipe 32, and an exhaust passage 3 3 and a heat exchanger H1 to H5 for exchanging heat with the exhaust gas.
- the metal catalyst devices 46A to 46D described below are provided in the fourth stage heat exchanger H. Incorporated in 4.
- the exhaust port 18 is located on the upstream side in the lengthwise direction of the exhaust gas and has an approximately constant diameter portion 18a having a substantially constant diameter.
- a second-stage heat exchanger H2 is provided on the outer periphery of the equal-diameter portion 18a, and a second-stage heat exchanger H2 is provided inside the enlarged-diameter portion 18b.
- a five-stage heat exchanger H5 is provided.
- the second-stage heat exchanger H2 is composed of one heat transfer tube 34 wound around the outer circumference of the equal-diameter portion 18a by about 5 turns.
- the fifth-stage heat exchanger H5 is composed of one heat transfer tube 35 wound in multiple stages and housed inside the enlarged diameter portion 18b.
- the heat transfer tube 35 of the fifth-stage heat exchanger H5 is tapered along the internal shape of the enlarged diameter portion 18b of the exhaust port 18.
- the inner layer coil is wound in a triple coil shape with the diameter decreasing from the back (left side in the figure) to the front (right side in the figure), and the coil in the middle layer after being folded at the front end is forward.
- the coil of the outer layer which is wound while increasing its diameter from the back to the back, is wound while reducing the diameter from the back to the front after being folded at the rear end.
- the water inlet shown in FIG. 9B is connected to the upstream fourth-stage heat exchanger H4 described later, and the water outlet shown in FIG. 9C is connected to the steam outlet 90 described later.
- Circled numbers 1 to ⁇ ⁇ shown in FIG. 9A indicate paths through which water flows in the heat transfer tubes 35.
- the heat transfer tube 35 of the fifth-stage heat exchanger H5 was wound in a triple coil shape tapered so as to follow the inner shape of the enlarged portion 18b of the exhaust port 18. A rectifying action can be given to the exhaust gas flowing through the diameter portion 18b, thereby contributing to a reduction in flow resistance.
- a disc-shaped distribution passage forming member 41 is connected to the rear end of the enlarged diameter portion 18b of the exhaust port 18.
- a second spiral distribution passage 43 is formed between the two distribution passage forming members 41, 42.
- the upstream end of the heat transfer tube 35 of the fifth-stage heat exchanger H5 is connected to the radially inner end of the second spiral distribution passage 43.
- Both distribution passage forming members 41 and 42 include the second spiral distribution passage.
- a spiral opening 44 is formed along 43.
- the cross section of the second helical opening 4 4 has a radially outward slope on the outlet side along the slope of the enlarged diameter portion 18 b of the exhaust port 18, and a number of guide vanes 4 5 inside. ... Is attached at an angle. Therefore, the exhaust gas supplied from the enlarged diameter portion 18b of the exhaust port 18 is swirled while diffusing outward in the radial direction when passing through the spiral opening 44.
- the outer periphery of the first stage metal catalyst unit 46 A to the fourth stage metal catalyst unit 46 D and the fourth stage heat exchanger H 4 The front end of the cylindrical case 47 covering the cylindrical case 47 is connected to the distribution passage forming member 42, and the two annular distribution passages are connected to the rear end of the cylindrical case 47 in a state of being overlapped with each other.
- a fourth circular distribution passage 50 is formed between the forming members 48, 49, and an outer end of a first spiral distribution passage 51 formed by spirally bending a pipe is connected to the fourth circular distribution passage 50. Is done.
- Each of the first-stage metal catalyst device 46 A to the fourth-stage metal catalyst device 46 D arranged in series has four types of corrugated metal carriers 52 to 55 carrying a catalyst for purifying exhaust gas on the surface. It is formed in the shape of a ring having a diameter and arranged concentrically. As shown in an enlarged manner in FIG. 7, the phases of the waveforms of the metal carriers 52 to 55 of the metal catalyst devices 46 A to 46 D at the respective stages are shifted from each other by a half pitch.
- the fourth-stage heat exchanger H4 is composed of four heat transfer tubes 56 to 59 wound in a coil shape having different diameters (see Fig. 10).
