US20070289721A1 - Loop type heat pipe and waste heat recovery device - Google Patents

Loop type heat pipe and waste heat recovery device Download PDF

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Publication number
US20070289721A1
US20070289721A1 US11/818,257 US81825707A US2007289721A1 US 20070289721 A1 US20070289721 A1 US 20070289721A1 US 81825707 A US81825707 A US 81825707A US 2007289721 A1 US2007289721 A1 US 2007289721A1
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United States
Prior art keywords
refrigerant
condenser
evaporator
tubes
fluid
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Abandoned
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US11/818,257
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English (en)
Inventor
Masashi Miyagawa
Yasutoshi Yamanaka
Seiji Inoue
Kimio Kohara
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Denso Corp
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Denso Corp
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Assigned to DENSO CORPORATION reassignment DENSO CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: INOUE, SEIJI, KOHARA, KIMIO, MIYAGAWA, MASASHI, YAMANAKA, YASUTOSHI
Publication of US20070289721A1 publication Critical patent/US20070289721A1/en
Abandoned legal-status Critical Current

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    • 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
    • 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

Definitions

  • the present invention relates to a loop type heat pipe, in which a refrigerant is evaporated by heat from a first fluid as a heat source, and the evaporated vapor refrigerant is cooled by a second fluid to be heated so as to heat the second fluid by condensation latent heat of the vapor refrigerant.
  • the loop type heat pipe can be suitably used for a waste heat recovery device.
  • a loop type heat pipe is described in JP-A-4-45393, for example.
  • This loop type heat pipe is provided with an evaporator for heating and evaporating refrigerant, and a condenser for cooling and condensing the evaporated vapor refrigerant.
  • operation of the loop type heat pipe is controlled by a switching valve (opening and closing valve).
  • the switching valve is located to open and close a passage through which the liquid refrigerant condensed in the condenser returns to the evaporator.
  • the loop type heat pipe is provided with a liquid refrigerant storage portion for storing the liquid refrigerant therein at an upstream side (i.e., condenser side) of the switching valve.
  • the liquid refrigerant storage portion and the switching valve are located outside of the condenser.
  • the condenser is located in a tank in which the second fluid to be heated flows, such that the vapor refrigerant introduced to the condenser is heat-exchanged with the second fluid flowing in the tank so as to heat the second fluid.
  • this loop type heat pipe it is difficult to always improve heating performance of the second fluid to be heated, by a simple structure.
  • a loop type heat pipe in which a refrigerant circulates includes an evaporator located to evaporate the refrigerant by heat-exchanging with a first fluid as a heat source, and a condenser located to liquefy and condense the evaporated vapor refrigerant by heat-exchanging with a second fluid to be heated.
  • the condenser has a refrigerant condensation side on which the condensed liquid refrigerant flows, and a refrigerant un-condensation side on which the vapor refrigerant before being condensed flows.
  • the loop type heat pipe is provided with a flow limitation means for flowing the second fluid from the refrigerant condensation side toward the refrigerant un-condensation side. Therefore, the condensed liquid refrigerant can be effectively cooled to a low temperature because a temperature difference between the refrigerant and the second fluid can be made larger on both the refrigerant condensation side and the refrigerant un-condensation side. Accordingly, the temperature of the liquid refrigerant to be supplied to the evaporator can be lowered, and heat absorbing amount of the refrigerant in the evaporator can be increased. As a result, heat pump efficiency of the loop type heat pipe can be effectively increased and thereby improving heating performance of the second fluid to be heated.
  • a liquid refrigerant storage portion may be provided to store the condensed liquid refrigerant.
  • the flow limitation means is provided for flowing the second fluid from a side of the liquid refrigerant storage portion toward the refrigerant un-condensation side.
  • the liquid refrigerant storage portion may be a part of the condenser.
  • an operation stop means for stopping the evaporation of the refrigerant in the evaporator may be provided.
  • the operation stop means may be a switching valve located to open and close a passage through which the liquid refrigerant condensed in the condenser flows to the evaporator, or may be a flow control means for controlling a flow amount of the first fluid flowing to the evaporator.
  • the loop type heat pipe may be suitably used for recovering waste heat of exhaust gas from an engine.
  • the first fluid is an exhaust gas of the engine
  • the second fluid is a coolant used for a coolant circuit of the engine
