US20080115923A1 - Exhaust heat recovering device - Google Patents

Exhaust heat recovering device Download PDF

Info

Publication number
US20080115923A1
US20080115923A1 US11/396,987 US39698706A US2008115923A1 US 20080115923 A1 US20080115923 A1 US 20080115923A1 US 39698706 A US39698706 A US 39698706A US 2008115923 A1 US2008115923 A1 US 2008115923A1
Authority
US
United States
Prior art keywords
evaporator
condenser
cooling water
heat
waste heat
Prior art date
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.)
Abandoned
Application number
US11/396,987
Inventor
Yasutoshi Yamanaka
Shinichi Hamada
Seiji Inoue
Kimio Kohara
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Denso Corp
Original Assignee
Denso Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Denso Corp filed Critical Denso Corp
Assigned to DENSO CORPORATION reassignment DENSO CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HAMADA, SHINICHI, INOUE, SEIJI, KOHARA, KIMIO, YAMANAKA, YASUTOSHI
Publication of US20080115923A1 publication Critical patent/US20080115923A1/en
Abandoned legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
    • F02G5/02—Profiting from waste heat of exhaust gases
    • F02G5/04—Profiting from waste heat of exhaust gases in combination with other waste heat from combustion engines
    • 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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P9/00—Cooling having pertinent characteristics not provided for in, or of interest apart from, groups F01P1/00 - F01P7/00
    • F01P9/02—Cooling by evaporation, e.g. by spraying water on to cylinders
    • 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
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F28D15/0233—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes the conduits having a particular shape, e.g. non-circular cross-section, annular
    • 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
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F28D15/0275—Arrangements for coupling heat-pipes together or with other structures, e.g. with base blocks; Heat pipe cores
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/26—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means being integral with the element
    • F28F1/28—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means being integral with the element the element being built-up from finned sections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P2060/00—Cooling circuits using auxiliaries
    • F01P2060/16—Outlet manifold
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2270/00—Thermal insulation; Thermal decoupling
    • 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 system using heat pipes to recover waste heat of exhaust gas of an internal combustion engine and utilizing it for heating cooling water of the internal combustion engine, for example, is suitably used for a vehicle provided with an internal combustion engine.
  • waste heat of the exhaust gas is transported to the engine cooling water by the heat pipes, whereby the engine cooling water at the time of a low temperature is positively heated and the warmup performance of the engine and heating performance of a heater using the engine cooling water as a heat source are improved.
  • the object of the present invention in consideration of the above problem, is to provide a waste heat recovery system utilizing heat pipes which prevents condensation of the working medium at the insulating part and enables reliable heat transport from the evaporator to the condenser.
  • the present invention employs the following technical means to achieve the above object.
  • a waste heat recovery system having a heat pipe ( 110 ) provided with a heat switch function limiting an amount of heat transported to a condenser ( 110 B) in accordance with the increase in the amount of heating of the evaporator ( 110 A), having the evaporator ( 110 A) arranged at an exhaust pipe ( 11 ) for carrying exhaust gas of the internal combustion engine ( 10 ), and having the condenser ( 110 B) arranged in a cooling water passage( 30 ) for carrying cooling water of the internal combustion engine ( 10 ) and using the heat pipe ( 110 ) to transport waste heat of exhaust gas to cooling water, characterized in that an insulating part ( 110 C) formed between the evaporator ( 110 A) and condenser ( 110 B) is provided with a wall part ( 160 ) for preventing heat transmission from an external fluid.
  • the working medium inside the heat pipe ( 110 ) evaporated at the evaporator ( 110 A) can be prevented from condensing at the insulating part ( 110 C), so reliable heat transport from the evaporator ( 110 A) to the condenser ( 110 B) becomes possible.
  • the wall part ( 160 ) is provided at the upstream side of the flow of the external fluid of the insulating part ( 110 C).
  • the flow of the external fluid is blocked by the wall part ( 160 ) and is prevented from striking the insulating part ( 110 C), so by setting the minimum extent of the wall part ( 160 ), the working medium can be prevented from condensing at the insulating part ( 110 C).
  • wall parts ( 160 ) are connected to the evaporator ( 110 A) and condenser ( 110 B) and are separated by a predetermined amount of clearance ( 161 ) formed between the evaporator ( 110 A) and the condenser ( 110 B), and the separated wall parts ( 160 ) are connected by an elastic part ( 162 ) having elasticity.
  • a plurality of heat pipes ( 110 ) are provided, and first end sides of the plurality of heat pipes ( 110 ) are provided with a connector ( 140 ) connecting the plurality of heat pipes ( 110 ) together.
  • the evaporator ( 110 A) is arranged under the condenser ( 110 B), and the connector ( 140 ) is provided at the evaporator ( 110 A) end side and arranged at the outer surface or inside of the exhaust pipe ( 11 ).
  • the working medium in the connector ( 140 ) is also heated positively by the exhaust gas, so dry out for activation of the heat switch function (cessation of waste heat recovery) can be performed earlier.
  • each heat pipe ( 110 ) is provided with a wick extending from the evaporator ( 110 A) to the condenser ( 110 B), and the evaporator ( 110 A) is arranged above the condenser ( 110 B).
  • an exhaust pipe part ( 130 A) forming part of the exhaust pipe ( 11 ) and a cooling water passage part ( 150 A) forming part of the cooling water passage ( 30 ) are provided, the exhaust pipe part ( 130 A) is joined with the evaporator ( 110 A), and the cooling water passage part ( 150 A) is joined with the condenser ( 110 B).
  • FIG. 1 is a schematic view showing the state of the waste heat recovery system mounted in a vehicle.
  • FIG. 2A is a front view of a waste heat recovery system in a first embodiment
  • FIG. 2B is a right side view of the same.
  • FIG. 3 is a graph showing the amount of heat transferred to engine cooling water according to a waste heat recovery system.
  • FIG. 4A is a front view of a waste heat recovery system in a second embodiment
  • FIG. 4B is a right side view of the same.
  • FIG. 5A is a front view of a waste heat recovery system in a third embodiment
  • FIG. 5B is a right side view of the same.
  • FIG. 6A is a front view of a waste heat recovery system in a first mode of a fourth embodiment
  • FIG. 6B is a right side view of the same.
  • FIG. 7A is a front view of a waste heat recovery system in a second mode of a fourth embodiment
  • FIG. 7B is a right side view of the same.
  • FIG. 8A is a front view of a waste heat recovery system in a third mode of a fourth embodiment
  • FIG. 7B is a right side view of the same.
  • FIG. 1 is a schematic view showing the state of the waste heat recovery system 100 mounted in a vehicle
  • FIG. 2A is a front view showing the waste heat recovery system 100
  • FIG. 2B is a right side view of FIG. 2A
  • FIG. 3 is a graph showing the amount of heat transferred to the engine cooling water by the waste heat recovery system 100 .
  • a vehicle engine 10 is a water-cooled internal combustion engine which has an exhaust pipe 11 from which exhaust gas is exhausted after fuel is burned.