- the four heat transfer tubes 56 to 59 are arranged concentrically and alternately with the four metal carriers 52 to 55 of the first-stage metal catalyst unit 46 A to the fourth-stage metal catalyst unit 46 D. It is stored in a cylindrical case 47. 4 heat transfer tubes
- the downstream ends of 56 to 59 are connected to the intermediate portion of the second spiral distribution passage 43, and the upstream ends of the four heat transfer tubes 56 to 59 are intermediate to the first spiral distribution passage 51.
- Two cylindrical cases 60 and 61 are coaxially arranged, and the third-stage heat exchange between both cylindrical cases 60 and 61
- the vessel H3 is arranged in an annular shape.
- the third-stage heat exchanger H 3 is composed of a number of heat transfer tubes 6 2... wound in one direction and a number of heat transfer tubes 6 3... wound in the other direction.
- the heat transfer tubes are arranged alternately in a state where the parts are combined, thereby increasing the arrangement density of the heat transfer tubes 62, 63, ... in the space.
- the outer circumferences of the first-stage metal catalyst unit 46 A to the fourth-stage metal catalyst unit 46 D and the fourth-stage heat exchanger H 4 are connected to the heat transfer tubes 6 3 of the third-stage heat exchanger H 3. -, Surrounded by 6 3 ...
- annular distribution passage forming member 64 fixed to the front end of the outer cylindrical case 60 and an annular distribution passage forming member 65 coupled to the front surface of the distribution passage forming member 64
- Three circular distribution passages 66 are formed.
- the upstream end of the heat transfer tubes 62, 63, ... of the third stage heat exchanger H3 is connected to the third circular distribution passage 66, and the downstream end of the heat transfer tubes 62, 63, ... 4 Connected to circular distribution passage 50.
- the first-stage metal catalyst unit 46A to the fourth-stage metal catalyst unit 46D and the fourth-stage heat exchanger H A dish-shaped end cap 6 7 covering the rear surface of 4 is fixed.
- the detachable cover 71 constituting the outer shell of the exhaust gas purifying apparatus C integrated with the evaporator is provided with a plate-shaped distribution passage forming member 72 having an exhaust hole 72 at the center thereof, which is connected to the exhaust pipe 32.
- a cylindrical case 75 located radially outward and a cylindrical case 76 located radially inward extend from the distribution passage forming member 73 at a small interval, and the outer cylindrical shape is formed.
- the flange 77 provided at the front end of the case 75 is overlapped with the flange 79 provided at the rear end of the mounting plate 78 fixed to the distribution passage forming member 42, and the cylinder head 1 Will be tightened together.
- An annular distribution passage forming member 81 is fixed to the front end of the inner cylindrical case 76, and the annular distribution passage forming member 82 is connected to the front surface of the distribution passage forming member 81 to form the second distribution passage forming member 82.
- a circular distribution passage 83 is formed.
- the first circular distribution channel 74 and the second circular distribution channel 83 are identical and face each other.
- An inner wall member 84 formed in a cup shape is housed inside the cover 71, and the first wall member 84 is disposed between the outer peripheral surface of the inner wall member 84 and the inner peripheral surface of the inner cylindrical case 76.
- Stage heat exchanger H1 is located You.
- the first-stage heat exchanger HI has a structure similar to that of the third-stage heat exchanger H3, and includes a number of heat transfer tubes 85 wound in one direction and a coil in the other direction. A large number of heat transfer tubes 86 are alternately arranged with a part of them joined together, and the outer circumference of the third-stage heat exchanger H3 is surrounded by the heat transfer tubes 85 ', 86 ... .
- the upstream ends of the heat transfer tubes 85... 86 are connected to the first circular distribution passage 74, and the downstream ends are connected to the second circular distribution passage 83.
- the heat transfer tubes 62..., 63— and the heat transfer tubes 85, 86... of the first stage heat exchanger HI are made of heat-resistant stainless steel (austenitic, for example, SUS 316L, SUS 310 S, or ferrite).
- austenitic for example, SUS 316L, SUS 310 S, or ferrite.
- SUS430, SUS444 or a nickel-based heat-resistant alloy is preferable.
- brazing or mechanical constraint is preferable for the connection of the heat transfer tubes.
