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US20080196401A1 - Exhaust heat recovery apparatus - Google Patents

Exhaust heat recovery apparatus Download PDF

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Publication number
US20080196401A1
US20080196401A1 US12/070,291 US7029108A US2008196401A1 US 20080196401 A1 US20080196401 A1 US 20080196401A1 US 7029108 A US7029108 A US 7029108A US 2008196401 A1 US2008196401 A1 US 2008196401A1
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US
United States
Prior art keywords
condensation
operation fluid
unit
evaporation
side communication
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
US12/070,291
Other languages
English (en)
Inventor
Kenshirou Muramatsu
Masashi Miyagawa
Yasutoshi Yamanaka
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: KOHARA, KIMIO, MIYAGAWA, MASASHI, INOUE, SEIJI, MURAMATSU, KENSHIROU, YAMANAKA, YASUTOSHI
Publication of US20080196401A1 publication Critical patent/US20080196401A1/en
Abandoned legal-status Critical Current

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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
    • 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
    • F28D15/0266—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 with separate evaporating and condensing chambers connected by at least one conduit; Loop-type heat pipes; with multiple or common evaporating or condensing chambers
    • 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
    • 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
    • F28D15/06—Control arrangements therefor
    • 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
    • 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 an exhaust heat recovery apparatus, which is used for a vehicle such as an automobile.
  • Japanese Unexamined Patent Application Publication No. 62-268722 describes an exhaust heat recovery apparatus for heating an engine coolant using heat of an exhaust gas from an engine. Specifically, an evaporation unit that has heat pipes is disposed in an engine exhaust pipe through which the exhaust gas flows and a condensation unit that has heat pipes is disposed in an engine coolant circuit through which the engine coolant flows.
  • Japanese Unexamined Patent Application Publication No. 4-45393 describes a looped heat pipe heat exchanger.
  • the disclosed heat exchanger includes a looped closed circulation passage filled with an internal heat-transfer fluid, an evaporation unit disposed on the circulation passage for evaporating the internal heat-transfer fluid therein by receiving external heat, and a condensation unit disposed on the circulation passage at a position higher than the evaporation unit for performing heat exchange between the evaporated internal heat-transfer fluid and an external heat-transfer fluid.
  • FIG. 6 shows an example of an exhaust heat recovery apparatus.
  • an evaporation unit J 1 and a condensation unit J 2 as heat exchanging units, are disposed adjacent to each other in a horizontal direction. Ends of heat pipes J 3 of the evaporation and condensation units J 1 , J 2 are coupled to headers (communication parts) J 5 , so that the heat pipes J 3 of the evaporation unit J 1 are in communication with the heat pipes J 3 of the condensation unit J 2 through the headers J 5 .
  • the temperature of the engine coolant is immediately increased by recovering the heat of exhaust gas, especially, in a cold starting of the engine, such as in winter. Therefore, fuel efficiency and heating operation can be improved.
  • an engine high-load condition such as in hot summer, it is necessary to restrict the recovery of the heat of the exhaust gas so as to avoid overheating of the engine.
  • the exhaust heat recovery apparatus with a diaphragm-type valve unit for stopping the circulation of the operation fluid.
  • the diaphragm-type valve unit is constructed of a diaphragm that is movable in response to the pressure of the operation fluid and a valve body that is driven by the diaphragm.
  • the valve unit restricts the heat from being excessively recovered.
  • the present invention is made in view of the foregoing matter, and it is an object of the present invention to provide an exhaust heat recovery apparatus, which is capable of restricting excess recovery of heat with a simple structure.
  • an exhaust heat recovery apparatus includes an evaporation unit, a condensation unit, an evaporation-side communication part, a condensation-side communication part and a throttle part.
  • the evaporation unit is to be disposed in an exhaust gas passage through which an exhaust gas exhausted from an engine flows, for performing heat exchange between the exhaust gas and an operation fluid flowing therein, thereby evaporating the operation fluid.
  • the condensation unit is to be disposed in a coolant passage through which an engine coolant flows, for performing heat exchange between the engine coolant and the operation fluid that has been evaporated in the evaporation unit, thereby condensing the operation fluid.