  • the exhaust pipe 11 is provided with a catalytic converter 12 for purifying the exhaust gas.
  • the engine 10 has a radiator circuit 20 by which the engine 10 is cooled by circulation of engine cooling water (hereinafter, “cooling water”) and a heater circuit 30 for heating air-conditioning air using the cooling water (warm water) as a heat source.
  • cooling water engine cooling water
  • heater circuit 30 for heating air-conditioning air using the cooling water (warm water) as a heat source.
  • the radiator circuit 20 is provided with a radiator 21 .
  • the radiator 21 is cooled by heat exchange of the cooling water circulated by a water pump 22 with the outside air.
  • the radiator circuit 20 is provided inside it with a bypass passage (not shown) through which cooling water circulates bypassing the radiator 21 and is designed so that a thermostat (not shown) adjusts the amount of cooling water circulated through the radiator 21 and the amount of cooling water circulating through the bypass passage. In particular, at the time of engine warmup, the amount of cooling water at the bypass passage side is increased and warmup is promoted (that is, overcooling of the cooling water by the radiator 21 is prevented).
  • the heater circuit (corresponding to the cooling water passage in the present invention) 30 is provided with a heater core 31 as a heating use heat exchanger and is designed so that cooling water (warm water) is circulated by the water pump 22 .
  • the heater core 31 is placed in an air-conditioning case of a not shown air-conditioning unit. The air-conditioning air sent in accordance with the blower is heated by heat exchange with warm water.
  • the waste heat recovery system 100 has a plurality of tubes 110 .
  • One end side of each tube 110 is arranged inside the exhaust pipe part 130 A, while the other end side is arranged inside the cooling water passage part 150 A (water tank 150 ).
  • the constituent members (explained below) are made of a stainless steel material provided with a high corrosion resistance. After the constituent members are assembled, they are soldered together by solder material provided at the abutting parts and engaging parts. Further, the exhaust pipe part 130 A is interposed in the exhaust pipe 11 at the part forming the downstream side of the catalytic converter 12 . Cooling water in the heater circuit 30 is circulated in the cooling water passage part 150 A.
  • FIGS. 2A and 2B will be used to explain details of the waste heat recovery system 100 .
  • the tubes 110 are evacuated to a vacuum, then a working medium is sealed in them in predetermined amounts so that the tubes act as heat pipes. They are used in a posture with their longitudinal directions in the vertical direction.
  • the bottom side forms the evaporator 110 A
  • the top side forms the condenser 110 B
  • the section between the two 110 A and 110 B forms the insulating part 110 C (bottom heat type).
  • the inside walls of the tubes 110 corresponding to the condenser 110 B are provided with wicks (porous substances) comprised of metal mesh, metal felt, sintered metal, etc. (not shown).
  • the tubes 110 are formed into flat shapes by combining two tube plates 111 , 112 facing each other. A plurality of (here, four) these are stacked along the left-right direction in FIG. 2A . These tubes 110 are blocked at their top ends and are opened at their bottom ends. Further, the tubes 110 are arranged so that a plurality of columns (for example, three columns) in the left-right direction in FIG. 2B (not shown).
  • the sections between the stacked tubes 110 and the outsides of the outermost tubes 110 are provided with corrugated type fins 120 formed into clamp sectional shapes from a thin sheet material.
  • the bottom ends (openings) of the tubes 110 are formed into square outer shapes and are joined to a first plate 131 formed with tube holes at positions corresponding to the tubes 110 . Further, the tubes 110 are passed through tube holes of a second plate 132 similar to the first plate 131 , while the second plate 132 is arranged at a position forming the top ends of the fins 120 and is joined with the tubes 110 . Further, like the second plate 132 , a third plate 133 is arranged at a boundary position between the condenser 110 B and the insulating part 110 C and is joined to the tubes 110 .
  • the two outermost fins 120 in the stacking direction of the tubes 110 are provided with side plates 134 forming square outside shapes.
  • the side plates 134 are joined to the fins 120 .
  • the bottom ends and the top ends of the side plates 134 are joined to the first plate 131 and second plate 132 .
  • the first plate 131 , second plate 132 , and two side plates 134 form a duct having a square passage cross-section.
  • This duct forms the exhaust pipe part 130 A. Therefore, the evaporator 110 A and fins 120 are arranged inside the exhaust pipe part 130 A.
  • the two openings of the exhaust pipe part 130 A have an inlet side attachment 135 and an outlet side attachment 136 joined with them.
  • the two attachments 135 , 136 form the same shapes.
  • the attachment 135 is a square frame having an opening 135 a the same as the opening of the exhaust pipe part 130 A.
  • the four corners are provided with attachment holes 135 b for attachment to the exhaust pipe 11 .
  • the bottom surface of the first plate 131 (bottom surface of exhaust pipe part 130 A) is joined to a shallow-bottom tank (corresponding to the connector the present invention) 140 opening at the first plate 131 side.
  • the tubes 110 are connected together by this tank 140 .
  • a sealing pipe 141 connected to the inside of the tank 140 is provided.
  • the tubes 110 are evacuated to a vacuum from the sealing pipe 141 , then a working medium is sealed in them, then the sealing pipe 141 is sealed.
  • the working medium used here is water. Water has a boiling point of usually (at one atmosphere) 100° C., but since the tubes 110 are evacuated, the boiling point becomes 30 to 40° C. Further, the working medium used may also be, in addition to water, alcohol, a fluorocarbon, chlorofluorocarbon, etc.
  • the top surface of the third plate 133 is joined with a water tank 150 of a flat box shape opening to the third plate 133 side.
  • the water tank 150 is provided with, at the left side face in FIG. 2A , an inlet pipe 151 and, further, is provided with, at the facing right side face, with an outlet pipe 152 .
  • the pipes 151 , 152 are connected to the inside of the water tank 150 .
  • the third plate 133 , water tank 150 , and two pipes 151 , 152 form the cooling water passage part 150 A.
  • the condenser 110 B is arranged inside the cooling water passage 150 A.
  • insulating wall parts 160 are provided for preventing the cooling air flowing through the region in the vehicle where the waste heat recovery system 100 is arranged (corresponding to the external fluid in the present invention) from striking the insulating part 110 C.
  • the cooling air flows from the left to right direction in FIG. 2A .
  • the insulating wall parts 160 are provided at the left and right sides in FIG. 2A .
  • the insulating wall parts 160 are plate-shaped members with bottom ends joined to the second plate 132 (evaporator 110 A) and with top ends joined to the third plate (condenser 110 B) 133 .
  • the insulating wall parts 160 are separated by formation of a predetermined amount of a notch (corresponding to the clearance in the present invention) 161 between the evaporator 110 A and condenser 110 B.
  • the separated wall parts 160 are connected by a curved part (corresponding to elastic part in the present invention) 162 formed curved and having elasticity as a plate spring.
  • the exhaust pipe part 130 A is interposed in the exhaust pipe 11 at the part forming the downstream side of the catalytic converter 12 and is fixed there by the two attachments 135 , 136 . Further, the inlet pipe 151 and outlet pipe 152 of the cooling water passage part 150 A are connected to the heater circuit 30 .
  • the exhaust pipe part 130 A forms part of the exhaust pipe 11
  • the cooling water passage part 150 A forms part of the heater circuit 30 .