- the metal carriers 52 to 55 of the first-stage metal catalyst unit 46 A to the fourth-stage metal catalyst unit 46 D are heat-resistant stainless steel (for example, 20 wt% Cr—5 wt% A 1 ferrite stainless steel). Also, a metal foil of nickel-base heat-resistant alloy (having a thickness of 0.1 mm or less) is preferable.
- a water supply port 87 for supplying water which is a source of high-pressure steam is provided in the first circular distribution passage 7, and the first circular distribution passage 74 is provided in the first stage heat exchange.
- HI communicates with the second circular distribution passage 83 via a number of heat transfer tubes 85, 86,...,
- the second circular distribution passage 83 communicates with the second stage heat exchanger H 2 through a communication passage 88. It communicates with one end of the heat transfer tube.
- the other end of the heat transfer tube 34 of the second-stage heat exchanger H2 communicates with the third circular distribution passage 66 via the communication passage 89, and the third circular distribution passage 66 is connected to the heat transfer tube 62 of the third-stage heat exchanger H3. , 63..
- the fourth circular distribution passage 50 communicates with the four heat transfer tubes 56 to 59 of the fourth stage heat exchanger H4 via the first spiral distribution passage 51.
- the four heat transfer tubes 56 to 59 of the fourth stage heat exchanger H4 are connected to the steam outlet 90 via the second spiral distribution passage 43 and the heat transfer tubes 35 of the fifth stage heat exchanger H5. Communicate.
- the water supplied from the water supply port 87 is supplied to the first-stage heat exchanger H1—the second-stage heat exchanger.
- the exhaust gas discharged from the internal combustion engine E passes through the equal-diameter portion 18a of the exhaust port 18 while being passed through the second heat-transfer tube 34 wound around the outer peripheral surface of the equal-diameter portion 18a.
- Exhaust gas flowing into the enlarged diameter portion 18b from the equal diameter portion 18a of the exhaust port 18 is formed by a third coil heat transfer tube 35 housed inside the enlarged diameter portion 18b.
- the heat exchange is performed by directly contacting the stage heat exchanger H5.
- the exhaust gas exiting the exhaust port 18 passes through the inside of the first-stage metal catalyst unit 46A to the fourth-stage metal catalyst unit 46D to purify harmful components.
- the fourth-stage metal catalyst unit 46 A to 46 D exchanges heat with the fourth-stage heat exchanger H 4 including heat transfer tubes 56 to 59 arranged concentrically.
- Exhaust gas that has passed through the first to fourth metal catalyst units 46 A to 46 D and the fourth stage heat exchanger H 4 is blocked by the end cap 67 and makes a U-turn, and a pair of cylindrical Heat is exchanged while flowing from the rear to the front through the third-stage heat exchanger H3 composed of heat transfer tubes 6 2... °
- the first-stage heat exchanger consisting of heat transfer tubes 8 5-, 86 ... arranged between the cylindrical case 76 and the inner wall member 84 by changing the direction and exchanging heat while flowing from the front to the back.
- the exhaust gas is discharged from the exhaust hole 72 a of the distribution passage forming member 72 to the exhaust pipe 32.
- the exhaust gas that has passed through the fifth-stage heat exchanger H5 diffuses radially outward when passing through the spiral opening 44 connected to the enlarged portion 18b of the exhaust port 18, and the spiral opening 4 A swirling flow is created by the guide vanes 4 5 ... mounted inside 4.
- the exhaust gas uniformly acts on the entire first to fourth stage metal catalyst devices 46 A to 46 D, and the inside of the first to fourth stage metal catalyst devices 46 A to 46 D ,
- the residence time of the exhaust gas can be lengthened to enhance the exhaust gas purification effect. Also, as shown in FIG.
- the pipe length are connected to the radially outer side of the first helical distribution passage 51 and the radially inner side of the second helical distribution passage 43, and the inner heat transfer tube having a shorter pipe length.
- the first and second spiral distributing passages 51, 43 are connected.
- the flow path lengths of the four heat transfer tubes 56 to 59, including a part of the flow path lengths, can be made as uniform as possible, and the pressure drop difference between the heat transfer tubes 56 to 59 can be reduced.
- first-stage to fourth-stage metal catalyst units 46 A to 46 D and the fourth-stage heat exchanger H 4 are integrated so that they can exchange heat with each other.