  • the evaporator and the condenser are located to recovery waste heat from the exhaust gas.
  • a waste heat recovery device includes: a loop-type heat pipe including an evaporator located to evaporate a refrigerant by performing a heat exchange with a first fluid, and a condenser located to cool and condense the evaporated vapor refrigerant from the evaporator; a first fluid flowing portion in which the first fluid flows to perform heat exchange with the refrigerant flowing in the evaporator; a second fluid flowing portion in which the second fluid flows to perform heat exchange with the refrigerant flowing in the condenser; an introducing pipe for introducing the second fluid to the second fluid flowing portion; and a discharging pipe for discharging the second fluid from the second fluid flowing portion after passing through the second fluid flowing portion.
  • the condenser has a refrigerant condensation side on which the condensed liquid refrigerant flows, and a refrigerant un-condensation side on which the vapor refrigerant before being condensed flows.
  • the introducing pipe is connected to the second fluid flowing portion at the refrigerant condensation side of the condenser, and the discharging pipe is connected to the second fluid flowing portion at the refrigerant un-condensation side of the condenser. Therefore, the condensed liquid refrigerant can be effectively cooled to a low temperature because a temperature difference between the refrigerant and the second fluid can be made larger on both the refrigerant condensation side and the refrigerant un-condensation side.
  • the temperature of the liquid refrigerant to be supplied to the evaporator can be lowered, and heat absorbing amount of the refrigerant in the evaporator can be increased.
  • heat recovery efficiency heat pump efficiency
  • FIG. 1 is a schematic diagram showing a loop type heat pipe used for a waste heat recovery device, according to a first embodiment of the present invention
  • FIG. 2 is a schematic diagram showing the waste heat recovery device for a vehicle engine, according to the first embodiment
  • FIG. 3 is a schematic diagram showing a loop type heat pipe used for a waste heat recovery device, according to a second embodiment of the present invention.
  • FIG. 4 is a schematic diagram showing a loop type heat pipe used for a waste heat recovery device, according to a third embodiment of the present invention.
  • a loop type heat pipe is typically used for a waste heat recovery device.
  • An engine (internal combustion engine) 1 is located for generating a rotation output for a vehicle running by fuel combustion.
  • the engine 1 is generally provided with a coolant circuit for controlling heat generated in the engine 1 , and an exhaust pipe 2 for discharging exhaust gas to atmosphere.
  • the coolant circuit includes a radiator circuit 3 , a heater circuit 4 and a waste heat recovery circuit 5 . Furthermore, a catalytic converter 6 for purifying the exhaust gas and the waste heat recovery device 7 are located in the exhaust pipe 2 .
  • a radiator 9 is located to perform heat exchange between the coolant circulated by a water pump 8 and outside air so as to cool the coolant.
  • a bypass passage 10 through which the coolant flows while bypassing the radiator 9 , is provided in the radiator circuit 3 .
  • a thermostat 11 is located in the radiator circuit 3 .
  • the thermostat 11 adjusts a ratio between a coolant amount passing through the radiator 9 and a coolant amount passing through the radiator bypass passage 10 such that the temperature of the coolant is controlled in a temperature range (e.g., 80° C. to 100° C.). For example, when the temperature of the coolant is low in an engine heating time, the coolant amount supplying to the radiator bypass passage 10 is increased so as to facilitate the engine heating operation at the engine heating time.
  • a temperature range e.g. 80° C. to 100° C.
  • the heater circuit 4 is connected to the engine 1 , such that the coolant flows out of the engine 1 from a position different from an engine outlet for the radiator circuit 3 , and is joined to the waste heat recovery circuit 5 on a downstream side of the waste heat recovery device 7 .
  • a heater core 12 is located in the heater circuit 4 to heat a fluid by using heat from the coolant.
  • the heater core 12 is located in an air duct for a vehicle air conditioner such that air flowing in the air duct is heat exchanged with the coolant. Therefore, air to be blown into a vehicle compartment is heated by the heater core 12 .
  • the waste heat recovery circuit 5 is branched from the radiator circuit 3 in a passage from the engine 1 to the radiator 9 , and is joined to the water pump 8 . Therefore, the coolant is circulated in the waste heat recovery circuit 5 by operation of the water pump 8 .
  • a water tank 13 (fluid tank) provided in the waste heat recovery device 7 is connected to a passage of the waste heat recovery circuit 5 .
  • the waste heat recovery device 7 is located to recover heat generated from the exhaust gas (first fluid as a heat source) and to heat the coolant (second fluid to be heated) flowing in the waste heat recovery circuit 5 by using the loop type heat pipe that performs heat transport (heat pump) due to refrigerant evaporation and refrigerant condensation.