  • the water pump 22 is operated and cooling water circulates through the radiator circuit 20 and heater circuit 30 .
  • the cooling water circulating through the heater circuit 30 flows through the cooling water passage part 150 A of the waste heat recovery system 100 .
  • the exhaust gas of the fuel burned in the engine 10 passes through the catalytic converter 12 and from the exhaust pipe 11 through the exhaust pipe part 130 A of the waste heat recovery system 100 to be discharged into the air.
  • the water (working medium) in the tubes 110 receives heat from the exhaust gas flowing through the exhaust pipe part 130 A at the tank 140 and evaporator 110 A and boils and vaporizes to form steam which rises inside the tubes 110 and flows into the condenser 110 B.
  • the steam flowing into the condenser 110 B is cooled by the cooling water flowing through the cooling water passage part 150 A and becomes condensed water at the wicks provided at their inside walls. This descends by gravity and returns to the evaporator 110 A.
  • the heat of the exhaust gas is transmitted to the water and is transported from the evaporator 110 A to the condenser 110 B.
  • the heat is discharged as the latent heat of condensation, whereby the cooling water flowing through the cooling water passage part is heated.
  • there is also part of the heat of the exhaust gas which is moved through the walls of the tubes 110 by heat conduction from the evaporator 110 A to the condenser 110 B.
  • the amount of heat transported from the evaporator 110 A to the condenser 110 B increases until a predetermined load (heat transfer amount switching point) (waste heat recovery by heat pipes ON).
  • the waste heat recovery by the heat pipes is turned ON, the cooling water is positively heated, and the warmup of the engine 10 is promoted, so the friction loss of the engine 10 is reduced, the increase in fuel for improving the low temperature starting ability is suppressed, and the fuel economy performance is improved. Further, the heating performance of the heater core 31 using the cooling water as a heat source is improved.
  • the inventors confirmed this in actual cars during which they obtained a 3 to 5% effect for the fuel economy performance in a 1.5 liter class gasoline car, 40 km/h, and an outside air temperature of 0 to 25° C. and, further, an effect of +5 to 8° C. for the inlet water temperature of the heater core 31 .
  • the insulating part 110 C of the tubes 110 is provided with insulating wall parts 160 , so even when for example the temperature of the cooling air striking the insulating part 110 C is lower than the cooling water temperature like in a cold region, the cooling air is prevented from striking the insulating part 110 C, so the steam evaporated at the evaporator 110 A can be prevented from condensing at the insulating part 110 C and reliable heat transport from the evaporator 110 A to the condenser 110 B becomes possible.
  • the insulating wall parts 160 are separated by the notch 161 , and the separated wall parts 160 are connected by a curved part 162 having elasticity, so the heat strain occurring at the insulating wall parts 160 due to the temperature difference between the evaporator 110 A and the condenser 110 B can be absorbed by the notch 161 and the curved part 162 . Further, while the insulating wall parts 160 are separated, since they are joined by the curved part 162 , the assembly efficiency will not fall. Further, when the amount of heat transported to the condenser 110 B due to the heat switch function increases, the heat conduction from the evaporator 110 A is blocked by the notch 161 , so the restriction of the heat transport will not be impaired.
  • a tank 140 connecting a plurality of tubes 110 is provided, by providing just one location of the connector 140 with a sealing pipe 141 , it becomes possible to evacuate the inside to a vacuum and seal in a working medium.
  • the evaporator 110 A is arranged under the condenser 110 B and the tank 140 is provided at the evaporator 110 A side end and arranged so as to contact the exhaust pipe part 130 A (first plate 131 ), the working medium in the tank 140 is also positively heated by the exhaust gas and the dry out for activating the heat switch function (turning waste heat recovery OFF) is performed early.
  • the exhaust pipe part 130 A forming part of the exhaust pipe 11 and the cooling water passage part 150 A forming part of the heater circuit 30 are joined integrally with the evaporator 110 A and condenser 110 B to form the waste heat recovery system 100 , it is possible to easily attach the exhaust pipe 11 and heater circuit 30 as a single heat exchanger.
  • FIGS. 4A and 4B A second embodiment of the present invention is shown in FIGS. 4A and 4B .
  • the second embodiment comprises the first embodiment where the tubes 110 and fins 120 are changed to the tubes 110 a and fins 120 a.
  • the tubes 110 a are flat type tubes 110 comprised of two tube plates 111 , 112 combined to form round tube types. Further, the fins 120 a are comprised of the corrugated type fins 120 provided with tube burring holes and are formed as plate types through which the tubes 110 a are inserted. Further, in the condenser 110 B, to improve the heat transmission with the cooling water side, plate type water side fins 120 b are attached. Due to this, similar effects to the first embodiment can be obtained.
  • FIGS. 5A and 5B A third embodiment of the present invention is shown in FIGS. 5A and 5B .
  • the third embodiment is comprised of the first embodiment eliminating the tubes 110 , water tank 150 , and insulating wall parts 160 and stacking plate type fins 120 c to form tubes 110 b , a water tank 150 a , and insulating wall parts 160 a.
  • the fins 120 c are provided with pluralities of holes having burring parts 121 . By stacking the fins 120 c , the burring parts 121 are successively connected whereby tubes 110 b corresponding to round tubes are formed.
  • the outer circumferences of the fins 120 c corresponding to the condenser 110 B are provided with raised edges 122 .
  • the raised edges 122 are successively connected and a water tank 150 a corresponding to a box shaped vessel is formed.
  • the pluralities of burring parts 121 of the fins 120 c corresponding to the condenser 110 B are provided with water holes so as to enable cooling water to circulate across the entire water tank 150 a.
  • the ends of the fins 120 c corresponding to the insulating parts 110 C are provided with bent parts 123 .
  • the bent parts 123 are successively aligned, whereby insulating wall parts 160 a corresponding to the plurality of separated plate-shaped members are formed.
  • FIG. 6A to FIG. 8B Fourth embodiments of the present invention are shown in FIG. 6A to FIG. 8B .
  • the fourth embodiments are comprised of the above first to third embodiments where the evaporators 110 A of the tubes 110 , 110 a , and 110 b are arranged above the condensers 110 B to form top heat types.
  • the waste heat recovery systems 100 shown in FIGS. 6A and 6B , FIGS. 7A and 7B , and FIGS. 8A and 8B appearance wise, are comprised of the waste heat recovery systems 100 explained in FIGS. 2A and 2B , FIGS. 4A and 4B , and FIGS. 5A and 5B inverted vertically and with the inside walls of the tubes 110 , 110 a , and 110 b provided with wicks extending from the condensers 110 B to the evaporators 110 A.
  • insulating wall parts 160 at two locations at the upstream side and downstream side of the cooling air flow, but the invention is not limited to this. It is also possible to provide a wall part at only one location at the upstream side of the cooling air flow. Due to this, the flow of the cooling air is effectively blocked by the insulating wall part 160 and can be prevented from striking the insulating part 110 C, so by setting the minimum extent of an insulating wall part 160 , condensation of the working medium at the insulating part 110 C can be prevented. Further, conversely, insulating wall parts 160 may also be provided at all of the circumference of the insulating part 110 C (four locations).