- the reaction heat generated in 46 A to 46 D can be recovered by the fourth-stage heat exchanger H 4 to increase the thermal energy recovery effect, and the flow rate of water flowing through the fourth-stage heat exchanger H 4
- the first- to fourth-stage metal catalyst devices 46 A to 46 D are heated and activated, and the first to fourth-stage metal catalyst devices 46 A to 46 A It is possible to improve the durability by cooling 46D.
- Exhaust gas that has passed through the first- to fourth-stage metal catalyst devices 46 A to 46 D and the fourth-stage heat exchanger H 4 is supplied to the first spiral distribution passage 5 composed of a spiral pipe material. It also exchanges heat when passing through 1. Since the exhaust gas flow is dispersed by the first spiral distribution passage 51, a heat spot is prevented from being generated at the end cap 67 located at the position where the exhaust gas is turned back, and severe thermal conditions are applied. It is possible to protect the end cap 67 below and prevent heat radiation from the end cap 67. Moreover, since the first spiral distribution passage 51 made of a spiral pipe material is flexible, it can absorb the difference in the amount of thermal expansion between the four heat transfer tubes 56 to 59 having different total lengths. it can.
- exhaust gas flows from the internal combustion engine E side to the exhaust pipe 32 side, while water flows from the exhaust pipe 32 side to the internal combustion engine E side, so that the exhaust gas and water have high heat exchange efficiency. It becomes the state of the cross lip.
- the first-stage heat exchanger H1—the third-stage heat exchanger H3 ⁇ the fourth-stage heat exchanger H4 ⁇ the fifth-stage heat exchanger Although it is necessary to flow water in the order of heat exchanger H5 ⁇ second-stage heat exchanger H2, in this embodiment, the first-stage heat exchanger H1—the second-stage heat exchanger H2 ⁇ Water is flowing in the order of three-stage heat exchanger H3 ⁇ fourth-stage heat exchanger H4 ⁇ fifth-stage heat exchanger H5.
- the water first passes through the first-stage heat exchanger H1 located at the most downstream in the exhaust gas flow direction, and then is supplied to the second-stage heat exchanger H2 located at the most upstream in the exhaust gas flow direction. From there, it is returned to the third stage heat exchanger H3, which is located downstream in the exhaust gas flow direction.
- the heat exchange with the fifth stage heat exchanger H5 located at the most downstream in the exhaust gas flow direction that is, the fifth stage heat exchanger H5 through which the exhaust gas whose temperature has been reduced after the end of the heat exchange flows.
- the combustion chamber 16 By supplying relatively low-temperature water that has passed only through the fifth-stage heat exchanger H5 to the second-stage heat exchanger H2 located immediately downstream of the exhaust valve 25, the combustion chamber 16 By exchanging heat with the high-temperature exhaust gas that has just come out, the exhaust port 18 and the exhaust valve 25 that are exposed to high temperatures are sufficiently cooled to increase durability, and the exhaust port 18 and By lowering the temperature of the fifth-stage heat exchanger H5, thermal leakage due to radiant heat can be reduced, and the thermal effect on devices such as a valve train which needs to maintain accuracy can be reduced.
- FIG. 12A shows the horizontal axis shows the integrated heat transfer area of the heat exchangers H1 to H5 measured from the water supply port 87, and the vertical axis shows the exhaust gas and water (steam).
- Figure 12A shows the first-stage heat exchanger HI—the third-stage heat exchanger H 3—the fourth-stage heat exchanger H4 ⁇ the fifth-stage heat exchanger H5 ⁇ the A conventional example in which water is flowed in the order of the two-stage heat exchanger H2 is shown in Fig. 12B.
- the first-stage heat exchanger HI ⁇ the second-stage heat exchanger H2-the third-stage heat exchanger H3 ⁇ the second This embodiment illustrates the flow of water in the order of the four-stage heat exchanger H4—the fifth-stage heat exchanger H5.
- the exhaust gas temperature and the water temperature increase as the integrated heat transfer area increases, that is, as the combustion chamber 16 of the internal combustion engine E approaches.
- the temperature difference ⁇ ⁇ ⁇ between the exhaust gas temperature and water in the second-stage heat exchanger H2, which is the final stage is relatively small, and the exhaust port 18 And the cooling performance of the exhaust valve 25 will be reduced.