  • the evaporation-side communication part connects the evaporation unit and the condensation unit for introducing evaporated operation fluid from the evaporation unit to the condensation unit.
  • the condensation-side communication part connects the condensation unit and the evaporation unit for introducing condensed operation fluid from the condensation unit to the evaporation unit.
  • the throttle part is disposed in the condensation-side communication part.
  • the throttle part is configured to restrict an exhaust heat from being excessively recovered. Accordingly, the excess recovery of heat is restricted by a simple structure.
  • the throttle part is constructed of a fixed throttle having an orifice.
  • An upper limit of the quantity of heat recovered in the exhaust heat recovery apparatus can be determined by setting an opening degree of an orifice of the throttle part and the amount of operation fluid enclosed in the exhaust heat recovery apparatus.
  • the throttle part is provided by a variable throttle that is capable of varying an opening degree of an orifice through which the operation fluid in accordance with a temperature of the operation fluid.
  • an exhaust heat recovery apparatus includes an evaporation unit, a condensation unit, an evaporation-side communication part, a condensation-side communication part.
  • the evaporation unit is to be disposed in an exhaust gas passage through which an exhaust gas flows, for performing heat exchange between the exhaust gas and an operation fluid flowing therein, thereby evaporating the operation fluid.
  • the condensation unit is to be disposed in a coolant passage through which an engine coolant flows, for performing heat exchange between the engine coolant and the operation fluid that has been evaporated in the evaporation unit, thereby condensing the operation fluid.
  • the evaporation-side communication part connects the evaporation unit and the condensation unit and defines a passage for introducing the operation fluid from the evaporation unit to the condensation unit.
  • the condensation-side communication part connects the condensation unit and the evaporation unit, and defines a passage for introducing the operation fluid from the condensation unit to the evaporation unit.
  • the condensation-side communication part includes a throttle portion that has a reduced passage area.
  • the excess recovery of heat is restricted by partly reducing the passage area of the condensation-side communication part.
  • FIG. 1 is a schematic cross-sectional view of an exhaust heat recovery apparatus according to a first embodiment of the present invention
  • FIGS. 2A and 2B are conceptual views for showing operations of an exhaust heat recovery apparatus as an comparative example
  • FIGS. 2C and 2D are conceptual views for showing operations of the exhaust heat recovery apparatus according to the first embodiment
  • FIG. 3A is an enlarged schematic cross-sectional view of an evaporation-side communication part of a exhaust heat recovery apparatus, in an operation fluid low-temperature condition, according to a second embodiment of the present invention
  • FIG. 3B is an enlarged schematic cross-sectional view of the evaporation-side communication part of the exhaust heat recovery apparatus, in an operation fluid high-temperature condition, according to the second embodiment of the present invention
  • FIG. 4 is an enlarged schematic cross-sectional view of a condensation-side communication part of an exhaust heat recovery apparatus according to a third embodiment of the present invention.
  • FIG. 5 is an enlarged schematic cross-sectional view of a condensation-side communication part of an exhaust heat recovery apparatus according to another embodiment of the present invention.
  • FIG. 6 is a schematic cross-sectional view of an exhaust heat recovery apparatus of a related art.
  • an exhaust heat recovery apparatus of a first embodiment of the present invention is employed in a vehicle that is driven by an engine (e.g., internal combustion engine), for recovering exhaust heat of an exhaust gas from an exhaust system of the engine and using the heat for facilitating an engine warming up or the like.
  • an engine e.g., internal combustion engine
  • the exhaust heat recovery apparatus generally includes an evaporation unit 1 and a condensation unit 2 .
  • the evaporation unit 1 is disposed in a first housing 100 that is in communication with an exhaust gas passage (not shown) through which the exhaust gas exhausted from the engine flows.
  • the first housing 100 is disposed in an exhaust pipe through which the exhaust gas flows.
  • the evaporation unit 1 performs heat exchange between the exhaust gas and an operation fluid flowing therein, thereby to evaporate the operation fluid.
  • the condensation unit 2 is disposed outside of the exhaust pipe.
  • the condensation unit 2 is disposed in a second housing 200 that is in communication with a coolant passage (not shown) of the engine, through which an engine coolant flows.