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Geometry (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

A waste heat recovery system having a heat pipe provided with a heat switch function limiting an amount of heat transported to a condenser in accordance with the increase in the amount of heating of the evaporator, having the evaporator arranged at an exhaust pipe for carrying exhaust gas of the internal combustion engine, and having the condenser arranged in a cooling water passage for carrying cooling water of the internal combustion engine and using the heat pipe to transport waste heat of exhaust gas to cooling water, characterized in that an insulating part formed between the evaporator and condenser is provided with a wall part for preventing heat transmission from an external fluid.

Description

    TECHNICAL FIELD
  • The present invention relates to a waste heat recovery system using heat pipes to recover waste heat of exhaust gas of an internal combustion engine and utilizing it for heating cooling water of the internal combustion engine, for example, is suitably used for a vehicle provided with an internal combustion engine.
    • BACKGROUND ART
  • As a conventional waste heat recovery system, for example, as shown in the reference (Wolf Dietrich Munzel, Daimler-Benz AG, “Heat Pipes for Recovery from Exhaust Gas of a Diesel Engine in a Passenger Car”, Proc. of International Heat Pipe Conference in Grenouble, France, 1987, pp. 740-743), one is known where the evaporator among the evaporator and condenser of the heat pump is placed in an engine exhaust pipe and the condenser is brought into heat contact with the engine cooling water. In this waste heat recovery system, waste heat of the exhaust gas is transported to the engine cooling water by the heat pipes, whereby the engine cooling water at the time of a low temperature is positively heated and the warmup performance of the engine and heating performance of a heater using the engine cooling water as a heat source are improved.
  • Here, it is described that by limiting (reducing) the amount of working medium sealed in the heat pipes, even if the engine speed rises (amount of exhaust heat increases), the evaporator will dry out and the transport of heat will be able to be suppressed.
  • However, in this waste heat recovery system, no consideration is particularly seen regarding the heat of the insulating part formed between the evaporator and condenser. For example, if the insulating part is struck by cooling air or another low temperature fluid, the working medium evaporated at the evaporator will end up being condensed at this insulating part and the waste heat of the exhaust gas will no longer be able to be transported to the condenser.
    • DISCLOSURE OF THE INVENTION
  • The object of the present invention, in consideration of the above problem, is to provide a waste heat recovery system utilizing heat pipes which prevents condensation of the working medium at the insulating part and enables reliable heat transport from the evaporator to the condenser.
  • The present invention employs the following technical means to achieve the above object.
  • In a first aspect of the present invention, there is provided a waste heat recovery system having a heat pipe (110) provided with a heat switch function limiting an amount of heat transported to a condenser (110B) in accordance with the increase in the amount of heating of the evaporator (110A), having the evaporator (110A) arranged at an exhaust pipe (11) for carrying exhaust gas of the internal combustion engine (10), and having the condenser (110B) arranged in a cooling water passage(30) for carrying cooling water of the internal combustion engine (10) and using the heat pipe (110) to transport waste heat of exhaust gas to cooling water, characterized in that an insulating part (110C) formed between the evaporator (110A) and condenser (110B) is provided with a wall part (160) for preventing heat transmission from an external fluid.
  • Due to this, even if the external fluid has a temperature lower than the cooling water temperature, the working medium inside the heat pipe (110) evaporated at the evaporator (110A) can be prevented from condensing at the insulating part (110C), so reliable heat transport from the evaporator (110A) to the condenser (110B) becomes possible.
  • In a second aspect of the present invention, the wall part (160) is provided at the upstream side of the flow of the external fluid of the insulating part (110C).
  • Due to this, the flow of the external fluid is blocked by the wall part (160) and is prevented from striking the insulating part (110C), so by setting the minimum extent of the wall part (160), the working medium can be prevented from condensing at the insulating part (110C).
  • In a third aspect of the present invention, wall parts (160) are connected to the evaporator (110A) and condenser (110B) and are separated by a predetermined amount of clearance (161) formed between the evaporator (110A) and the condenser (110B), and the separated wall parts (160) are connected by an elastic part (162) having elasticity.
  • Due to this, the heat strain at the wall parts (160) caused by the temperature difference between the evaporator (110A) and condenser (110B) can be absorbed by the clearance (161) and elastic part (162). Further, while the wall parts (160) are separated, since they are joined by the elastic part (162), the assembly efficiency will not fall.
  • Further, when the amount of heat transported to the condenser (110B) due to the heat switch function increases, the heat conduction from the evaporator (110A) is blocked by the clearance (161), so the restriction of the heat transport will not be impaired.
  • In a fourth aspect of the present invention, a plurality of heat pipes (110) are provided, and first end sides of the plurality of heat pipes (110) are provided with a connector (140) connecting the plurality of heat pipes (110) together.
  • Due to this, by providing just one location of the connector (140) with a seal (141), it becomes possible to evacuate the inside to a vacuum and seal in a working medium.
  • In a fifth aspect of the present invention, the evaporator (110A) is arranged under the condenser (110B), and the connector (140) is provided at the evaporator (110A) end side and arranged at the outer surface or inside of the exhaust pipe (11).
  • Due to this, the working medium in the connector (140) is also heated positively by the exhaust gas, so dry out for activation of the heat switch function (cessation of waste heat recovery) can be performed earlier.
  • In a sixth aspect of the present invention, the inside wall of each heat pipe (110) is provided with a wick extending from the evaporator (110A) to the condenser (110B), and the evaporator (110A) is arranged above the condenser (110B).
  • Due to this, even if the evaporator (110A) is arranged above the condenser (110B) in accordance with the set positions of the exhaust pipe (11) and cooling water passage (30), heat transport between the two (110A, 110B) becomes possible.
  • In a seventh aspect of the present invention, an exhaust pipe part (130A) forming part of the exhaust pipe (11) and a cooling water passage part (150A) forming part of the cooling water passage (30) are provided, the exhaust pipe part (130A) is joined with the evaporator (110A), and the cooling water passage part (150A) is joined with the condenser (110B).
  • Due to this, it is possible to provide a waste heat recovery system (100) enabling the exhaust pipe (11) and cooling water passage (30) to be easily joined as a single heat exchanger.
  • Further, the reference numerals in parentheses of the means show the correspondence with the specific means described in the later explained embodiments.
  • Below, the present invention will be more readily understood from the attached drawings and the description of the preferred embodiments of the present invention.
    • BRIEF DESCRIPTION OF THE DRAWINGS
  • FIG. 1 is a schematic view showing the state of the waste heat recovery system mounted in a vehicle.
  • FIG. 2A is a front view of a waste heat recovery system in a first embodiment, and FIG. 2B is a right side view of the same.
  • FIG. 3 is a graph showing the amount of heat transferred to engine cooling water according to a waste heat recovery system.
  • FIG. 4A is a front view of a waste heat recovery system in a second embodiment, and FIG. 4B is a right side view of the same.
  • FIG. 5A is a front view of a waste heat recovery system in a third embodiment, and FIG. 5B is a right side view of the same.
  • FIG. 6A is a front view of a waste heat recovery system in a first mode of a fourth embodiment, and FIG. 6B is a right side view of the same.
  • FIG. 7A is a front view of a waste heat recovery system in a second mode of a fourth embodiment, and FIG. 7B is a right side view of the same.
  • FIG. 8A is a front view of a waste heat recovery system in a third mode of a fourth embodiment, and FIG. 7B is a right side view of the same.
    •  BEST MODE FOR CARRYING OUT THE INVENTION
  • A first embodiment of the present invention is shown in FIG. 1 to FIG. 3. First, the specific configuration will be explained. A waste heat recovery system 100 of the present embodiment is applied to a vehicle (automobile) having an engine 10 as a drive source for running. In this connection, FIG. 1 is a schematic view showing the state of the waste heat recovery system 100 mounted in a vehicle, FIG. 2A is a front view showing the waste heat recovery system 100, FIG. 2B is a right side view of FIG. 2A, and FIG. 3 is a graph showing the amount of heat transferred to the engine cooling water by the waste heat recovery system 100.