  • the waste heat recovery device 7 heats the coolant by using heat of the exhaust gas after passing through the catalytic converter 6 .
  • an evaporator 14 and a condenser 15 contained in a tank 13 are integrally formed to construct the loop type heat pipe. Furthermore, a switching valve such as a differential pressure regulating valve 16 is located to control the operation of the loop type heat pipe in accordance with an interior pressure of the loop type heat pipe.
  • the evaporator 14 and the condenser 15 accommodated in the tank 13 are made of an anti-corrosion material (e.g., stainless steel), and are integrally bonded using a bonding technique such as brazing. After the bonding, the differential pressure regulating valve 16 is assembled to the integrated member of the evaporator 14 and the condenser 15 , so as to form the loop type heat pipe used for the waste heat recovery device 7 .
  • an anti-corrosion material e.g., stainless steel
  • the waste heat recovery device 7 has a sealing portion (not shown). After the interior of the waste heat recovery device 7 is vacuated and a refrigerant (operation fluid) is filled therein, the sealing portion is sealed.
  • water is used as one example of the refrigerant.
  • the water has a boiling point of 100° C. at 1 atm. Because the interior of the waste heat recovery device 7 is decompressed and vacuated to, for example, 0.01 atm, water in the waste heat recovery device 7 has a boiling point in a range of 5° C.-10° C.
  • an operation fluid other than water such as alcohol, fluorocarbon, Freon, etc. may be used.
  • the evaporator 14 is a heat exchanger in which the exhaust gas passing through the exhaust pipe 2 is heat exchanged with water flowing in the evaporator 14 .
  • Any type heat exchanger for example, a laminated-type heat exchanger, a header type heat exchanger, a drawn-cup type heat exchanger may be used as the evaporator 14 .
  • the evaporator 14 includes a heat exchanging portion 17 , a lower tank 18 and an upper tank 19 .
  • the heat exchanging portion 17 is a laminated type in which tubes 17 a and fins 17 b are alternately laminated in a lamination direction.
  • the heat exchanging portion 17 is mounted on a vehicle such that the longitudinal direction of the tubes 17 a are directed in the up-down direction of the vehicle.
  • the fins 17 b may be omitted in the heat exchanging portion 17 .
  • the exhaust efficiency and durability can be improved in the heat exchanging portion 17 , although the refrigerant evaporation capacity is decreased.
  • the lower tank 18 is positioned at a lower side of the heat exchanging portion 17 when the waste heat recovery device 7 is mounted on the vehicle.
  • the differential pressure regulating valve 16 is located in the lower tank 18 , such that condensed water supplied from the differential pressure regulating valve 16 is distributed into the tubes 17 through the lower tank 18 .
  • the upper tank 19 is positioned at an upper side of the heat exchanging portion 17 when the waste heat recovery device 7 is mounted on the vehicle, such that the evaporated vapor refrigerant rising in the tubes 17 a is collected in the upper tank 19 .
  • the evaporated vapor refrigerant collected in the upper tank 19 is introduced to the condenser 15 .
  • the condenser 15 is located in the tank 13 in which the coolant flows.
  • the tank 13 is a container, and is located such that the coolant flows between the tank 13 and the evaporator 14 .
  • the tank 13 is constructed with a tank plate connected to a side surface of the evaporator 14 , and a tank cup connected to the tank plate to receive the condenser 15 .
  • a coolant introducing pipe 21 for introducing the coolant into the tank 13 , and a coolant discharging pipe 22 for discharging the coolant after passing through the tank 13 are connected to the tank 13 .
  • the condenser 15 is a heat exchanger in which the vapor refrigerant supplied from the evaporator 14 is heat exchanged with the coolant flowing in the tank 13 .
  • Any type heat exchanger for example, a laminated-type heat exchanger, a header type heat exchanger, a drawn-cup type heat exchanger may be used as the condenser 15 .
  • the condenser 15 is located on the side surface of the evaporator 14 , adjacent to the evaporator 14 , as shown in FIG. 1 .
  • the condenser 15 includes a heat exchanging portion 23 , a refrigerant upstream tank 24 and a refrigerant downstream tank 25 .
  • the heat exchanging portion 23 includes a plurality of tubes 23 a that are laminated at intervals. The coolant passes through the clearances between the tubes 23 a in the tank 13 to be heat exchanged with the refrigerant flowing in the tubes 23 a .
  • Each of the tubes 23 a extends between the refrigerant upstream tank 24 and the refrigerant downstream tank 25 in parallel with the tubes 17 a of the evaporator 14 .
  • the waste heat recovery device 7 is mounted on the vehicle such that the longitudinal direction of the tubes 23 a of the heat exchanging portion 23 is directed in the vertical direction. Fins may be located on the tubes 23 a of the heat exchanging portion 23 in order to improve heat exchanging efficiency.