- FIG. 12B showing the present embodiment since the temperature of the water passing through the second-stage heat exchanger H2 immediately downstream of the exhaust valve 35 is relatively low, The temperature difference ⁇ ⁇ from the exhaust gas passing therethrough becomes relatively large, and the exhaust ports 18 and the exhaust valves 25 exposed to high temperatures can be effectively cooled.
- the exhaust passage 33 is bent in a three-stage zigzag shape, and the first, third, and fourth stage heat exchangers HI, H3, and H4 are laminated in the radial direction, thermal leakage is prevented. While minimizing emissions and preventing noise from radiating from the inside, the overall size of the exhaust gas purifier C integrated with the evaporator is made as small as possible and placed compactly on the cylinder head 12 of the internal combustion engine E. be able to.
- the first, third and fourth stage heat exchangers HI, H3 and H4 and the first to fourth stage metal catalyst units 46A to 46D are laminated in the radial direction to form a maze.
- the noise reduction effect not only prevents the exhaust noise from leaking to the outside of the exhaust gas purifier C with the integrated evaporator, but also mainly reduces the heat from the first to fifth stages.
- the effects of reducing the exhaust gas temperature can be obtained by the exchangers H1 to H5.
- the exhaust muffler can be simplified or omitted, and the exhaust device itself can be reduced in size and weight.
- the temperature of the exhaust passage especially downstream of the first stage heat exchanger HI, decreases due to the decrease in the exhaust gas temperature, the degree of freedom in heat resistance design increases, and the use of a material such as plastic for the exhaust passage is required. Becomes possible.
- the evaporator of the embodiment has a total of five stages of heat exchangers HI to H5, but the present invention can be applied to a device having a total of three or more stages of heat exchangers.
- the exhaust gas purifying apparatus C integrated with the evaporator is exemplified.
- the present invention can be applied to a heat exchanger configured separately from the exhaust gas purifying apparatus.
- water is exemplified as the working medium, but a working medium other than water may be employed. It is possible.
- the waste heat recovery device for an internal combustion engine can be suitably applied to an evaporator of a Rankine cycle device of an internal combustion engine, but any device that utilizes waste heat of exhaust gas of an internal combustion engine.
- the present invention can be applied to a waste heat recovery device for any other use.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Exhaust Gas After Treatment (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP01970191A EP1321644B1 (en) | 2000-09-25 | 2001-09-21 | Waste heat recovery device of internal combustion engine |
DE60109468T DE60109468T2 (de) | 2000-09-25 | 2001-09-21 | Abwärmerückgewinnung für brennkraftmaschinen |
US10/380,999 US6823668B2 (en) | 2000-09-25 | 2001-09-21 | Waste heat recovery device of internal combustion engine |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2000295422A JP2002097946A (ja) | 2000-09-25 | 2000-09-25 | 内燃機関の廃熱回収装置 |
JP2000-295422 | 2000-09-25 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2002025077A1 true WO2002025077A1 (fr) | 2002-03-28 |
Family
ID=18777848
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2001/008258 WO2002025077A1 (fr) | 2000-09-25 | 2001-09-21 | Dispositif de recuperation de la chaleur perdue d'un moteur thermique |
Country Status (5)
Country | Link |
---|---|
US (1) | US6823668B2 (ja) |
EP (1) | EP1321644B1 (ja) |
JP (1) | JP2002097946A (ja) |
DE (1) | DE60109468T2 (ja) |
WO (1) | WO2002025077A1 (ja) |