  • As shown in FIG. 1, a vehicle engine 10 is a water-cooled internal combustion engine which has an exhaust pipe 11 from which exhaust gas is exhausted after fuel is burned. The exhaust pipe 11 is provided with a catalytic converter 12 for purifying the exhaust gas.
  • Further, the engine 10 has a radiator circuit 20 by which the engine 10 is cooled by circulation of engine cooling water (hereinafter, “cooling water”) and a heater circuit 30 for heating air-conditioning air using the cooling water (warm water) as a heat source.
  • The radiator circuit 20 is provided with a radiator 21. The radiator 21 is cooled by heat exchange of the cooling water circulated by a water pump 22 with the outside air. Further, the radiator circuit 20 is provided inside it with a bypass passage (not shown) through which cooling water circulates bypassing the radiator 21 and is designed so that a thermostat (not shown) adjusts the amount of cooling water circulated through the radiator 21 and the amount of cooling water circulating through the bypass passage. In particular, at the time of engine warmup, the amount of cooling water at the bypass passage side is increased and warmup is promoted (that is, overcooling of the cooling water by the radiator 21 is prevented).
  • The heater circuit (corresponding to the cooling water passage in the present invention) 30 is provided with a heater core 31 as a heating use heat exchanger and is designed so that cooling water (warm water) is circulated by the water pump 22. The heater core 31 is placed in an air-conditioning case of a not shown air-conditioning unit. The air-conditioning air sent in accordance with the blower is heated by heat exchange with warm water.
  • The waste heat recovery system 100 has a plurality of tubes 110. One end side of each tube 110 is arranged inside the exhaust pipe part 130A, while the other end side is arranged inside the cooling water passage part 150A (water tank 150). The constituent members (explained below) are made of a stainless steel material provided with a high corrosion resistance. After the constituent members are assembled, they are soldered together by solder material provided at the abutting parts and engaging parts. Further, the exhaust pipe part 130A is interposed in the exhaust pipe 11 at the part forming the downstream side of the catalytic converter 12. Cooling water in the heater circuit 30 is circulated in the cooling water passage part 150A.
  • Below, FIGS. 2A and 2B will be used to explain details of the waste heat recovery system 100. The tubes 110, as explained later, are evacuated to a vacuum, then a working medium is sealed in them in predetermined amounts so that the tubes act as heat pipes. They are used in a posture with their longitudinal directions in the vertical direction. The bottom side forms the evaporator 110A, the top side forms the condenser 110B, and the section between the two 110A and 110B forms the insulating part 110C (bottom heat type). Further, the inside walls of the tubes 110 corresponding to the condenser 110B are provided with wicks (porous substances) comprised of metal mesh, metal felt, sintered metal, etc. (not shown).
  • Here, the tubes 110 are formed into flat shapes by combining two tube plates 111, 112 facing each other. A plurality of (here, four) these are stacked along the left-right direction in FIG. 2A. These tubes 110 are blocked at their top ends and are opened at their bottom ends. Further, the tubes 110 are arranged so that a plurality of columns (for example, three columns) in the left-right direction in FIG. 2B (not shown).
  • In the evaporator 110A (region from the bottom ends of the tubes 110 toward the top sides to a position over the center), the sections between the stacked tubes 110 and the outsides of the outermost tubes 110 are provided with corrugated type fins 120 formed into clamp sectional shapes from a thin sheet material.
  • The bottom ends (openings) of the tubes 110 are formed into square outer shapes and are joined to a first plate 131 formed with tube holes at positions corresponding to the tubes 110. Further, the tubes 110 are passed through tube holes of a second plate 132 similar to the first plate 131, while the second plate 132 is arranged at a position forming the top ends of the fins 120 and is joined with the tubes 110. Further, like the second plate 132, a third plate 133 is arranged at a boundary position between the condenser 110B and the insulating part 110C and is joined to the tubes 110.
  • The two outermost fins 120 in the stacking direction of the tubes 110 (fins 120 at left and right sides in FIG. 2A) are provided with side plates 134 forming square outside shapes. The side plates 134 are joined to the fins 120. The bottom ends and the top ends of the side plates 134 are joined to the first plate 131 and second plate 132.
  • The first plate 131, second plate 132, and two side plates 134 form a duct having a square passage cross-section. This duct forms the exhaust pipe part 130A. Therefore, the evaporator 110A and fins 120 are arranged inside the exhaust pipe part 130A. Further, the two openings of the exhaust pipe part 130A have an inlet side attachment 135 and an outlet side attachment 136 joined with them. The two attachments 135, 136 form the same shapes. The attachment 135 is a square frame having an opening 135 a the same as the opening of the exhaust pipe part 130A. The four corners are provided with attachment holes 135 b for attachment to the exhaust pipe 11.
  • The bottom surface of the first plate 131 (bottom surface of exhaust pipe part 130A) is joined to a shallow-bottom tank (corresponding to the connector the present invention) 140 opening at the first plate 131 side. The tubes 110 are connected together by this tank 140. At the center of the tank 140, a sealing pipe 141 connected to the inside of the tank 140 is provided.
  • Further, the tubes 110 are evacuated to a vacuum from the sealing pipe 141, then a working medium is sealed in them, then the sealing pipe 141 is sealed. The working medium used here is water. Water has a boiling point of usually (at one atmosphere) 100° C., but since the tubes 110 are evacuated, the boiling point becomes 30 to 40° C. Further, the working medium used may also be, in addition to water, alcohol, a fluorocarbon, chlorofluorocarbon, etc.
  • The top surface of the third plate 133 is joined with a water tank 150 of a flat box shape opening to the third plate 133 side. The water tank 150 is provided with, at the left side face in FIG. 2A, an inlet pipe 151 and, further, is provided with, at the facing right side face, with an outlet pipe 152. The pipes 151, 152 are connected to the inside of the water tank 150. The third plate 133, water tank 150, and two pipes 151, 152 form the cooling water passage part 150A. The condenser 110B is arranged inside the cooling water passage 150A.
  • Outside of the insulating part 110C, insulating wall parts 160 are provided for preventing the cooling air flowing through the region in the vehicle where the waste heat recovery system 100 is arranged (corresponding to the external fluid in the present invention) from striking the insulating part 110C. Here, the cooling air flows from the left to right direction in FIG. 2A. The insulating wall parts 160 are provided at the left and right sides in FIG. 2A. The insulating wall parts 160 are plate-shaped members with bottom ends joined to the second plate 132 (evaporator 110A) and with top ends joined to the third plate (condenser 110B) 133. Further, the insulating wall parts 160 are separated by formation of a predetermined amount of a notch (corresponding to the clearance in the present invention) 161 between the evaporator 110A and condenser 110B. The separated wall parts 160 are connected by a curved part (corresponding to elastic part in the present invention) 162 formed curved and having elasticity as a plate spring.
  • In the thus configured waste heat recovery system 100, the exhaust pipe part 130A is interposed in the exhaust pipe 11 at the part forming the downstream side of the catalytic converter 12 and is fixed there by the two attachments 135, 136. Further, the inlet pipe 151 and outlet pipe 152 of the cooling water passage part 150A are connected to the heater circuit 30. The exhaust pipe part 130A forms part of the exhaust pipe 11, while the cooling water passage part 150A forms part of the heater circuit 30.
  • Next, the operation based on the above configuration will be explained. When the engine 10 is operated, the water pump 22 is operated and cooling water circulates through the radiator circuit 20 and heater circuit 30. The cooling water circulating through the heater circuit 30 flows through the cooling water passage part 150A of the waste heat recovery system 100. Further, the exhaust gas of the fuel burned in the engine 10 passes through the catalytic converter 12 and from the exhaust pipe 11 through the exhaust pipe part 130A of the waste heat recovery system 100 to be discharged into the air.
  • In the waste heat recovery system 100, the water (working medium) in the tubes 110 receives heat from the exhaust gas flowing through the exhaust pipe part 130A at the tank 140 and evaporator 110A and boils and vaporizes to form steam which rises inside the tubes 110 and flows into the condenser 110B. The steam flowing into the condenser 110B is cooled by the cooling water flowing through the cooling water passage part 150A and becomes condensed water at the wicks provided at their inside walls. This descends by gravity and returns to the evaporator 110A.