  • the condensation unit 2 performs heat exchange between the operation fluid that has been evaporated in the evaporation unit 1 and the engine coolant, thereby to condense the operation fluid.
  • the second housing 200 has a coolant inlet port 201 and a coolant outlet port 202 .
  • the coolant inlet port 201 is coupled to the coolant passage at a position downstream of the engine for introducing the coolant into the second housing 200 .
  • the coolant outlet port 202 is coupled to the coolant passage at a position upstream of the engine for introducing the coolant from the second housing 200 to the coolant passage.
  • the first housing 100 and the second housing 200 are disposed adjacent to each other. Also, a clearance is provided between the first housing 100 and the second housing 200 .
  • the evaporation unit 1 has a plurality of evaporation-side heat pipes 3 a and evaporation-side fins 4 a joined to outer surfaces of the heat pipes 3 a .
  • the fins 4 a are, for example, corrugate fins.
  • Each of the heat pipes 3 a has a generally flat tubular shape.
  • the heat pipe 3 a is orientated such that its longitudinal axis extends in a vertical direction V, such as, an up and down direction in FIG. 1 .
  • the heat pipe 3 a is orientated such that a major axis of a cross-section defined in a direction perpendicular to the longitudinal axis of the pipe 3 a is substantially parallel to a flow direction of the exhaust gas, such as in a direction perpendicular to a paper surface of FIG. 1 .
  • the heat pipes 3 a are stacked parallel to each other in a pipe stacking direction H, such as in a horizontal direction.
  • the evaporation unit 1 has evaporation-side headers 5 a at both ends of the heat pipes 3 a .
  • the headers 5 a extend in the pipe stacking direction H to be in communication with all the heat pipes 3 a .
  • One of the headers 5 a which is in communication with upper ends of the heat pipes 3 a , is referred to as a first evaporation-side header 51 a
  • the other header 5 a which is in communication with lower ends of the heat pipes 3 a
  • the condensation unit 2 includes condensations-side heat pipes 3 b and condensation-side fins 4 b joined to outer surfaces of the heat pipes 3 b .
  • the fins 4 b are, for example, corrugate fins.
  • the heat pipes 3 b are generally flat tubes. Each of the heat pipes 3 b is orientated such that its longitudinal axis extends in the vertical direction V, such as, in the up and down direction in FIG. 1 . Also, the heat pipe 3 b is orientated such that a major axis of a cross-section defined in a direction perpendicular to the longitudinal axis of the pipe 3 b is substantially parallel to the flow direction of the exhaust gas of the evaporation unit 1 , such as in the direction perpendicular to the paper surface of FIG. 1 .
  • the heat pipes 3 b are stacked parallel to each other in the pipe stacking direction H, such as in the horizontal direction.
  • the condensation unit 2 includes condensation-side headers 5 b at both ends of the heat pipes 3 b .
  • the headers 5 b extend in the pipe stacking direction H to be in communication with all the heat pipes 3 b .
  • One of the headers 5 b which is in communication with upper ends of the heat pipes 3 b , is referred to as a first condensation-side header 51 b
  • the other header 5 b which is in communication with lower ends of the heat pipes 3 b
  • the evaporation-side headers 5 a are in communication with the condensation-side headers 5 b through communication parts 6 , which have substantially tubular shapes.
  • a closed, looped path is formed by the heat pipes 3 a , 3 b , the headers 5 a , 5 b and the communication parts 6 .
  • the path is filled with the operation fluid that is capable of being evaporated and condensed, such as water, alcohol or the like.
  • the operation fluid circulates through the evaporation unit 1 and the condensation unit 2 .
  • One of the communication parts 6 which is located on an upper side and connects the first evaporation-side header 51 a and the first condensation-side header 51 b , is referred to as a evaporation-side communication part 61 .
  • the operation fluid that has been evaporated in the evaporation unit 1 is introduced to the condensation unit 2 through the evaporation-side communication part 61 .
  • the other communication part 6 which is located on a lower side and connects the second evaporation-side header 52 a and the second condensation-side header 52 b , is referred to as a condensation-side communication part 62 .
  • the operation fluid that has been condensed in the condensation unit 2 is introduced to the evaporation unit 1 through the condensation-side communication part 62 .
  • the condensation-side communication part 62 has a fixed throttle 7 a as a throttle part.
  • a throttle member 70 is disposed in the condensation-side communication part 62 , and the fixed throttle 7 a is provided by the throttle member 70 . That is, the throttle member 70 is disposed such that a passage area (e.g., a cross-sectional area) of a passage through which the condensed operation fluid flows is partly reduced in the condensation-side communication part 62 .