Families Citing this family (23)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
AU9420101A (en) * | 2000-10-10 | 2002-04-22 | Honda Motor Co Ltd | Rankine cycle device of internal combustion engine |
DE60209338T2 (de) * | 2001-01-26 | 2006-08-03 | Honda Giken Kogyo K.K. | Brennkraftmaschine |
JP3802799B2 (ja) * | 2001-11-21 | 2006-07-26 | 本田技研工業株式会社 | 熱交換装置 |
US7337835B2 (en) * | 2005-01-25 | 2008-03-04 | Indian Institute Of Technology Delhi | Baffle and tube for a heat exchanger |
FR2884555A1 (fr) * | 2005-04-13 | 2006-10-20 | Peugeot Citroen Automobiles Sa | Dispositif de recuperation d'energie d'un moteur a combustion interne |
US7306029B2 (en) * | 2005-10-26 | 2007-12-11 | Westinghouse Savannah River Company Llc | Two part condenser for varying the rate of condensing and related method |
US8327654B2 (en) * | 2008-03-17 | 2012-12-11 | Denso International America, Inc. | Condenser, radiator, and fan module with Rankine cycle fan |
US20100083919A1 (en) * | 2008-10-03 | 2010-04-08 | Gm Global Technology Operations, Inc. | Internal Combustion Engine With Integrated Waste Heat Recovery System |
JP5254082B2 (ja) * | 2009-03-05 | 2013-08-07 | 株式会社ユタカ技研 | 熱交換用チューブ |
US20110061388A1 (en) * | 2009-09-15 | 2011-03-17 | General Electric Company | Direct evaporator apparatus and energy recovery system |
US8511085B2 (en) * | 2009-11-24 | 2013-08-20 | General Electric Company | Direct evaporator apparatus and energy recovery system |
US20110209473A1 (en) * | 2010-02-26 | 2011-09-01 | Jassin Fritz | System and method for waste heat recovery in exhaust gas recirculation |
US8628025B2 (en) * | 2010-03-09 | 2014-01-14 | GM Global Technology Operations LLC | Vehicle waste heat recovery system and method of operation |
DE102010046804A1 (de) | 2010-09-28 | 2012-03-29 | Voith Patent Gmbh | Rohrbündel-Wärmetauscher |
DE102011007748A1 (de) * | 2011-04-20 | 2012-10-25 | Behr Gmbh & Co. Kg | Abgaskühler zum Kühlen von Verbrennungsabgas einer Verbrennungskraftmaschine, Wassersammeladapter, Abgaskühlsystem und Verfahren zum Herstellen eines Abgaskühlsystems |
RU2587507C1 (ru) * | 2012-07-20 | 2016-06-20 | Футаба Индастриал Ко., Лтд. | Устройство рекуперации тепла отработавших газов |
EP2803843B1 (en) * | 2013-05-14 | 2018-02-14 | Bosal Emission Control Systems NV | Unit for recovering thermal energy from exhaust gas of an internal combustion engine |
WO2017178120A1 (de) * | 2016-04-14 | 2017-10-19 | Linde Aktiengesellschaft | Gewickelter wärmeübertrager |
CN106121778B (zh) * | 2016-06-28 | 2018-12-25 | 芜湖澳奔玛汽车部件有限公司 | 一种汽车发动机尾气排放处理系统 |
DE102016216430A1 (de) * | 2016-08-31 | 2018-03-01 | Hanon Systems | Abgaskühler sowie Verfahren und Montagewerkzeug zur Einbringung von Kühlrippen in einen Abgaskühler |
CN106703931A (zh) * | 2017-01-03 | 2017-05-24 | 浙江吉利控股集团有限公司 | 一种用于发动机机油的加热系统 |
CN107040168B (zh) * | 2017-05-22 | 2019-03-19 | 武汉理工大学 | 一种利用废气温差发电的热交换装置 |
CA3164688A1 (en) | 2018-05-08 | 2019-11-08 | Enginuity Power Systems, Inc. | Combination systems and related methods for providing power, heat and cooling |
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2001
- 2001-09-21 US US10/380,999 patent/US6823668B2/en not_active Expired - Fee Related
- 2001-09-21 EP EP01970191A patent/EP1321644B1/en not_active Expired - Lifetime
- 2001-09-21 DE DE60109468T patent/DE60109468T2/de not_active Expired - Fee Related
- 2001-09-21 WO PCT/JP2001/008258 patent/WO2002025077A1/ja active IP Right Grant
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Also Published As
Publication number | Publication date |
---|---|
DE60109468T2 (de) | 2005-08-04 |
JP2002097946A (ja) | 2002-04-05 |
EP1321644B1 (en) | 2005-03-16 |
EP1321644A1 (en) | 2003-06-25 |
US6823668B2 (en) | 2004-11-30 |
DE60109468D1 (de) | 2005-04-21 |
US20040025501A1 (en) | 2004-02-12 |
EP1321644A4 (en) | 2004-08-25 |
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