  • In this way, the heat of the exhaust gas is transmitted to the water and is transported from the evaporator 110A to the condenser 110B. When the steam condenses at this condenser 110B, the heat is discharged as the latent heat of condensation, whereby the cooling water flowing through the cooling water passage part is heated. Further, there is also part of the heat of the exhaust gas which is moved through the walls of the tubes 110 by heat conduction from the evaporator 110A to the condenser 110B.
  • Further, as shown in FIG. 3, along with the amount of exhaust heat, which increases in accordance with the load of the engine 10, the amount of heat transported from the evaporator 110A to the condenser 110B, that is, the amount of heat transfer to the cooling water, increases until a predetermined load (heat transfer amount switching point) (waste heat recovery by heat pipes ON).
  • In this way, when the engine 10 is started when the outside air temperature is relatively low, the waste heat recovery by the heat pipes is turned ON, the cooling water is positively heated, and the warmup of the engine 10 is promoted, so the friction loss of the engine 10 is reduced, the increase in fuel for improving the low temperature starting ability is suppressed, and the fuel economy performance is improved. Further, the heating performance of the heater core 31 using the cooling water as a heat source is improved.
  • On the other hand, when the engine 10 increases in load to a predetermined load and the amount of exhaust heat further increases, evaporation of the water in the evaporator 110A is promoted and the flow rate of the steam toward the condenser 110B side (toward the top) increases. Further, due to the flow rate of the steam at this time, the condensed water condensed at the condenser 110B is inhibited from descending and the condensed water remains held by the wicks. This being the case, the water of the evaporator 110A completely evaporates (dries out), the heat transport by the evaporation and condensation of water is stopped, and the amount of heat transmitted to the cooling water side becomes only the heat conduction through the tubes 110 (waste heat recovery by heat pipes OFF). Further, the switching ON and OFF of the waste heat recovery by the heat pipes corresponds to the heat switch function.
  • Therefore, if continuing the waste heat recovery while the amount of exhaust heat is increasing along with the increase in load of the engine 10, the cooling water temperature rises too much, the heat radiation ability of the radiator 21 (for example, 4 kW) is exceeded, and overheating results. By switching to waste heat recovery OFF at this time, this inconvenience is prevented.
  • Further, the inventors confirmed this in actual cars during which they obtained a 3 to 5% effect for the fuel economy performance in a 1.5 liter class gasoline car, 40 km/h, and an outside air temperature of 0 to 25° C. and, further, an effect of +5 to 8° C. for the inlet water temperature of the heater core 31.
  • Here, in this embodiment, the insulating part 110C of the tubes 110 is provided with insulating wall parts 160, so even when for example the temperature of the cooling air striking the insulating part 110C is lower than the cooling water temperature like in a cold region, the cooling air is prevented from striking the insulating part 110C, so the steam evaporated at the evaporator 110A can be prevented from condensing at the insulating part 110C and reliable heat transport from the evaporator 110A to the condenser 110B becomes possible.
  • Further, the insulating wall parts 160 are separated by the notch 161, and the separated wall parts 160 are connected by a curved part 162 having elasticity, so the heat strain occurring at the insulating wall parts 160 due to the temperature difference between the evaporator 110A and the condenser 110B can be absorbed by the notch 161 and the curved part 162. Further, while the insulating wall parts 160 are separated, since they are joined by the curved part 162, the assembly efficiency will not fall. Further, when the amount of heat transported to the condenser 110B due to the heat switch function increases, the heat conduction from the evaporator 110A is blocked by the notch 161, so the restriction of the heat transport will not be impaired.
  • Further, since a tank 140 connecting a plurality of tubes 110 is provided, by providing just one location of the connector 140 with a sealing pipe 141, it becomes possible to evacuate the inside to a vacuum and seal in a working medium.
  • Further, since the evaporator 110A is arranged under the condenser 110B and the tank 140 is provided at the evaporator 110A side end and arranged so as to contact the exhaust pipe part 130A (first plate 131), the working medium in the tank 140 is also positively heated by the exhaust gas and the dry out for activating the heat switch function (turning waste heat recovery OFF) is performed early.
  • Further, since the exhaust pipe part 130A forming part of the exhaust pipe 11 and the cooling water passage part 150A forming part of the heater circuit 30 are joined integrally with the evaporator 110A and condenser 110B to form the waste heat recovery system 100, it is possible to easily attach the exhaust pipe 11 and heater circuit 30 as a single heat exchanger.
  • A second embodiment of the present invention is shown in FIGS. 4A and 4B. The second embodiment comprises the first embodiment where the tubes 110 and fins 120 are changed to the tubes 110 a and fins 120 a.
  • The tubes 110 a are flat type tubes 110 comprised of two tube plates 111, 112 combined to form round tube types. Further, the fins 120 a are comprised of the corrugated type fins 120 provided with tube burring holes and are formed as plate types through which the tubes 110 a are inserted. Further, in the condenser 110B, to improve the heat transmission with the cooling water side, plate type water side fins 120 b are attached. Due to this, similar effects to the first embodiment can be obtained.
  • A third embodiment of the present invention is shown in FIGS. 5A and 5B. The third embodiment is comprised of the first embodiment eliminating the tubes 110, water tank 150, and insulating wall parts 160 and stacking plate type fins 120 c to form tubes 110 b, a water tank 150 a, and insulating wall parts 160 a.
  • The fins 120 c are provided with pluralities of holes having burring parts 121. By stacking the fins 120 c, the burring parts 121 are successively connected whereby tubes 110 b corresponding to round tubes are formed.
  • The outer circumferences of the fins 120 c corresponding to the condenser 110B are provided with raised edges 122. By stacking the fins 120 c, the raised edges 122 are successively connected and a water tank 150 a corresponding to a box shaped vessel is formed. Further, the pluralities of burring parts 121 of the fins 120 c corresponding to the condenser 110B are provided with water holes so as to enable cooling water to circulate across the entire water tank 150 a.
  • Further, the ends of the fins 120 c corresponding to the insulating parts 110C are provided with bent parts 123. By stacking the fins 120 c, the bent parts 123 are successively aligned, whereby insulating wall parts 160 a corresponding to the plurality of separated plate-shaped members are formed.
  • Due to this, the tubes 110, water tank 150, and insulating wall parts 160 are eliminated and the price can be lowered.
  • Fourth embodiments of the present invention are shown in FIG. 6A to FIG. 8B. The fourth embodiments are comprised of the above first to third embodiments where the evaporators 110A of the tubes 110, 110 a, and 110 b are arranged above the condensers 110B to form top heat types. The waste heat recovery systems 100 shown in FIGS. 6A and 6B, FIGS. 7A and 7B, and FIGS. 8A and 8B, appearance wise, are comprised of the waste heat recovery systems 100 explained in FIGS. 2A and 2B, FIGS. 4A and 4B, and FIGS. 5A and 5B inverted vertically and with the inside walls of the tubes 110, 110 a, and 110 b provided with wicks extending from the condensers 110B to the evaporators 110A.
  • Due to this, even if the evaporator 110A is arranged above the condenser 110B in accordance with the positions of the exhaust pipe 11 and heater circuit 30 set in the vehicle, heat transport between the two 110A, 110B becomes possible.
  • Finally, another embodiment will be explained. In the above embodiments, the explanation was given providing insulating wall parts 160 at two locations at the upstream side and downstream side of the cooling air flow, but the invention is not limited to this. It is also possible to provide a wall part at only one location at the upstream side of the cooling air flow. Due to this, the flow of the cooling air is effectively blocked by the insulating wall part 160 and can be prevented from striking the insulating part 110C, so by setting the minimum extent of an insulating wall part 160, condensation of the working medium at the insulating part 110C can be prevented. Further, conversely, insulating wall parts 160 may also be provided at all of the circumference of the insulating part 110C (four locations).
  • Note that the present invention was explained in detail based on specific embodiments, but a person skilled in the art can make various changes, modifications, etc. without departing from the claims and concept of the present invention.