  • the throttle member 70 forms an orifice having a reduced cross-section.
  • the throttle member 70 has a shape so that a cross-sectional area of the orifice gradually reduces from an upstream end toward a middle portion and gradually increases from the middle portion toward a downstream end, with respect to the flow of the condensed operation fluid.
  • the throttle member 70 has a first tapered tubular wall 701 whose inner diameter reduces from an upstream position toward a downstream position with respect to the flow of the operation fluid, and a second tapered tubular wall 702 continuously extends from a downstream end of the first tapered tubular wall 702 .
  • An inner diameter of the second tapered tubular wall 702 increases from an upstream position toward a downstream position with respect to the flow of the operation fluid.
  • FIGS. 2A and 2B are conceptual views for showing operations of an exhaust heat recovery apparatus without having a throttle part as a comparative example.
  • FIGS. 2C and 2D are conceptual views for showing operations of the exhaust heat recovery apparatus of the present embodiment.
  • FIGS. 2A and 2C show conditions where the quantity Qin of heat of the exhaust gas introduced in the exhaust heat recovery apparatus is a first value Q 1 .
  • FIGS. 2B and 2D show conditions where the quantity Qin of heat of the exhaust gas is a second value Q 2 that is greater than the first value Q 1 .
  • the plurality of evaporation-side heat pipes 3 a is simply illustrated by a singe heat pipe 3 a , for convenience of explanation.
  • the plurality of condensation-side heat pipes 3 b is simply illustrated by a single heat pipe 3 b .
  • the illustration of the fins 4 a , 4 b and the first and second housings 100 , 200 are omitted in FIGS. 2A to 2D .
  • the operation fluid evaporated in the evaporation unit 1 flows in the condensation unit 2 through the evaporation-side communication part 61 .
  • the operation fluid is condensed and liquefied.
  • the liquefied operation fluid flows in the evaporation unit 1 through the condensation-side communication part 62 .
  • a water level difference h of the operation fluid is generated between the evaporation unit 1 and the condensation unit 2 .
  • the operation fluid is returned to the evaporation unit 1 from the condensation unit 2 due to the water level difference h. In this way, the operation fluid is circulated in the exhaust heat recovery apparatus.
  • pressure loss ⁇ P 1 of a return flow of the operation fluid and the water level difference h satisfy the following relation:
  • p denotes the density of the operation fluid in a liquid phase
  • g denotes the gravitational acceleration.
  • the density p of the operation fluid and the gravitational acceleration g are constant.
  • ⁇ P′ ⁇ P 1 + ⁇ P 2
  • a water level difference h 2 between the evaporation unit 1 and the condensation unit 2 is greater than the water level difference h of the exhaust heat recovery apparatus shown in FIG. 2A by the amount of the pressure loss ⁇ P 2 of the fixed throttle 7 a.
  • the fixed throttle 7 a is provided in the condensation-side communication part 62 .
  • the upper limit of the quantity of heat recovered in the exhaust heat recovery apparatus is determined by previously setting an opening degree of the fixed throttle 7 a , such as the passage area of the orifice of the fixed throttle 7 a , and the amount of the operation fluid filled in the exhaust heat recovery apparatus.
  • the condensation-side communication part 62 is provided with a variable throttle 7 b as the throttle part, in place of the fixed throttle 7 a of the first embodiment.
  • the variable throttle 7 b is configured to vary the opening degree of an orifice defined therein, that is, the cross-sectional area of the passage of the operation fluid, in accordance with the temperature of the operation fluid.
  • FIG. 3A shows a condition of the variable throttle 7 b when the temperature of the operation fluid is low
  • FIG. 3B shows a condition of the variable throttle 7 b when the temperature of the operation fluid is high.
  • the variable throttle 7 b is configured such that the opening degree is reduced in accordance with an increase in the temperature of the operation fluid.
  • variable throttle 7 b is made of a material that is deformable in accordance with the ambient temperature.
  • the material of the variable throttle 7 b can be a bi-metal, a shape-memory alloy, or the like.
  • the variable throttle 7 b is configured such that the passage of the operation fluid is not fully closed, even when the temperature of the operation fluid flowing through the condensation-side communication part 62 is increased.
  • variable throttle 7 b is provided in the condensation-side communication part 62 .
  • the opening degree of the variable throttle 7 b reduces with the increase of the temperature of the operation fluid, and hence the pressure loss ⁇ P 2 increases. As such, an increase in the quantity of the heat recovered in the exhaust heat recovery apparatus is limited at a certain point.
  • the condensation-side communication part 62 is provided with the variable throttle 7 b that varies the opening degree in accordance with the increase in the temperature of the operation fluid. Therefore, the quantity of heat recovered in the exhaust heat recovery apparatus is reduced in accordance with the increase in temperature of the operation fluid. Because the quantity of heat recovered in the exhaust heat recovery apparatus is limited when an engine load is high, such as in summer, in which the temperature of the operation fluid is high, it is less likely that the engine will be overheated.
  • a third embodiment of the present invention will be described with reference to FIG. 4 .
  • Components similar to the first embodiment will be designated by the same reference numerals, and a description thereof is not repeated.
  • the exhaust heat recovery apparatus of the present embodiment has a variable throttle 7 c in the condensation-side communication part 62 , as the throttle part.
  • the variable throttle 7 c includes an orifice 71 , a valve body 72 for opening and closing the orifice 71 , and a temperature sensitive deformable member 73 .
  • An end of the deformable member 73 is connected to an end wall of the vale body 72 on a side opposite to the orifice 71 .
  • An opposite end of the deformable member 73 is connected to a support member 74 that is disposed in the condensation-side communication part 62 .
  • the deformable member 73 is deformable in response to the temperature.
  • the deformable member 73 is configured to be thermally expanded when the temperature of the operation fluid passing through the condensation-side communication part 62 exceeds a predetermined temperature.
  • the deformable member 73 is, for example, made of thermo-wax, thermo-metal, or the like, which has a coefficient of thermal expansion greater than that of the metal of the condensation-side communication part 62 .
  • the valve body 72 When the temperature of the operation fluid passing through the condensation-side communication part 62 increases, the valve body 72 is moved in a direction to reduce the opening degree of the orifice 71 . On the other hand, when the temperature of the operation fluid passing through the condensation-side communication part 62 reduces, the valve body 72 is moved in a direction to increase the opening degree of the orifice 71 . In the present embodiment, the valve body 72 does not fully close the orifice 71 , even when the temperature of the operation fluid passing through the condensation-side communication part 62 is increased.
  • the condensation-side communication part 62 is provided with the variable throttle 7 c that varies the opening degree of the orifice 71 in accordance with the increase in the temperature of the operation fluid, the quantity of heat recovered in the exhaust heat recovery apparatus is reduced in accordance with the increase in temperature of the operation fluid. As such, the effects similar to the second embodiment will be provided.
  • the throttle member 70 forms the orifice the inner diameter of which gradually reduces from the upstream position toward the middle position and gradually increases from the middle position toward the downstream position with respect to the flow of the operation fluid.
  • the shape of the orifice of the throttle member 70 is not limited to the above.
  • the throttle member 70 may have a cylindrical shape and may have a substantially constant passage area.
  • the fixed throttle 7 a is provided by the throttle member 70 .
  • the fixed throttle 7 a can be formed by partly reducing a passage area (e.g., inner diameter) of the condensation-side communication part 62 , as shown in FIG. 5 . In this case, the number of components is reduced. Further, the pressure loss ⁇ P 2 of the fixed throttle 7 a is determined by arranging an inner diameter d and a length L of the fixed throttle 7 a.
  • variable throttles 7 b , 7 c are disposed to directly contact the operation fluid, and the opening degrees of the variable throttles 7 b , 7 c are mechanically controlled in accordance with the temperature of the operation fluid.
  • a temperature sensor can be separately employed to detect the temperature of the operation fluid passing through the condensation-side communication part 62 , and the variable throttle 7 b , 7 c can be configured such that the opening degrees thereof are electrically controlled based on the temperature detected by the temperature sensor.
  • the condensation-side communication part 62 is exemplarily orientated horizontally.
  • the orientation of the condensation-side communication part 62 is not limited to the above.
  • the condensation-side communication part 62 can be inclined relative to a horizontal direction.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Exhaust Silencers (AREA)
US12/070,291 2007-02-19 2008-02-18 Exhaust heat recovery apparatus Abandoned US20080196401A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2007037482A JP2008202450A (ja) 2007-02-19 2007-02-19 排気熱回収器
JP2007-037482 2007-02-19

Publications (1)

Publication Number Publication Date
US20080196401A1 true US20080196401A1 (en) 2008-08-21

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ID=39646268

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Application Number Title Priority Date Filing Date
US12/070,291 Abandoned US20080196401A1 (en) 2007-02-19 2008-02-18 Exhaust heat recovery apparatus

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US (1) US20080196401A1 (de)
JP (1) JP2008202450A (de)
CN (1) CN101251060A (de)
DE (1) DE102008009212A1 (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20170074596A1 (en) * 2015-09-16 2017-03-16 Acer Incorporated Thermal dissipation module
CN109974135A (zh) * 2019-04-19 2019-07-05 青岛海尔智能技术研发有限公司 一种散热器、空调室外机和空调器
CN109974138A (zh) * 2019-04-19 2019-07-05 青岛海尔智能技术研发有限公司 一种散热器、空调室外机和空调器
US20250230988A1 (en) * 2024-01-15 2025-07-17 Raytheon Company Adaptive oscillating heat pipe

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105697104A (zh) * 2016-04-17 2016-06-22 曹阳 一种燃油燃气电栅机动车尾气净化器

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62268722A (ja) 1986-05-16 1987-11-21 Nippon Denso Co Ltd 内燃機関の排気熱利用装置
JPH0445393A (ja) 1990-06-12 1992-02-14 Aisin Seiki Co Ltd ループ型ヒートパイプ式熱交換器

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20170074596A1 (en) * 2015-09-16 2017-03-16 Acer Incorporated Thermal dissipation module
CN109974135A (zh) * 2019-04-19 2019-07-05 青岛海尔智能技术研发有限公司 一种散热器、空调室外机和空调器
CN109974138A (zh) * 2019-04-19 2019-07-05 青岛海尔智能技术研发有限公司 一种散热器、空调室外机和空调器
US20250230988A1 (en) * 2024-01-15 2025-07-17 Raytheon Company Adaptive oscillating heat pipe

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DE102008009212A1 (de) 2008-08-28
CN101251060A (zh) 2008-08-27
JP2008202450A (ja) 2008-09-04

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