  • the refrigerant upstream tank 24 is positioned on the upper side of the heat exchanging portion 23 , and the refrigerant downstream tank 25 is positioned on the lower side of the heat exchanging portion 23 , in this embodiment. Therefore, vapor refrigerant supplied from the upper tank 19 of the evaporator 14 to the refrigerant upstream tank 24 is distributed into the tubes 23 a to be cooled and condensed by the coolant flowing in the tank 13 . Then, the condensed liquid refrigerant from the tubes 23 a is collected to the refrigerant downstream tank 25 and is introduced to the differential pressure regulating valve 16 .
  • the differential pressure regulating valve 16 used as an operation stop means for stopping the evaporation of refrigerant in the evaporator 14 will be described.
  • the differential pressure regulating valve 16 is one example of an opening and closing valve type, and is located in a communication passage through which the liquid refrigerant condensed in the condenser 15 is introduced to the evaporator 14 .
  • the differential pressure regulating valve 16 When the interior pressure of the waste heat recovery device 7 is increased to be larger than a first value, the differential pressure regulating valve 16 is closed to shut the communication between the lower tank 18 of the evaporator 14 and the refrigerant downstream tank 25 of the condenser 15 so as to prevent an exceed pressure increase in the waste heat recovery device 7 . In contrast, when the interior pressure of the waste heat recovery device 7 is decreased to be lower than a second value lower than the first value, the differential pressure regulating valve 16 opens the communication passage between the lower tank 18 of the evaporator 14 and the refrigerant downstream tank 25 of the condenser 15 so as to restart the waste heat recovery operation of the waste heat recovery device 7 .
  • the differential pressure regulating valve 16 is an opening and closing valve (switching valve) which performs the communication or the shutting between the refrigerant downstream tank 25 of the condenser 15 and the lower tank 18 of the evaporator 14 , based on a differential pressure between the interior pressure of the waste heat recovery device 7 and the atmosphere. If the atmosphere is constant, when the interior pressure of the waste heat recovery device 7 is increased to a valve closing pressure Pc, the communication between the lower tank 18 of the evaporator 14 and the refrigerant downstream tank 25 of the condenser 15 is shut.
  • switching valve switching valve
  • FIG. 1 shows an example structure of the differential pressure regulating valve 16 .
  • the differential pressure regulating valve 16 includes a housing 26 , a valve body 27 , a diaphragm 28 and a return spring (not shown).
  • the housing 26 is an approximately cylindrical member located in the refrigerant downstream tank 25 , and the valve body 27 is held in the housing 26 to be movable in an axial direction.
  • the housing 26 has an inner space 26 a , and the inner space 26 a communicates with the refrigerant downstream tank 25 through a side port 26 b so that the liquid refrigerant in the refrigerant downstream tank 25 flows into the inner space 26 a of the housing 26 of the differential pressure regulating valve 16 .
  • the inner space 26 a of the housing 26 communicates with the lower tank 18 of the evaporator 14 through a valve open port 26 c that is opened and closed by a valve body 27 . Therefore, when the valve open port 26 c is opened by the valve body 27 , the liquid refrigerant in the inner space 26 a flows into the lower tank 18 through the valve open port 26 c.
  • the valve body 27 is held in the housing 26 to be displaceable in its axial direction.
  • the valve body 27 is provided with a valve bell 27 a which opens and closes the valve open port 26 c in accordance with a displacement of the valve body 27 in the axial direction.
  • the diaphragm 28 is located to displace the valve body 27 in the axial direction based on the differential pressure between the interior pressure of the waste heat recovery device 7 and the atmosphere, and to prevent panting of the differential pressure regulating valve 16 by reflection operation of the diaphragm 28 .
  • the return spring (not shown) is a spring member that biases the valve body 27 from the atmosphere side to the valve opening direction. By adjusting the biasing force of the return spring, the valve open pressure Po for displacing the diaphragm 28 to the valve opening direction and the valve close pressure Pc for displacing the diaphragm 28 to the valve closing direction can be adjusted.
  • valve open pressure Pc is set at an interior pressure of the waste heat recovery device 7 when the operation load of the engine 1 is a half throttle load at a temperature (e.g., 70° C.) of the coolant immediately after finishing the engine heating.
  • valve open pressure Po is set at an interior pressure of the waste heat recovery device 7 in an engine idling (zero load operation) at a temperature (e.g., 70° C.) of the coolant immediately after finishing the engine heating.
  • the water pump 8 is operated such that the coolant is circulated in the radiator circuit 3 , the heater circuit 4 and the waste heat recovery circuit 5 .
  • exhaust gas generated with the fuel combustion of the engine 1 flows into the exhaust pipe 2 , the catalytic converter 6 and the evaporator 14 of the waste heat recovery device 7 , and then is discharged to the atmosphere.
  • the refrigerant circulating in the loop type heat pipe between the evaporator 14 and the condenser 15 water is used. Therefore, the exhaust gas from the engine 1 through the exhaust pipe 2 heats water as the refrigerant within the evaporator 14 while passing through the evaporator 14 .
  • the water in the evaporator 14 is boiled and evaporated by absorbing heat from the exhaust gas, and the evaporated water vapor flows in the tubes 17 a upwardly to be collected into the upper tank 19 . Then, the water vapor flows from the upper tank 19 of the evaporator 14 into the refrigerant upstream tank 24 of the condenser 15 .
  • the water vapor (refrigerant vapor) introduced into the condenser 15 is cooled and condensed by the coolant flowing in the tank 13 .
  • the interior pressure of the waste heat recovery device 7 is not increased to the valve close pressure Pc.
  • the differential pressure regulating valve 16 is opened, thereby the condensed water cooled and condensed in the condenser 15 returns to the lower tank 18 of the evaporator 14 through the differential pressure regulating valve 16 .
  • the waste heat recovery cycle can be repeated in the waste heat recovery device 7 .
  • the refrigerant e.g., water
  • the water as the refrigerant is evaporated in the evaporator 14 by absorbing heat from the exhaust gas, and heat contained in the water as the refrigerant is exhausted as condensation latent heat while being condensed so as to heat the coolant circulating in the waste heat recovery circuit 5 .
  • a part of heat of the exhaust gas is transmitted to members constructing the evaporator 14 and the condenser 15 , and heats the coolant flowing in the waste heat recovery circuit 5 via those members.
  • the heating of the engine 1 can be facilitated at an engine start time, and a fuel increasing time (auto choke operation ratio) for facilitating the engine heating can be shortened, thereby improving fuel consumption efficiency.
  • the heat quantity of the exhaust gas for heating the water as the refrigerant in the evaporator 14 is increased, and the vapor amount generated in the evaporator 14 is increased thereby increasing the interior pressure of the loop type heat pipe in the waste heat recovery device 7 .
  • the interior pressure of the loop type heat pipe in the waste heat recovery device 7 is increased to the valve close pressure Pc, the differential pressure regulating valve 16 is closed, so that condensed water in the condenser 15 does not return to the evaporator 14 .
  • the waste heat recovery device 7 is provided with a flow limitation means for performing a flow of the coolant from a refrigerant condensation side (i.e., a side of the refrigerant downstream tank 25 ) to a refrigerant un-condensation side (i.e., a side of the refrigerant upstream tank 24 ).
  • a refrigerant condensation side is a side on which the condensed liquid refrigerant stays or flows
  • the refrigerant un-condensation side is a side on which the vapor refrigerant before being condensed stays or flows.
  • the coolant introducing pipe 21 for introducing the coolant into the tank 13 is located at a most downstream side (refrigerant condensation side) of the condenser 15 in a refrigerant flow direction
  • the coolant discharging pipe 22 for discharging the coolant after passing through the tank 13 is located at a most upstream side (refrigerant un-condensation side) of the condenser 15 in the refrigerant flow direction.
  • the coolant introducing pipe 21 is located at a bottom portion of the tank 13
  • the coolant discharging pipe 22 is located at a top portion of the tank 13 , so as to form the flow limitation means.
  • the coolant introducing pipe 21 is located at the bottom portion of the tank 13 and the coolant discharging pipe 22 is located at the top portion of the tank 13 .
  • the coolant flows in a direction from the refrigerant condensation side (i.e., the side of the refrigerant downstream tank 25 ) toward the refrigerant un-condensation side (i.e., the side of the refrigerant upstream tank 24 ). Therefore, liquid refrigerant condensed in the condenser 15 can be cooled by the coolant before being heated or slightly heated to have a relatively low temperature. Accordingly, the liquid refrigerant to be supplied to the evaporator 14 can be cooled to a relatively low temperature so as to be super-cooled.
  • the vapor refrigerant immediately after being introduced to the condenser 15 has a high temperature, and its temperature is lowered as the condensation is more performed. That is, the refrigerant has a high temperature at the refrigerant un-condensation side (i.e., the side of the refrigerant upstream tank 24 ), and the temperature of the refrigerant is lowered as the refrigerant moves toward the refrigerant condensation side (i.e., the side of the refrigerant downstream tank 25 ).
  • the coolant introducing pipe 21 is located at the bottom portion of the tank 13 and the coolant discharging pipe 22 is located at the top portion of the tank 13 , so that the coolant flows in the direction from the refrigerant condensation side (i.e., the side of the refrigerant downstream tank 25 ) toward the refrigerant un-condensation side (i.e., the side of the refrigerant upstream tank 24 ), as described above. Therefore, the coolant having been heated by the condensed liquid refrigerant having a relative low temperature, can be further heated by the un-condensation vapor refrigerant having a relative high temperature. Accordingly, the temperature of the coolant heated by the condenser 15 while passing through the tank 13 can be effectively increased.
  • the differential pressure regulating valve 16 is closed when the interior pressure of the loop type heat pipe in the waste heat recovery device 7 is increased. Therefore, it can prevent the waste heat recovery device 7 from being overheated during a high engine load in the summer, thereby preventing the waste heat recovery device 7 from being damaged.
  • the liquid refrigerant storage portion 29 for storing the condensed liquid refrigerant is located in the condenser 15 at a refrigerant upstream side of the valve open port 26 c of the differential pressure regulating valve 16 . Therefore, when the differential pressure regulating valve 16 is closed, the amount of the liquid refrigerant stored in the liquid refrigerant storage portion 29 is increased.
  • the liquid refrigerant of the condenser 15 flows into the evaporator 14 by using the difference between the liquid height (liquid surface position of the refrigerant in the condenser 15 ) in the liquid refrigerant storage portion 29 and the liquid height (liquid surface position of the refrigerant in the evaporator 14 ) of the evaporator 14 .
  • the liquid refrigerant storage portion 29 in which condensed liquid refrigerant is stored, can be formed at a refrigerant downstream side position of the condenser 15 and at a refrigerant upstream side position of the valve open port 26 c of the differential pressure regulating valve 16 .
  • the waste heat recovery device 7 of this embodiment is provided with the liquid refrigerant storage portion 29 for storing the liquid refrigerant to the lower portion in the condenser 15 , and the flow limitation means for flowing the coolant from the side of the liquid refrigerant storage portion 29 to the refrigerant un-condensation portion of the condenser 15 . Accordingly, the liquid refrigerant condensed in the condenser 15 can be super-cooled by the unheated coolant or the coolant having a relative low temperature, thereby the liquid refrigerant returned to the evaporator 14 can be accurately cooled to a low temperature.
  • the tubes 23 a of the condenser 15 are elongated in the vertical direction so that liquid refrigerant moves downwardly by its weight when the waste heat recovery device 7 is mounted on a vehicle. That is, in the above-described first embodiment, the condenser 15 is located on the side surface of the evaporator 14 such that the tubes 17 a of the evaporator 14 and the tubes 23 a of the condenser 15 are arranged in parallel with each other to be elongated in the vertical direction when the waste heat recovery device 7 is mounted on a vehicle. However, in the second embodiment, the condenser 15 is located such that the longitudinal direction of the tubes 23 a of the condenser 15 is approximately perpendicular to the longitudinal direction of the tubes 17 a of the evaporator 14 .
  • the condenser 15 is located at a top portion of the evaporator 14 , such that the tubes 23 a of the condenser 15 are elongated in the vehicle horizontal direction and the tubes 17 a of the evaporator 14 are elongated in the vehicle vertical direction when the waste heat recovery device 7 is mounted on the vehicle.
  • the refrigerant upstream tank 24 of the condenser 15 is connected to the upper tank 19 of the evaporator 14 to directly communicate with the upper tank 19 of the evaporator 14 .
  • the differential pressure regulating valve 16 is located in the refrigerant downstream tank 25 of the condenser 15 to adjust the flow of refrigerant from the refrigerant downstream tank 25 to the evaporator 14 , similarly to the above-described first embodiment.
  • An open outlet of the differential pressure regulating valve 16 is connected to the lower tank 18 of the evaporator 14 through a liquid refrigerant passage 31 .
  • the liquid refrigerant passage 31 may be constructed outside of the evaporator 14 or may be constructed inside of the evaporator 14 .
  • a heat insulation material is used for the tube 17 a used as the liquid refrigerant passage 31 so that the liquid refrigerant is not evaporated while passing through the liquid refrigerant passage 31 .
  • the tubes 23 a of the condenser 15 are elongated approximately horizontally when being mounted on the vehicle. Even in this case, the refrigerant inside the tubes 23 a of the condenser 15 flows to the refrigerant downstream tank 25 by the pressure of the evaporated vapor refrigerant supplied from the refrigerant upstream tank 24 , so that condensed liquid refrigerant is collected to the refrigerant downstream tank 25 .
  • the waste heat recovery device 7 is provided with a flow limitation means such that coolant flows in a direction from the refrigerant condensation side (i.e., the side of the refrigerant downstream tank 25 ) toward the refrigerant un-condensation side (i.e., the side of the refrigerant upstream tank 24 ), similarly to the above-described first embodiment.
  • the coolant introducing pipe 21 is connected to the tank 13 at the side of the refrigerant downstream tank 25
  • the coolant discharge pipe 22 is connected to the tank 13 at the side of the refrigerant upstream tank 24 so as to form the flow limitation means.
  • the other parts may be made similar to those of the above-described first embodiment.
  • the differential pressure regulating valve 16 is used as one example of the operation stop means of the waste heat recovery device 7 , to open and close the communication passage through which the liquid refrigerant condensed in the condenser 15 flows to the evaporator 14 .
  • the differential pressure regulating valve 16 is not provided.
  • an operation stop means for stopping evaporation of the refrigerant in the evaporator 14 is constructed without using the differential pressure regulating means 16 .
  • a fluid control means for controlling a supply amount of exhaust gas (first fluid for heating) introduced to the evaporator 14 through the exhaust gas pipe 2 is provided so as to stop the evaporation of refrigerant in the evaporator 14 .
  • the fluid control means is a switching means for switching an exhaust passage through which the exhaust gas passes through the evaporator 14 .
  • the fluid control means By controlling the amount of the exhaust gas passing through the evaporator 14 to be heat exchanged with the refrigerant by using the fluid control means, the evaporation amount of the refrigerant in the evaporator 14 can be controlled.
  • the waste heat recovery device 7 is provided with a flow limitation means such that the coolant (second fluid to be heated) flows in a direction from the refrigerant condensation side (i.e., the side of the refrigerant downstream tank 25 ) toward the refrigerant un-condensation side (i.e., the side of the refrigerant upstream tank 24 ), similarly to the above-described first embodiment.
  • the coolant introducing pipe 21 is connected to the tank 13 at the side of the refrigerant downstream tank 25
  • the coolant discharge pipe 22 is connected to the tank 13 at the side of the refrigerant upstream tank 24 so as to form the flow limitation means.
  • the evaporator 14 and the condenser 15 are constructed of a drawn-cup heat exchanger.
  • the evaporator 14 and the condenser 15 may be constructed of the other type heat exchanger, for example, a laminated type heat exchanger and a header type heat exchanger.
  • the upper tank 19 of the evaporator 14 and the refrigerant upstream tank 24 of the condenser 15 are connected by a vapor refrigerant passage 32
  • the lower tank 18 of the evaporator 14 and the refrigerant downstream tank 25 of the condenser 15 are connected by a liquid refrigerant passage 31 .
  • the upper tank 19 of the evaporator 14 and the refrigerant upstream tank 24 of the condenser 15 may be directly connected
  • the lower tank 18 of the evaporator 14 and the refrigerant downstream tank 25 of the condenser 15 may be directly connected.
  • a throttle may be provided in a passage between the lower tank 18 of the evaporator 14 and the refrigerant downstream tank 25 of the condenser 15 .
  • the other parts may be made similar to those of the above-described first embodiment.
  • the differential pressure regulating valve 16 is used as an example of a switching valve (opening and closing valve).
  • a thermo valve for opening and closing its valve in accordance with a temperature of the coolant
  • an electrical valve e.g., electromagnetic valve
  • an operation state e.g., a detection value, a predetermined value
  • the switching valve (e.g., the differential pressure regulating valve 16 ) is disposed inside the refrigerant downstream tank 25 of the condenser 15 outside of the condenser 15 .
  • the switching valve may be located under the condenser 15 .
  • the switching valve is located to construct a part of the liquid refrigerant storage portion 29 , and the flow limitation means is constructed such that the coolant flows from a side of the switching valve to a side of the refrigerant downstream tank 25 of the condenser 15 .
  • the exhaust gas is used as an example of a heat source first fluid.
  • the other waste heat such as a battery waste heat, an inverter waste heat, and an intercooler waste heat may be used as the heat source first fluid.
  • the loop type heat pipe constructed with the evaporator 14 and the condenser 15 is typically used for a waste heat recovery device for a vehicle.
  • the loop type heat pipe of the present invention can be used for the other use for a fixed equipment, for example.
  • the exhaust gas of the engine is used as an example of a heat source fluid (first fluid), and the coolant is used as an example of a fluid to be heated (second fluid).
  • first fluid a heat source fluid
  • second fluid a fluid to be heated
  • any other heat source fluid may be used instead of the exhaust gas
  • any other fluid used for a thermal medium for a heater may be used as the fluid to be heated.
  • the refrigerant circulating between the evaporator 14 and the condenser 15 in the loop type heat pipe the other operation fluid may be suitably used.

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  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)
US11/818,257 2006-06-14 2007-06-13 Loop type heat pipe and waste heat recovery device Abandoned US20070289721A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006-165177 2006-06-14
JP2006165177A JP2007333293A (ja) 2006-06-14 2006-06-14 ループ式ヒートパイプ

Publications (1)

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US20070289721A1 true US20070289721A1 (en) 2007-12-20

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US (1) US20070289721A1 (ja)
JP (1) JP2007333293A (ja)
CN (1) CN100575854C (ja)
DE (1) DE102007027108A1 (ja)

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US20100077741A1 (en) * 2008-10-01 2010-04-01 Woodson Wayne Samuel Waste heat auxiliary power unit
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
US7891186B1 (en) * 2010-01-12 2011-02-22 Primlani Indru J System and method of waste heat recovery and utilization
US20130118423A1 (en) * 2011-11-08 2013-05-16 Behr Gmbh & Co. Kg Cooling circuit
US8714288B2 (en) 2011-02-17 2014-05-06 Toyota Motor Engineering & Manufacturing North America, Inc. Hybrid variant automobile drive
CN104456908A (zh) * 2013-09-12 2015-03-25 珠海格力电器股份有限公司 热交换设备及具有其的除湿机
US20150136381A1 (en) * 2012-04-23 2015-05-21 Toyota Jidosha Kabushiki Kaisha Heat transport device
US20160377352A1 (en) * 2014-03-19 2016-12-29 Areva Gmbh Passive two-phase cooling circuit
US20170181319A1 (en) * 2015-12-22 2017-06-22 Abb Technology Oy Cooling apparatus
US20170265330A1 (en) * 2015-02-09 2017-09-14 Fujitsu Limited Cooling apparatus and electronic device
US20180022188A1 (en) * 2016-07-19 2018-01-25 Honda Motor Co.,Ltd. Air conditioner for vehicle
WO2019056114A1 (en) * 2017-09-22 2019-03-28 Dana Canada Corporation LOCATED REINFORCEMENT FOR HEAT EXCHANGERS WITH STACKED STACKED SHEETS
US10845127B2 (en) 2015-03-06 2020-11-24 Kabushiki Kaisha Toshiba Cooling device
US10912222B2 (en) * 2017-04-05 2021-02-02 Fujitsu Limited Cooling system, cooling device, and electronic system
WO2023212978A1 (zh) * 2022-05-06 2023-11-09 天津大学滨海工业研究院有限公司 一种锅炉设备用余热回收装置

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JP5316452B2 (ja) * 2010-03-23 2013-10-16 株式会社デンソー 排気熱回収装置
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JP6341239B2 (ja) * 2016-08-05 2018-06-13 マツダ株式会社 エンジンの排熱回収装置
JP6733630B2 (ja) * 2017-09-13 2020-08-05 株式会社デンソー サーモサイフォン
CN109489303A (zh) * 2018-11-12 2019-03-19 北京工业大学 一种工质充注量可调的热泵/热管复合供热装置
JP2020106210A (ja) 2018-12-27 2020-07-09 川崎重工業株式会社 蒸発器及びループ型ヒートパイプ
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Family Cites Families (5)

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Publication number Priority date Publication date Assignee Title
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JPS59146203U (ja) * 1983-03-22 1984-09-29 日産自動車株式会社 車両用蓄熱式暖房装置
JPH0440969Y2 (ja) * 1989-03-02 1992-09-25
JPH02115015U (ja) * 1989-03-02 1990-09-14
JPH02310117A (ja) * 1989-05-24 1990-12-25 Nissan Motor Co Ltd 車両用暖房装置

Cited By (21)

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US20100077741A1 (en) * 2008-10-01 2010-04-01 Woodson Wayne Samuel Waste heat auxiliary power unit
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
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
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
US7891186B1 (en) * 2010-01-12 2011-02-22 Primlani Indru J System and method of waste heat recovery and utilization
US8714288B2 (en) 2011-02-17 2014-05-06 Toyota Motor Engineering & Manufacturing North America, Inc. Hybrid variant automobile drive
US20130118423A1 (en) * 2011-11-08 2013-05-16 Behr Gmbh & Co. Kg Cooling circuit
US8985066B2 (en) * 2011-11-08 2015-03-24 Behr Gmbh & Co. Kg Cooling circuit
US20150136381A1 (en) * 2012-04-23 2015-05-21 Toyota Jidosha Kabushiki Kaisha Heat transport device
CN104456908A (zh) * 2013-09-12 2015-03-25 珠海格力电器股份有限公司 热交换设备及具有其的除湿机
US20160377352A1 (en) * 2014-03-19 2016-12-29 Areva Gmbh Passive two-phase cooling circuit
US9874406B2 (en) * 2014-03-19 2018-01-23 Areva Gmbh Passive two-phase cooling circuit
US20170265330A1 (en) * 2015-02-09 2017-09-14 Fujitsu Limited Cooling apparatus and electronic device
US10123457B2 (en) * 2015-02-09 2018-11-06 Fujitsu Limited Cooling apparatus and electronic device
US10845127B2 (en) 2015-03-06 2020-11-24 Kabushiki Kaisha Toshiba Cooling device
US20170181319A1 (en) * 2015-12-22 2017-06-22 Abb Technology Oy Cooling apparatus
US20180022188A1 (en) * 2016-07-19 2018-01-25 Honda Motor Co.,Ltd. Air conditioner for vehicle
US10912222B2 (en) * 2017-04-05 2021-02-02 Fujitsu Limited Cooling system, cooling device, and electronic system
WO2019056114A1 (en) * 2017-09-22 2019-03-28 Dana Canada Corporation LOCATED REINFORCEMENT FOR HEAT EXCHANGERS WITH STACKED STACKED SHEETS
WO2023212978A1 (zh) * 2022-05-06 2023-11-09 天津大学滨海工业研究院有限公司 一种锅炉设备用余热回收装置

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DE102007027108A1 (de) 2008-02-14
CN100575854C (zh) 2009-12-30
CN101089540A (zh) 2007-12-19
JP2007333293A (ja) 2007-12-27

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