Claims (7)

1. A waste heat recovery system to transport waste heat of exhaust gas to cooling water, comprising:
a heat pipe having an evaporator arranged at the exhaust gas pipe for carrying exhaust gas of the internal combustion engine, a condenser arranged in a cooling water passage for carrying cooling water of the internal combustion engine, and a heat switch limiting the amount of heat transported to the condenser in accordance with the increase in the amount of heating of the evaporator, and
an insulating part formed between the evaporator and condenser is provided with a wall part for preventing heat transmission from an external fluid.
2. A waste heat recovery system as set forth in claim 1, wherein the wall part is provided at the upstream side of the flow of the external fluid of the insulating part.
3. A waste heat recovery system as set forth in claim 1, wherein
wall parts are connected to the evaporator and condenser and are separated by a predetermined amount of clearance formed between the evaporator and the condenser, and
the separated wall parts are connected by an elastic part having elasticity.
4. A waste heat recovery system as set forth in claim 1, wherein
a plurality of heat pipes are provided,
and first end sides of the plurality of heat pipes are provided with a connector connecting the plurality of heat pipes together.
5. A waste heat recovery system as set forth in claim 4, wherein
the evaporator is arranged under the condenser, and
the connector is provided at the evaporator end side and arranged at the outer surface or inside of the exhaust pipe.
6. A waste heat recovery system as set forth in claim 1, wherein
the inside wall of each heat pipe is provided with a wick extending from the evaporator to the condenser, and
the evaporator is arranged above the condenser.
7. A waste heat recovery system as set forth in claim 1, wherein
an exhaust pipe part forming part of the exhaust pipe and
a cooling water passage part forming part of the cooling water passage are provided,
the exhaust pipe part is joined with the evaporator, and
the cooling water passage part is joined with the condenser.
US11/396,987 2005-04-04 2006-04-03 Exhaust heat recovering device Abandoned US20080115923A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2005-107809 2005-04-04
JP2005107809A JP2006284144A (en) 2005-04-04 2005-04-04 Exhaust heat recovery device

Publications (1)

Publication Number Publication Date
US20080115923A1 true US20080115923A1 (en) 2008-05-22

Family

ID=37295563

Family Applications (1)

Application Number Title Priority Date Filing Date
US11/396,987 Abandoned US20080115923A1 (en) 2005-04-04 2006-04-03 Exhaust heat recovering device

Country Status (3)

Country Link
US (1) US20080115923A1 (en)
JP (1) JP2006284144A (en)
DE (1) DE102006015379A1 (en)

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100011738A1 (en) * 2008-07-18 2010-01-21 General Electric Company Heat pipe for removing thermal energy from exhaust gas
US20100018180A1 (en) * 2008-07-23 2010-01-28 General Electric Company Apparatus and method for cooling turbomachine exhaust gas
US20100024382A1 (en) * 2008-07-29 2010-02-04 General Electric Company Heat recovery steam generator for a combined cycle power plant
US20100025016A1 (en) * 2008-07-29 2010-02-04 General Electric Company Apparatus and method employing heat pipe for start-up of power plant
US20100028140A1 (en) * 2008-07-29 2010-02-04 General Electric Company Heat pipe intercooler for a turbomachine
US20100024429A1 (en) * 2008-07-29 2010-02-04 General Electric Company Apparatus, system and method for heating fuel gas using gas turbine exhaust
US20100024424A1 (en) * 2008-07-29 2010-02-04 General Electric Company Condenser for a combined cycle power plant
US20100064655A1 (en) * 2008-09-16 2010-03-18 General Electric Company System and method for managing turbine exhaust gas temperature
US20100072292A1 (en) * 2008-09-25 2010-03-25 Munro Mark S Indoor Space Heating Apparatus
US20100077741A1 (en) * 2008-10-01 2010-04-01 Woodson Wayne Samuel Waste heat auxiliary power unit
US20100089548A1 (en) * 2007-04-11 2010-04-15 Viorel Braic Heat exchanger
US20100095648A1 (en) * 2008-10-17 2010-04-22 General Electric Company Combined Cycle Power Plant
US20110006523A1 (en) * 2009-07-08 2011-01-13 Toyota Motor Eengineering & Manufacturing North America, Inc. Method and system for a more efficient and dynamic waste heat recovery system
CN102803887A (en) * 2010-02-18 2012-11-28 丰田自动车株式会社 Exhaust heat recovery device
US8714288B2 (en) 2011-02-17 2014-05-06 Toyota Motor Engineering & Manufacturing North America, Inc. Hybrid variant automobile drive
US20150300261A1 (en) * 2014-04-17 2015-10-22 General Electric Company Fuel heating system for use with a combined cycle gas turbine
US20160109193A1 (en) * 2014-10-21 2016-04-21 Greenergy Products, Inc. Equipment and Method
US20160363381A1 (en) * 2015-06-15 2016-12-15 Hamilton Sundstrand Corporation Variable heat rejection using heat pipe heat exchanger
CN109489460A (en) * 2018-11-27 2019-03-19 重庆大学 A kind of ash-laden gas stage purification residual neat recovering system and dedusting store heat-exchanger rig
CN109989811A (en) * 2019-05-14 2019-07-09 河北工业大学 A kind of intermediate medium type exhaust gases of internal combustion engines temperature difference electricity generation device
US10428713B2 (en) 2017-09-07 2019-10-01 Denso International America, Inc. Systems and methods for exhaust heat recovery and heat storage
US10577989B2 (en) * 2015-08-18 2020-03-03 Hanon Systems Vehicle oil warmer and heat exchange system
CN111957170A (en) * 2020-08-13 2020-11-20 四川淼垚森环保科技有限公司 Combustion flue gas recycling device and using method thereof
US11208938B2 (en) * 2018-10-22 2021-12-28 Hyundai Motor Company Exhaust tail trim for vehicle
WO2023212978A1 (en) * 2022-05-06 2023-11-09 天津大学滨海工业研究院有限公司 Waste heat recovery device for boiler equipment

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4450056B2 (en) * 2007-11-21 2010-04-14 トヨタ自動車株式会社 Exhaust heat recovery unit
JP4870702B2 (en) * 2008-03-13 2012-02-08 トヨタ自動車株式会社 Exhaust heat recovery unit
DE102011004599A1 (en) * 2011-02-23 2012-08-23 J. Eberspächer GmbH & Co. KG Water heating system, especially for campers
DE102011121471A1 (en) * 2011-12-17 2013-06-20 Volkswagen Aktiengesellschaft Heat accumulator for storage of waste heat from e.g. motor car, has accumulator main portion that is filled with fluid and pouring elements
CN116045715B (en) * 2023-01-09 2023-07-18 浙江志高动力科技有限公司 Energy-saving screw air compressor

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4177858A (en) * 1977-08-22 1979-12-11 Foster Wheeler Energy Corporation Heat exchanger
US4781242A (en) * 1987-03-09 1988-11-01 Volvo Flygmotor A.B. Exhaust heat recovery system for compartment heating
US6793009B1 (en) * 2003-06-10 2004-09-21 Thermal Corp. CTE-matched heat pipe

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4177858A (en) * 1977-08-22 1979-12-11 Foster Wheeler Energy Corporation Heat exchanger
US4781242A (en) * 1987-03-09 1988-11-01 Volvo Flygmotor A.B. Exhaust heat recovery system for compartment heating
US6793009B1 (en) * 2003-06-10 2004-09-21 Thermal Corp. CTE-matched heat pipe

Cited By (37)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100089548A1 (en) * 2007-04-11 2010-04-15 Viorel Braic Heat exchanger
US9097466B2 (en) * 2007-04-11 2015-08-04 MAHLE Behr GmbH & Co. KG Heat exchanger
US20100011738A1 (en) * 2008-07-18 2010-01-21 General Electric Company Heat pipe for removing thermal energy from exhaust gas
US8596073B2 (en) * 2008-07-18 2013-12-03 General Electric Company Heat pipe for removing thermal energy from exhaust gas
US20100018180A1 (en) * 2008-07-23 2010-01-28 General Electric Company Apparatus and method for cooling turbomachine exhaust gas
US8186152B2 (en) 2008-07-23 2012-05-29 General Electric Company Apparatus and method for cooling turbomachine exhaust gas
US20100024429A1 (en) * 2008-07-29 2010-02-04 General Electric Company Apparatus, system and method for heating fuel gas using gas turbine exhaust
US8015790B2 (en) 2008-07-29 2011-09-13 General Electric Company Apparatus and method employing heat pipe for start-up of power plant
US8425223B2 (en) 2008-07-29 2013-04-23 General Electric Company Apparatus, system and method for heating fuel gas using gas turbine exhaust
US8359824B2 (en) * 2008-07-29 2013-01-29 General Electric Company Heat recovery steam generator for a combined cycle power plant
US20100024424A1 (en) * 2008-07-29 2010-02-04 General Electric Company Condenser for a combined cycle power plant
US20100024382A1 (en) * 2008-07-29 2010-02-04 General Electric Company Heat recovery steam generator for a combined cycle power plant
US20100025016A1 (en) * 2008-07-29 2010-02-04 General Electric Company Apparatus and method employing heat pipe for start-up of power plant
US20100028140A1 (en) * 2008-07-29 2010-02-04 General Electric Company Heat pipe intercooler for a turbomachine
US8157512B2 (en) 2008-07-29 2012-04-17 General Electric Company Heat pipe intercooler for a turbomachine
US20100064655A1 (en) * 2008-09-16 2010-03-18 General Electric Company System and method for managing turbine exhaust gas temperature
US20100072292A1 (en) * 2008-09-25 2010-03-25 Munro Mark S Indoor Space Heating Apparatus
US8046998B2 (en) 2008-10-01 2011-11-01 Toyota Motor Engineering & Manufacturing North America, Inc. Waste heat auxiliary power unit
US8555640B2 (en) 2008-10-01 2013-10-15 Toyota Motor Engineering And Manufacturing North America, Inc. Waste heat auxiliary power unit
US20100077741A1 (en) * 2008-10-01 2010-04-01 Woodson Wayne Samuel Waste heat auxiliary power unit
US20100095648A1 (en) * 2008-10-17 2010-04-22 General Electric Company Combined Cycle Power Plant
US8330285B2 (en) 2009-07-08 2012-12-11 Toyota Motor Engineering & Manufacturing North America, Inc. Method and system for a more efficient and dynamic waste heat recovery system
US20110006523A1 (en) * 2009-07-08 2011-01-13 Toyota Motor Eengineering & Manufacturing North America, Inc. Method and system for a more efficient and dynamic waste heat recovery system
CN102803887A (en) * 2010-02-18 2012-11-28 丰田自动车株式会社 Exhaust heat recovery device
US8714288B2 (en) 2011-02-17 2014-05-06 Toyota Motor Engineering & Manufacturing North America, Inc. Hybrid variant automobile drive
US20150300261A1 (en) * 2014-04-17 2015-10-22 General Electric Company Fuel heating system for use with a combined cycle gas turbine
US20160109193A1 (en) * 2014-10-21 2016-04-21 Greenergy Products, Inc. Equipment and Method
US9939203B2 (en) * 2015-06-15 2018-04-10 Hamilton Sundstrand Corporation Variable heat rejection using heat pipe heat exchanger
US20160363381A1 (en) * 2015-06-15 2016-12-15 Hamilton Sundstrand Corporation Variable heat rejection using heat pipe heat exchanger
US10577989B2 (en) * 2015-08-18 2020-03-03 Hanon Systems Vehicle oil warmer and heat exchange system
US10428713B2 (en) 2017-09-07 2019-10-01 Denso International America, Inc. Systems and methods for exhaust heat recovery and heat storage
US11208938B2 (en) * 2018-10-22 2021-12-28 Hyundai Motor Company Exhaust tail trim for vehicle
CN109489460A (en) * 2018-11-27 2019-03-19 重庆大学 A kind of ash-laden gas stage purification residual neat recovering system and dedusting store heat-exchanger rig
WO2020107826A1 (en) * 2018-11-27 2020-06-04 重庆大学 Staged purification and waste heat recovery system for dust-containing flue gas and dedusting heat storage and exchange device
CN109989811A (en) * 2019-05-14 2019-07-09 河北工业大学 A kind of intermediate medium type exhaust gases of internal combustion engines temperature difference electricity generation device
CN111957170A (en) * 2020-08-13 2020-11-20 四川淼垚森环保科技有限公司 Combustion flue gas recycling device and using method thereof
WO2023212978A1 (en) * 2022-05-06 2023-11-09 天津大学滨海工业研究院有限公司 Waste heat recovery device for boiler equipment

Also Published As

Publication number Publication date
DE102006015379A1 (en) 2006-11-16
JP2006284144A (en) 2006-10-19

Similar Documents

Publication Publication Date Title
US20080115923A1 (en) Exhaust heat recovering device
US7946112B2 (en) Exhaust heat recovery device
JP4375454B2 (en) Waste heat recovery device
JP5331026B2 (en) Waste heat recovery device
JP2007278623A (en) Exhaust heat recovery system
US20060231235A1 (en) Heat pipe
JP4245063B2 (en) Waste heat recovery device
JP4259583B2 (en) Exhaust heat recovery device
JP2007024423A (en) Exhaust heat recovery device
JP2007332857A (en) Exhaust heat recovery equipment
JP4627254B2 (en) Heat pipe equipment
JP2009074494A (en) Exhaust heat recovery device
JP2008014304A (en) Exhaust heat recovery equipment
JP2007170299A (en) Exhaust heat recovery system
JP2010223060A (en) Heat exchanger and exhaust heat recovery device
JP2008275292A (en) Exhaust heat recovery device
JP2008267354A (en) Exhaust gas heat recovery device
JP2011196345A (en) Exhaust heat recovery device
JP2012102923A (en) Heat recovery device
JP4941445B2 (en) Exhaust heat recovery device
JP4065741B2 (en) Absorption chiller / heater
JP2007023963A (en) Exhaust heat recovery device
JP3616900B2 (en) Cross-flow boiler, cross-flow regenerator, and absorption refrigerator equipped with the regenerator
JP3021860B2 (en) Heat exchanger
JP2568803B2 (en) Absorption refrigeration equipment

Legal Events

Date Code Title Description
AS Assignment

Owner name: DENSO CORPORATION, JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:YAMANAKA, YASUTOSHI;HAMADA, SHINICHI;INOUE, SEIJI;AND OTHERS;REEL/FRAME:017991/0839

Effective date: 20060526

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION