US20100282445A1 - Heat pipe, exhaust heat recoverer provided therewith - Google Patents
Heat pipe, exhaust heat recoverer provided therewith Download PDFInfo
- Publication number
- US20100282445A1 US20100282445A1 US12/743,925 US74392508A US2010282445A1 US 20100282445 A1 US20100282445 A1 US 20100282445A1 US 74392508 A US74392508 A US 74392508A US 2010282445 A1 US2010282445 A1 US 2010282445A1
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- US
- United States
- Prior art keywords
- heat pipe
- unit side
- side heat
- heating unit
- evaporation unit
- 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
Links
- 238000001704 evaporation Methods 0.000 claims abstract description 157
- 230000008020 evaporation Effects 0.000 claims abstract description 154
- 238000010438 heat treatment Methods 0.000 claims abstract description 118
- 239000012530 fluid Substances 0.000 claims description 67
- 238000009833 condensation Methods 0.000 claims description 31
- 230000005494 condensation Effects 0.000 claims description 31
- 239000012808 vapor phase Substances 0.000 claims description 26
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 abstract description 87
- 230000000979 retarding effect Effects 0.000 abstract description 6
- 239000000498 cooling water Substances 0.000 description 16
- 238000010792 warming Methods 0.000 description 14
- 239000007791 liquid phase Substances 0.000 description 12
- 238000011144 upstream manufacturing Methods 0.000 description 7
- 230000000717 retained effect Effects 0.000 description 6
- 238000005192 partition Methods 0.000 description 5
- 230000007423 decrease Effects 0.000 description 4
- 230000003247 decreasing effect Effects 0.000 description 3
- 230000002093 peripheral effect Effects 0.000 description 3
- 239000000470 constituent Substances 0.000 description 2
- 150000001298 alcohols Chemical class 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000003197 catalytic effect Effects 0.000 description 1
- 230000007797 corrosion Effects 0.000 description 1
- 238000005260 corrosion Methods 0.000 description 1
- 239000013529 heat transfer fluid Substances 0.000 description 1
- 239000010705 motor oil Substances 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 238000003303 reheating Methods 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
- 239000010935 stainless steel Substances 0.000 description 1
Images
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 from exhaust energy
- F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting from exhaust energy the devices using heat
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
-
- 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 invention relates to a heat pipe used in a vehicle such as an automobile, an exhaust heat recoverer provided therewith.
- a conventional example of the related art uses the principle of a heat pipe to recover exhaust heat of exhaust gas discharged from an engine of a vehicle and use this exhaust heat to promote engine warming and the like.
- a loop heat pipe heat exchanger has been proposed that utilizes the principle of a heat pipe (see, for example, Japanese Patent Application Publication No. 4-45393 (JP-A-4-45393)).
- This heat exchanger has a closed circulation path that forms a closed loop, a working fluid charged into the circulation path enabling evaporation and condensation, an evaporation unit arranged in the circulation path that evaporates the working fluid by introducing heat from the outside, and a condensation unit arranged at a higher location than the evaporation unit of the circulation path that carries out heat exchange between the working fluid evaporated in the evaporation unit and a heat transfer fluid from the outside.
- an exhaust heat recoverer in order to install on a vehicle, the structure of an exhaust heat recoverer is required to be compactly designed. Consequently, in the case of using a loop heat pipe heat exchanger as an exhaust heat recoverer, a configuration is preferably employed as shown in FIG. 5 having a plurality of heat pipes c, a heating unit a that heats a working fluid using the heat of exhaust gas, and an evaporation unit b that evaporates the working fluid heated by this heating unit a using the heat of exhaust gas, arranged in parallel in the horizontal direction, and headers d 1 and d 2 (connecting portions) respectively connecting both ends in the vertical direction of each heat pipe c.
- the header d 2 on the side of the evaporation unit b of each heat pipe c (top of FIG. 5 ) is connected to a condensation unit so that the evaporated working fluid is subjected to heat exchange with a target of promotion of warming, while the header d 1 on the side of the heating unit a of each heat pipe c (bottom of FIG. 5 ) is connected to the condensation unit so that working fluid that has been condensed by heat exchange with the target of promotion of warming is returned.
- an exhaust heat recoverer configured in this manner still has the problems described below. Namely, since the heat pipes c employ the same shape for the heating unit a side thereof and the evaporation unit b side thereof, or in other words, a heat pipe portion c 1 on the side of the heating unit and a heat pipe portion c 2 on the side of the evaporation unit mutually form a pair and are formed to the same shape, when working fluid heated in the heat pipe portion c 1 on the heating unit side is transformed to a vapor phase and expands in volume during evaporation in the heat pipe section c 2 on the side of the evaporation unit, the pressure of the working fluid increases accompanying this expansion in volume, and causing the working fluid to be sent to the condensation unit by passing through the inside of the heat pipe section c 2 on the evaporation unit side at a rapid flow rate.
- the heat of the exhaust gas has difficulty in acting on the vapor phase working fluid, thereby preventing the vapor phase working fluid in the heat pipe portion c 2 on the side of the evaporation unit from being reheated by heat from the exhaust gas.
- heat of the working fluid is lost directly as a result of the vapor phase working fluid contacting, for example, the cold peripheral walls of the condensation unit, thereby preventing heat exchange with the target of promotion of warming from being carried out efficiently.
- the invention provides a heat pipe capable of enabling heat exchange with a target of promotion of warming, such as during cold starting, to be carried out efficiently by adequately reheating an evaporated, vapor phase working fluid using heat of exhaust gas, an exhaust heat recoverer provided therewith.
- a first aspect of the invention relates to a heat pipe provided with a heating unit that is provided with a heating unit side heat pipe portion that heats a working fluid using heat of exhaust gas discharged from an engine, an evaporation unit that is provided with an evaporation unit side heat pipe portion through which the working fluid flows, and that evaporates the working fluid heated by the heating unit using the heat of the exhaust gas, and flow rate retardation means for retarding the flow rate of the working fluid flowing into the evaporation unit side heat pipe portion.
- the heating unit side heat pipe portion may be provided in plurality, and the flow rate retardation means may be provided with a merging portion that merges the working fluid respectively heated by the plurality of heating unit side heat pipe portions, on the evaporation unit side.
- the cross-sectional area of a flow path orthogonal to the vertical direction of the merging portion may be set to be larger than the cross-sectional area of a flow path orthogonal to the vertical direction of the plurality of evaporation unit side heat pipe portions.
- the cross-sectional area of a flow path orthogonal to the vertical direction of the merging portion may be set to be larger than the cross-sectional area of a flow path orthogonal to the vertical direction of the evaporation unit side heat pipe portion.
- the heat pipe according to this first aspect may be provided with throttling means which is provided between the merging portion and the evaporation unit side heat pipe portion and which restricts the cross-sectional area of the flow path orthogonal to the vertical direction.
- throttling means which is provided between the merging portion and the evaporation unit side heat pipe portion and which restricts the cross-sectional area of the flow path orthogonal to the vertical direction.
- the heat pipe according to this first aspect may be provided near the center of the exhaust pipe.
- the heat of exhaust gas near the center of the exhaust pipe where the temperature within the exhaust pipe is the highest acts on the working fluid inside the merging portion, and the heat of exhaust gas is efficiently imparted to the working fluid retained in the merging portion.
- the vapor phase working fluid evaporated in the merging portion on the side of the evaporation unit is efficiently heated by the heat of high-temperature exhaust gas near the center of the exhaust pipe to ensure an adequate amount of heat.
- the cross-section of the merging portion orthogonal to the direction of flow of the exhaust gas may be in the shape of a semicircular arc.
- the working fluid further heated by the evaporation unit may be a vapor phase working fluid.
- the evaporation unit may be arranged higher than the heating unit in the vertical direction.
- a second aspect of the invention relates to an exhaust heat recoverer that is provided with the heat pipe according to the first aspect, and a condensation unit into which is introduced the working fluid evaporated in the evaporation unit and in which the introduced working fluid is cooled.
- a third aspect of the invention relates to an exhaust heat recoverer comprising a heat pipe including a heating unit for heating a working fluid using heat of exhaust gas discharged from an engine, and an evaporation unit that is provided with an evaporation unit side heat pipe portion through which the working fluid flows, and that evaporates the working fluid heated by the heating unit using the heat of the exhaust gas.
- the heat pipe is provided with flow rate retardation means for retarding the flow rate of the working fluid flowing through the evaporation unit side heat pipe portion.
- FIG. 1 is a perspective view showing an exhaust heat recoverer as claimed in a first embodiment of the invention applied to an exhaust pipe of an automobile;
- FIG. 2 is a longitudinal cross-sectional side view of the same exhaust heat recoverer applied to the exhaust pipe of an automobile;
- FIG. 3 is a longitudinal cross-sectional front view of the same exhaust heat recoverer as viewed from the axial direction of an exhaust pipe;
- FIG. 4 is a longitudinal cross-sectional front view of an exhaust heat recoverer as claimed in a second embodiment of the invention as viewed from the axial direction of an exhaust pipe;
- FIG. 5 is a longitudinal cross-sectional front view of an exhaust heat recoverer as claimed in the related art as viewed from the axial direction of an exhaust pipe.
- FIGS. 1 and 2 show an exhaust pipe of an automobile in which is applied an exhaust heat recoverer as claimed in a first embodiment of the invention, and an exhaust heat recoverer 2 is provided at an intermediate location in this exhaust pipe 1 .
- the exhaust pipe 1 is divided at the exhaust gas recoverer 2 into an upstream exhaust pipe path 11 and a downstream exhaust pipe path 12 , and while the upstream side in the direction of exhaust gas flow of an evaporation side case 25 (to be described later) of the exhaust heat recoverer 2 is connected to the upstream exhaust pipe path 11 , the downstream side in the direction of exhaust gas flow of the evaporation side case 25 is connected to the downstream side exhaust pipe path 12 .
- a catalytic converter is provided on the upstream side of the upstream side exhaust pipe path 11 (farther upstream than the exhaust heat recoverer 2 ).
- a muffler is provided on the downstream side of the downstream side exhaust pipe path 12 (farther downstream than the exhaust heat recoverer 2 ).
- the exhaust heat recoverer 2 is provided with a heat pipe 23 having a heating unit 21 and an evaporation unit 22 , and a condensation unit 24 .
- the heat pipe 23 allows the passage there through of a working fluid in the form of pure water, and is housed within the evaporation side case 25 roughly in the shape of a rectangular frame.
- the central portion of the evaporation side case 25 in which this heat pipe 23 is located is arranged so as to face the inside of the exhaust pipe 1 .
- the heat pipe 23 is provided with a plurality of heating unit side heat pipe portions 23 a on the side of the heating unit 21 that heats pure water with the heat of the exhaust gas (bottom of FIG. 3 ), and a plurality of evaporation unit side heat pipe portions 23 b on the side of the evaporation unit 22 that evaporates the pure water heated by the heating unit side heat pipe portions 23 a (top of FIG. 3 ).
- each heating unit side heat pipe portion 23 a and each evaporation unit side heat pipe portion 23 b has a prescribed length (of about, for example, 60 mm) in the direction of flow of the exhaust gas flowing through the exhaust pipe 1 , and are provided extending in the vertical direction at prescribed intervals in the left and right directions, respectively, on the side of the heating unit 21 and the side of the evaporation unit 22 within the evaporation side case 25 .
- the condensation unit 24 has the shape of an enclosed tank, and is arranged outside the exhaust pipe 1 .
- An inlet port 31 and an outlet port 32 of a cooling water path 3 which circulates engine cooling water of an automobile, are connected to the condensation unit 24 .
- the condensation unit 24 and the evaporation side case 25 are linked through upper and lower communication paths 26 a and 26 b , and vapor phase pure water, or water vapor, evaporated by the heat pipe 23 of the evaporation side case 25 (heating unit side heat pipe portions 23 a and evaporation unit side heat pipe portions 23 b ), is introduced into the condensation unit 24 through the upper communication path 26 a .
- a water vapor layer 251 where water vapor evaporated by the heat pipe 23 merges, is provided in the upper end of the evaporation side case 25 , and an upper end of each evaporation unit side heat pipe portion 23 b of the heat pipe 23 is fit and inserted into the lower surface of this water vapor layer 251 .
- an intake portion 252 into which liquid phase pure water accumulated in a reservoir portion 27 to be described later is introduced, is provided in the lower end of the evaporation side case 25 , and the lower end of each heating unit side heat pipe portion 23 a of the heat pipe 23 is fit and inserted into the upper surface of this intake portion 252 .
- each heating unit side heat pipe portion 23 a and each evaporation unit side heat pipe portion 23 b are formed to respectively have the same diameter.
- the condensation unit 24 is divided into a two-layer structure by a partition 241 , and carries out heat exchange between engine cooling water, introduced from the inlet port 31 of the cooling water path 3 on the side of an outer layer 241 a to the outside of this partition 241 , and water vapor introduced from the water vapor layer 251 on the side of an inner layer 241 b to the inside of the partition 241 , thereby resulting in condensation of water vapor from which heat has been lost due to heat exchange with the engine cooling water from the vapor phase to the liquid phase of pure water.
- Engine cooling water that has undergone heat exchange with water vapor in the condensation unit 24 flows out from the side of the outer layer 241 a of the condensation unit 24 through the outlet port 32 of the cooling water path 3 .
- the inlet port 31 of the cooling water path 3 is located on the side of the water vapor layer 251 on the side of the outer layer 241 a of the condensation unit 24 , and heat of the high-temperature water vapor immediately after being introduced from the water vapor layer 251 is imparted thereto.
- the reservoir portion 27 is provided on the lower surface of the condensation unit 24 , and pure water that has entered the liquid phase as a result of heat exchange with engine cooling water in the condensation unit 24 moves from the condensation unit 24 into the reservoir portion 27 and is accumulated therein. Liquid phase pure water that has accumulated in the reservoir portion 27 is returned to the evaporation side case 25 through the lower communication path 26 b .
- a valve 271 for controlling the return the return of liquid phase pure water to the reservoir portion 27 in the lower portion of the evaporation side case 25 is provided at the connection with the lower communication path 26 b of the reservoir portion 27 .
- This valve 271 is opened and closed by an operating portion 272 activated by negative pressure from the engine side, and as a result of being closed by the operation of the operating portion 272 such as at completion of warming when heat exchange with engine cooling water in the condensation unit 24 is no longer required, the movement of the pure water (water vapor) is controlled to allow the heat load to dissipate to a radiator.
- the pure water used for the working fluid of the exhaust heat recoverer 2 is sealed while maintaining a vacuum (reduced pressure) in the heat pipe 23 (heating unit side heat pipe portions 23 a and evaporation unit side heat pipe portions 23 b ), the condensation unit 24 , the reservoir portion 27 and the upper and lower communication paths 26 a and 26 b .
- the heat pipe 23 , condensation unit 24 , reservoir portion 27 and upper and lower communication paths 26 a and 26 b are composed of stainless steel having high resistance to corrosion.
- Flow rate retardation means 4 for retarding the flow rate of vapor phase pure water (water vapor) flowing in the form of water vapor through each of the evaporation unit side heat pipe portions 23 b , is provided on the side of the evaporation unit 22 of the heat pipe 23 .
- This flow rate retardation means 24 is provided with a merging portion 23 c that merges pure water respectively heated by each heating unit side heat pipe portion 23 a on the side of the evaporation unit 22 .
- the upper end of each heating unit side heat pipe portion 23 a is respectively connected to the lower end of this merging portion 23 c .
- each evaporation unit side heat pipe portion 23 b is respectively connected to the upper end of the merging portion 23 c located between mutually adjacent heating unit side heat pipe portions 23 a , and is connected to the lower end of the water vapor phase 251 by extending upward in the vertical direction.
- corrugated fins 23 d are joined between the evaporation side case 25 and the heating unit side heat pipe portions 23 a and the evaporation unit side heat pipe portions 23 b adjacent thereto, between mutually adjacent heating unit side heat pipe portions 23 a , and between mutually adjacent evaporation unit side heat pipe portions 23 b , and the corrugated fins 23 d promote heat exchange between pure water and exhaust gas by increasing the heat transfer areas of the evaporation unit side and heating unit side heat pipe portions 23 a and 23 b .
- the merging portion 23 c is provided extending in roughly the horizontal direction (roughly horizontal direction orthogonal to the axis of the exhaust pipe) near the center of the exhaust pipe 1 . In this case, the diagonal lines shown in FIG.
- the merging portion 23 c not only merges pure water heated within each of the heating unit side heat pipe portions 23 a , but rather when heat exchange with pure water is promoted due to increase in the amount of heat of the exhaust gas, also merges water vapor evaporated as a result of heating proceeding to the inside of each of the heating unit side heat pipe portions 23 a.
- merging portion 23 c on the side of the evaporation unit 22 is set to have a flow path cross-sectional area larger than the flow path cross-sectional area in each heating unit side heat pipe portion 23 a .
- merging portion 23 c is continuously provided extending between heating unit side heat pipe portions 23 a on one side in the horizontal direction orthogonal to the direction of flow of exhaust gas (left edge of FIG. 3 ) and heating unit side heat pipe portions 23 a on the other side in the horizontal direction orthogonal to the direction of flow of exhaust gas (right edge of FIG.
- the cross-sectional area of the flow path orthogonal to the vertical direction of the merging portion 23 c is set to be larger than the total cross-sectional area of the flow paths orthogonal to the vertical direction of each heating unit side heat pipe portion 23 a of which seven are intermittently provided in the horizontal direction orthogonal to the direction of flow of exhaust gas.
- the merging portion 23 c on the side of the evaporation unit 22 is set to have a flow path cross-sectional area larger than the flow path cross-sectional area of each evaporation unit side heat pipe portion 23 b .
- six evaporation unit side heat pipe portions 23 b are arranged in the horizontal direction orthogonal to the direction of flow of exhaust gas, and as a result thereof, the flow path cross-sectional area of the merging portion 23 c continuously provided extending between the heating unit side heat pipe portions 23 a on both one side and the other side in the horizontal direction orthogonal to the direction of flow of exhaust gas is set to be larger than the total flow path cross-sectional area of each evaporation unit side heat pipe portion 23 b of which six are intermittently provided in the horizontal direction orthogonal to the direction of flow of exhaust gas.
- the total cross-sectional area of flow paths orthogonal to the vertical direction of each of the heating unit side heat pipe portions 23 a is set to be larger than the total cross-sectional area of flow paths orthogonal to the vertical direction of each of the evaporation unit side heat pipe portions 23 b.
- each heating unit side heat pipe portion 23 a is respectively connected to the intake portion 252 on the lower end of the evaporation side case 25 , and the upper end thereof is connected to the lower end of the merging portion 23 c by extending upward in the vertical direction.
- the lower end of each evaporation unit side heat pipe portion 23 b is respectively connected to the merging portion 23 c located between mutually adjacent heating unit side heat pipe portions 23 a , and the upper end thereof is connected to the lower end of the water vapor phase 251 on the upper end of the evaporation side case 25 by extending upward in the vertical direction.
- the heat pipe 23 causes the flow rate of pure water flowing through each of the heating unit side heat pipe portions 23 a to be retarded in the merging portion 23 c on the side of the evaporation unit 22 by the flow rate retardation means 4 provided with the merging portion 23 c that merges pure water respectively heated by the seven heating unit side heat pipe portions 23 a on the side of the heating unit 21 to the side of the evaporation unit 22 .
- the flow path cross-sectional area of the merging portion 23 c is provided to be larger than the flow path cross-sectional area of each evaporation unit side heat pipe portion 23 b , pure water that has merged from each heating unit side heat pipe portion 23 a into the merging portion 23 c resists being rapidly introduced into each evaporation unit side heat pipe portion 23 b having a small flow path cross-sectional area, thereby causing the flow rate of pure water to temporarily decrease in the merging portion 23 c .
- the heat of exhaust gas easily acts on pure water for which the flow rate thereof has been retarded in the merging portion 23 c on the side of the evaporation unit 22 , and water vapor (vapor phase pure water) evaporated in the merging portion 23 c on the side of the evaporation unit 22 is adequately reheated by the heat of the exhaust gas, thereby ensuring an adequate amount of heat.
- heat exchange with engine cooling water can be carried out efficiently by avoiding the heat of the water vapor being lost directly due to contact with the cold partition 241 and the like of the condensation unit 24 , particularly during cold starting when promotion of warming is required.
- the merging portion 23 c of the evaporation unit 22 is provided extending in the horizontal direction near the center of the exhaust pipe 1 , the heat of the exhaust gas that reaches the highest temperature near the center of the exhaust pipe 1 can be efficiently imparted to the pure water retained in the merging portion 23 c , which is extremely advantageous in terms of improving the efficiency of heat exchange with engine cooling water.
- each of the heating unit side heat pipe portions 23 a is set to be larger than the total flow path circumferential cross-sectional area of each of the evaporation unit side heat pipe portions 23 b , the heat of exhaust gas aggressively and effectively acts on liquid phase pure water in each of the heating unit side heat pipe portions 23 a due to the large flow path circumferential cross-sectional area thereof, thereby making it possible to efficiently heat the liquid phase pure water in each of the heating unit side heat pipe portions 23 a.
- a heat pipe 28 allows the flow of a working fluid in the form of pure water there through, and is housed within the evaporation side case 25 in the shape of a rectangular frame.
- a central portion of the evaporation side case 25 in which this heat pipe 28 is located is arranged so as to face an inside of the exhaust pipe 1 .
- the heat pipe 28 is provided with a plurality of heating unit side heat pipe portions 28 a on the side of the heating unit 21 (bottom of FIG. 4 ) that heats pure water with heat of exhaust gas, and a plurality of evaporation unit side heat pipe portions 28 b on the side of the evaporation unit 22 (top of FIG. 4 ) that evaporates pure water heated by the heating unit side heat pipe portions 28 a .
- This heat pipe 28 carries out heat exchange between pure water flowing through the inside of each heating unit side heat pipe portion 28 a and each evaporation unit side heat pipe portion 28 b , and exhaust gas discharged from an engine, thereby evaporating the pure water by heating.
- each of the heating unit side heat pipe portions 28 a and each of the evaporation unit side heat pipe portions 28 b are provided within the evaporation side case 25 extending in the vertical direction at prescribed intervals in the left and right directions, respectively.
- the heat pipe 28 is provided with flow rate retardation means 5 for retarding the flow rate of vapor phase pure water (water vapor) flowing in the form of water vapor through each of the evaporation unit side heat pipe portions 28 b .
- This flow rate retardation means 5 is provided with merging portions 28 c having a roughly semi-circular cross-section orthogonal to the direction of flow of the exhaust gas that cause pure water respectively heated by each of the heating unit side heat pipe portions 28 a to merge onto the side of the evaporation unit 22 .
- corrugated fins 28 d are joined between the evaporation side case 25 and the heating unit side heat pipe portions 28 a and the evaporation unit side heat pipe portions 28 b adjacent thereto, between mutually adjacent heating unit side heat pipe portions 28 a , and between mutually adjacent evaporation unit side heat pipe portions 28 b , and the corrugated fins 28 d promote heat exchange between pure water and exhaust gas by increasing the heat transfer area of the heat pipe 28 .
- Each merging portion 28 c is provided arranged in rows at prescribed intervals in respectively roughly the horizontal direction (roughly horizontal direction orthogonal to the axis of the exhaust pipe) near the center of the exhaust pipe 1 .
- the diagonal lines shown in the heat pipe 28 in FIG. 4 indicate liquid phase pure water, while the dots indicate water vapor (vapor phase pure water).
- each merging portion 28 c on the side of the evaporation unit 22 is set to have a flow path cross-sectional area larger than the flow path cross-sectional area of each heating unit side heat pipe portion 28 a .
- each merging portion 28 c is provided continuously extending between the two heating unit side heat pipe portions 28 a , and as a result, the flow path cross-sectional area of the merging portions 28 c is set to be larger than the total flow path cross-sectional area of each of the two heating unit side heat pipe portions 28 a provided intermittently in the horizontal direction orthogonal to the direction of flow of exhaust gas.
- each merging portion 28 c on the side of the evaporation unit 22 is set to have a flow path cross-sectional area larger than the flow path cross-sectional area of each of the evaporation unit side heat pipe portion 28 b .
- the flow path cross-sectional area of the merging portion 28 c provided continuously extending between two heating unit side heat pipe portions 28 a is set to be larger than the flow path cross-sectional area of a single evaporation unit side heat pipe portion 28 b connected to the upper end of this merging portion 28 c .
- the total flow path cross-sectional area of the two heating unit side heat pipe portions 28 a is set to be twice as large as the flow path cross-sectional area of the single evaporation unit side heat pipe portion 28 b.
- each group of two heating unit side heat pipe portions 28 a are respectively connected to the intake portion 252 on the lower end of the evaporation side case 25 , and the upper ends thereof are connected to the lower ends of the merging portions 28 c by extending upward in the vertical direction.
- the lower end of each evaporation unit side heat pipe portion 28 b is respectively connected to the upper end of the merging portion 28 c located between a group of two heating unit side heat pipe portions 28 a , and the upper end thereof is connected to the lower end of the water vapor layer 251 on the upper end of the evaporation side case 25 by extending upward in the vertical direction.
- three evaporation unit side heat pipe portions 28 b are arranged on the side of the evaporation unit 22 .
- the heat pipe 28 retards the flow rate of pure water passing through each of the heating unit side heat pipe portions 28 a in each of the merging portions 28 c on the side of the evaporation unit 22 by the flow rate retardation means 5 provided with the merging portions 28 c merging pure water respectively heated by each group of two heating unit side heat pipe portions 28 a on the side of the heating unit 21 to the side of the evaporation unit 22 .
- each merging portion 28 c is set to be larger than the flow path cross-sectional area of a single evaporation unit side heat pipe portion 28 b , pure water that has merged from each heating unit side heat pipe portion 28 a into each merging portion 28 c resists being rapidly introduced into each evaporation unit side heat pipe portion 28 b having a small flow path cross-sectional area, thereby causing the flow rate of pure water to temporarily decrease in the merging portions 28 c .
- the heat of exhaust gas easily acts on pure water for which the flow rate thereof has been retarded in each merging portion 28 c on the side of the evaporation unit 22 , and water vapor (vapor phase pure water) evaporated in each merging portion 28 c on the side of the evaporation unit 22 is adequately reheated by the heat of the exhaust gas, thereby ensuring an adequate amount of heat.
- heat exchange with engine cooling water can be carried out efficiently by avoiding the heat of the water vapor being lost directly due to contact with the cold partition 241 and the like of the condensation unit 24 , particularly during cold starting when promotion of warming is required.
- each merging portion 28 c of the evaporation unit 22 is provided extending in the horizontal direction near the center of the exhaust pipe 1 , the heat of the exhaust gas that reaches the highest temperature near the center of the exhaust pipe 1 can be efficiently imparted to the pure water retained in each merging portion 28 c , which is extremely advantageous in terms of improving the efficiency of heat exchange with engine cooling water.
- each of the six heating unit side heat pipe portions 28 a is set to be larger than the total flow path cross-sectional area of each of the three evaporation unit side heat pipe portions 28 b , the heat of exhaust gas aggressively and effectively acts on liquid phase pure water in each of the heating unit side heat pipe portions 28 a due to the large flow path cross-sectional area thereof, thereby making it possible to efficiently heat the liquid phase pure water in each of the heating unit side heat pipe portions 28 a.
- the invention is not limited to the each of the above-mentioned embodiments, but rather includes various other variations thereof.
- the flow path cross-sectional areas of the merging portions 23 c and 28 c on the side of the evaporation unit 22 is set to be larger than the flow path cross-sectional areas of each of the evaporation unit side heat pipe portions 23 b and 28 b in each of the embodiments
- throttling means may be provided between the merging portion and the evaporation unit side heat pipe portions, namely on the downstream side of the merging portion on the side of the evaporation unit 22 or on the upstream side of each evaporation unit side heat pipe portion, that restricts flow path cross-sectional area.
- working fluid that has merged from each heating unit side heat pipe portion into the merging portion further resists being introduced into the evaporation unit side heat pipe portion having a restricted flow path cross-sectional area, and the heat of exhaust gas acts even more reliably on working fluid for which the flow rate thereof has been further decreased in the merging portion.
- each of the evaporation unit side heat pipe portions 23 b and each of the heating unit side heat pipe portions 23 a are respectively formed to the same diameter
- the number of the evaporation unit side heat pipe portions 23 b is one fewer than the number of the heating unit side heat pipe portions 23 a , namely six, and therefore the total flow path cross-sectional area of the six evaporation unit side heat pipe portions 23 b is set to be smaller than the total flow path cross-sectional area of the seven heating unit side heat pipe portions 23 a
- the total flow path cross-sectional area of each of the evaporation unit side heat pipe portions is set to be smaller than the total flow path cross-sectional area of each of the heating unit side heat pipe portions, it is not necessary for each of the evaporation unit side heat pipe portions and each of the heating unit side heat pipe portions to respectively have the same diameter, and the difference in the numbers of evaporation unit side heat pipe portions and heating unit side heat pipe portions
- each of the evaporation unit side heat pipe portions 28 b and each of the heating unit side heat pipe portions 28 a are respectively formed to the same diameter, and the upper ends of each group of two heating unit side heat pipe portions 28 a are connected to the lower end of a single evaporation unit side heat pipe portion 28 b through the merging portions 28 c , and therefore the flow path cross-sectional area of a single evaporation unit side heat pipe portion 28 b is set to be roughly half the total flow path cross-sectional area of each group of two heating unit side heat pipe portions 28 a , if the total flow path cross-sectional area of the evaporation unit side heat pipe portion is set to be smaller than the total flow path cross-sectional area of the heating unit side heat pipe portions, it is not necessary for each evaporation unit side heat pipe portion and each heating unit side heat pipe portion to be respectively formed to the same diameter, and the difference in the numbers of evaporation unit side heat pipe portions and heating unit side heat pipe portions
- valve 271 for controlling the return of liquid phase pure water to the reservoir portion 27 is provided in the connection with the lower communication path 26 b of the reservoir portion 27 in the embodiments, the location at which this valve is provided is not limited thereto, but rather it may be provided at any location provided the movement of water vapor to the condensation unit is controlled when the valve is closed such as at completion of warming when heat exchange with engine cooling water is no longer necessary in the condensation unit.
- engine cooling water is applied as the target of heat exchange that carries out heat exchange with exhaust gas in the exhaust heat recoverer 2 in the embodiments
- engine oil or transmission oil and the like may also be a target of heat exchange.
- working fluids other then water, such as alcohols or fluorocarbons, may also be applied.
Abstract
A heat pipe 23 has seven heating unit side heat pipe portions 23 a on the side of a heating unit 21 for heating pure water using heat of exhaust gas discharged from an engine, six evaporation unit side heat pipe portions 23 b on the side of an evaporation unit 22 for evaporating the pure water heated by each heating unit side heat pipe portion 23 a using heat of exhaust gas, and flow rate retardation means 4 for retarding the flow rate of the pure water flowing in the evaporation unit side heat pipe portions. The flow rate retardation means 4 is provided with a merging portion 23 c that merges the pure water heated by each heating unit side heat pipe portion, on the evaporation unit side, and whose a flow path cross-sectional area is set to be larger than that of each heating unit side heat pipe portion 23 a.
Description
- 1. Field of the Invention
- The invention relates to a heat pipe used in a vehicle such as an automobile, an exhaust heat recoverer provided therewith.
- 2. Description of the Related Art
- A conventional example of the related art uses the principle of a heat pipe to recover exhaust heat of exhaust gas discharged from an engine of a vehicle and use this exhaust heat to promote engine warming and the like.
- In addition, a loop heat pipe heat exchanger has been proposed that utilizes the principle of a heat pipe (see, for example, Japanese Patent Application Publication No. 4-45393 (JP-A-4-45393)). This heat exchanger has a closed circulation path that forms a closed loop, a working fluid charged into the circulation path enabling evaporation and condensation, an evaporation unit arranged in the circulation path that evaporates the working fluid by introducing heat from the outside, and a condensation unit arranged at a higher location than the evaporation unit of the circulation path that carries out heat exchange between the working fluid evaporated in the evaporation unit and a heat transfer fluid from the outside.
- However, in order to install on a vehicle, the structure of an exhaust heat recoverer is required to be compactly designed. Consequently, in the case of using a loop heat pipe heat exchanger as an exhaust heat recoverer, a configuration is preferably employed as shown in
FIG. 5 having a plurality of heat pipes c, a heating unit a that heats a working fluid using the heat of exhaust gas, and an evaporation unit b that evaporates the working fluid heated by this heating unit a using the heat of exhaust gas, arranged in parallel in the horizontal direction, and headers d1 and d2 (connecting portions) respectively connecting both ends in the vertical direction of each heat pipe c. In this case, the header d2 on the side of the evaporation unit b of each heat pipe c (top of FIG. 5) is connected to a condensation unit so that the evaporated working fluid is subjected to heat exchange with a target of promotion of warming, while the header d1 on the side of the heating unit a of each heat pipe c (bottom ofFIG. 5 ) is connected to the condensation unit so that working fluid that has been condensed by heat exchange with the target of promotion of warming is returned. - However, an exhaust heat recoverer configured in this manner still has the problems described below. Namely, since the heat pipes c employ the same shape for the heating unit a side thereof and the evaporation unit b side thereof, or in other words, a heat pipe portion c1 on the side of the heating unit and a heat pipe portion c2 on the side of the evaporation unit mutually form a pair and are formed to the same shape, when working fluid heated in the heat pipe portion c1 on the heating unit side is transformed to a vapor phase and expands in volume during evaporation in the heat pipe section c2 on the side of the evaporation unit, the pressure of the working fluid increases accompanying this expansion in volume, and causing the working fluid to be sent to the condensation unit by passing through the inside of the heat pipe section c2 on the evaporation unit side at a rapid flow rate. Consequently, despite the vapor phase working fluid evaporated in the heat pipe section c2 on the side of the evaporator being exposed to heat of the exhaust gas, the heat of the exhaust gas has difficulty in acting on the vapor phase working fluid, thereby preventing the vapor phase working fluid in the heat pipe portion c2 on the side of the evaporation unit from being reheated by heat from the exhaust gas. As a result, during cold starting and the like when promotion of warming is particularly required, heat of the working fluid is lost directly as a result of the vapor phase working fluid contacting, for example, the cold peripheral walls of the condensation unit, thereby preventing heat exchange with the target of promotion of warming from being carried out efficiently.
- The invention provides a heat pipe capable of enabling heat exchange with a target of promotion of warming, such as during cold starting, to be carried out efficiently by adequately reheating an evaporated, vapor phase working fluid using heat of exhaust gas, an exhaust heat recoverer provided therewith.
- A first aspect of the invention relates to a heat pipe provided with a heating unit that is provided with a heating unit side heat pipe portion that heats a working fluid using heat of exhaust gas discharged from an engine, an evaporation unit that is provided with an evaporation unit side heat pipe portion through which the working fluid flows, and that evaporates the working fluid heated by the heating unit using the heat of the exhaust gas, and flow rate retardation means for retarding the flow rate of the working fluid flowing into the evaporation unit side heat pipe portion.
- In the heat pipe according to this first aspect, the heating unit side heat pipe portion may be provided in plurality, and the flow rate retardation means may be provided with a merging portion that merges the working fluid respectively heated by the plurality of heating unit side heat pipe portions, on the evaporation unit side.
- As a result of employing this configuration, the working fluid merged from each heating unit side heat pipe portion is retained in the merging portion resulting in retardation of the flow rate thereof. As a result, the heat of exhaust gas is able to easily act on the working fluid for which the flow rate thereof has been retarded in the merging portion on the side of the evaporation unit, thereby enabling vapor phase working fluid evaporated in the merging portion on the side of the evaporation unit to be adequately reheated by the heat of exhaust gas to ensure an adequate amount of heat. As a result, during cold starting and the like during which promotion of warming is particularly required, the direct loss of heat by the vapor phase working fluid caused by contact with the peripheral walls of the condensation unit and the like is avoided, thereby enabling heat exchange with a target of promotion of warming to be carried out efficiently.
- In the heat pipe according to this first aspect, the cross-sectional area of a flow path orthogonal to the vertical direction of the merging portion may be set to be larger than the cross-sectional area of a flow path orthogonal to the vertical direction of the plurality of evaporation unit side heat pipe portions. According to this configuration, the working fluid that has merged from each evaporation unit side heat pipe portion into the wide merging portion is reliably acted on by the heat of exhaust gas retained in the merging portion on the side of the evaporation unit. As a result, the vapor phase working fluid evaporated in the merging portion on the side of the evaporation unit is adequately reheated by the heat of exhaust gas to ensure an adequate amount of heat.
- In addition, in the heat pipe according to this first aspect, the cross-sectional area of a flow path orthogonal to the vertical direction of the merging portion may be set to be larger than the cross-sectional area of a flow path orthogonal to the vertical direction of the evaporation unit side heat pipe portion. According to this configuration, the working fluid that has merged from each heating unit side heat pipe portion into the merging portion resists being rapidly introduced into the evaporation unit side heat pipe portion having a small flow path cross-sectional area. Consequently, the flow rate of the working fluid that has merged from each heating unit side heat pipe portion temporarily decreases in the merging portion, and the heat of exhaust gas reliably acts on the working fluid for which the flow rate thereof has decreased in this merging portion. As a result, the vapor phase working fluid evaporated in the merging portion on the side of the evaporation unit is adequately reheated by the heat of exhaust gas to ensure an adequate amount of heat.
- In addition, the heat pipe according to this first aspect may be provided with throttling means which is provided between the merging portion and the evaporation unit side heat pipe portion and which restricts the cross-sectional area of the flow path orthogonal to the vertical direction. According to this configuration, the working fluid that has merged from each heating unit side heat pipe portion into the merging portion further resists being introduced into the evaporation unit side heat pipe portion having a restricted cross-sectional area for the flow path. Consequently, the flow rate of the working fluid that has merged from each heating unit side heat pipe portion into the merging portion further decreases, and the heat of exhaust gas acts even more reliably on the working fluid for which the flow rate thereof has further decreased in this merging portion. As a result, the vapor phase working fluid evaporated in the merging portion on the side of the evaporation unit is adequately reheated by the heat of exhaust gas to ensure an adequate amount of heat.
- Moreover, the heat pipe according to this first aspect may be provided near the center of the exhaust pipe. According to this configuration, the heat of exhaust gas near the center of the exhaust pipe where the temperature within the exhaust pipe is the highest acts on the working fluid inside the merging portion, and the heat of exhaust gas is efficiently imparted to the working fluid retained in the merging portion. As a result, the vapor phase working fluid evaporated in the merging portion on the side of the evaporation unit is efficiently heated by the heat of high-temperature exhaust gas near the center of the exhaust pipe to ensure an adequate amount of heat.
- In the heat pipe according to this first aspect, the cross-section of the merging portion orthogonal to the direction of flow of the exhaust gas may be in the shape of a semicircular arc.
- In the heat pipe according to this first aspect, the working fluid further heated by the evaporation unit may be a vapor phase working fluid.
- In the heat pipe according to this first aspect, the evaporation unit may be arranged higher than the heating unit in the vertical direction.
- In summary of that described above, by retarding the flow rate of the working fluid with flow rate retardation means provided with a merging portion and the like that merges the working fluid heated in each heating unit side heat pipe portion of the heat pipe on the side of the evaporation unit, the heat of exhaust gas easily acts on the working fluid for which the flow rate thereof has been retarded in the merging portion on the side of the evaporation unit, thereby ensuring an adequate amount of heat for the vapor phase working fluid, and making it possible to efficiently carry out heat exchange with a target of promotion of warming by avoiding the heat of the vapor phase working fluid being lost directly due to contact with the cold peripheral walls and the like of the condensation unit, particularly during cold starting when promotion of warming is required.
- A second aspect of the invention relates to an exhaust heat recoverer that is provided with the heat pipe according to the first aspect, and a condensation unit into which is introduced the working fluid evaporated in the evaporation unit and in which the introduced working fluid is cooled.
- A third aspect of the invention relates to an exhaust heat recoverer comprising a heat pipe including a heating unit for heating a working fluid using heat of exhaust gas discharged from an engine, and an evaporation unit that is provided with an evaporation unit side heat pipe portion through which the working fluid flows, and that evaporates the working fluid heated by the heating unit using the heat of the exhaust gas. In the exhaust heat recoverer, the heat pipe is provided with flow rate retardation means for retarding the flow rate of the working fluid flowing through the evaporation unit side heat pipe portion.
- The foregoing and further objects, features and advantages of the invention will become apparent from the following description of example embodiments with reference to the accompanying drawings, wherein like numerals are used to represent like elements and wherein:
-
FIG. 1 is a perspective view showing an exhaust heat recoverer as claimed in a first embodiment of the invention applied to an exhaust pipe of an automobile; -
FIG. 2 is a longitudinal cross-sectional side view of the same exhaust heat recoverer applied to the exhaust pipe of an automobile; -
FIG. 3 is a longitudinal cross-sectional front view of the same exhaust heat recoverer as viewed from the axial direction of an exhaust pipe; -
FIG. 4 is a longitudinal cross-sectional front view of an exhaust heat recoverer as claimed in a second embodiment of the invention as viewed from the axial direction of an exhaust pipe; and -
FIG. 5 is a longitudinal cross-sectional front view of an exhaust heat recoverer as claimed in the related art as viewed from the axial direction of an exhaust pipe. - The following provides an explanation of a mode for carrying out the invention based on the drawings.
-
FIGS. 1 and 2 show an exhaust pipe of an automobile in which is applied an exhaust heat recoverer as claimed in a first embodiment of the invention, and anexhaust heat recoverer 2 is provided at an intermediate location in thisexhaust pipe 1. More specifically, theexhaust pipe 1 is divided at theexhaust gas recoverer 2 into an upstreamexhaust pipe path 11 and a downstreamexhaust pipe path 12, and while the upstream side in the direction of exhaust gas flow of an evaporation side case 25 (to be described later) of theexhaust heat recoverer 2 is connected to the upstreamexhaust pipe path 11, the downstream side in the direction of exhaust gas flow of theevaporation side case 25 is connected to the downstream sideexhaust pipe path 12. In addition, a catalytic converter is provided on the upstream side of the upstream side exhaust pipe path 11 (farther upstream than the exhaust heat recoverer 2). On the other hand, a muffler is provided on the downstream side of the downstream side exhaust pipe path 12 (farther downstream than the exhaust heat recoverer 2). - In addition, as shown in
FIG. 3 , theexhaust heat recoverer 2 is provided with aheat pipe 23 having aheating unit 21 and anevaporation unit 22, and acondensation unit 24. - The
heat pipe 23 allows the passage there through of a working fluid in the form of pure water, and is housed within theevaporation side case 25 roughly in the shape of a rectangular frame. The central portion of theevaporation side case 25 in which thisheat pipe 23 is located is arranged so as to face the inside of theexhaust pipe 1. Theheat pipe 23 is provided with a plurality of heating unit sideheat pipe portions 23 a on the side of theheating unit 21 that heats pure water with the heat of the exhaust gas (bottom ofFIG. 3 ), and a plurality of evaporation unit sideheat pipe portions 23 b on the side of theevaporation unit 22 that evaporates the pure water heated by the heating unit sideheat pipe portions 23 a (top ofFIG. 3 ). Theheat pipe 23 carries out heat exchange between the pure water flowing through the inside of each heating unit sideheat pipe portion 23 a and each evaporation unit sideheat pipe portion 23 b and exhaust gas present within theexhaust pipe 1 discharged from an engine, thereby heating and evaporating the pure water. In this case, each heating unit sideheat pipe portion 23 a and each evaporation unit sideheat pipe portion 23 b has a prescribed length (of about, for example, 60 mm) in the direction of flow of the exhaust gas flowing through theexhaust pipe 1, and are provided extending in the vertical direction at prescribed intervals in the left and right directions, respectively, on the side of theheating unit 21 and the side of theevaporation unit 22 within theevaporation side case 25. - The
condensation unit 24 has the shape of an enclosed tank, and is arranged outside theexhaust pipe 1. Aninlet port 31 and anoutlet port 32 of a cooling water path 3, which circulates engine cooling water of an automobile, are connected to thecondensation unit 24. In addition, thecondensation unit 24 and theevaporation side case 25 are linked through upper andlower communication paths heat pipe 23 of the evaporation side case 25 (heating unit sideheat pipe portions 23 a and evaporation unit sideheat pipe portions 23 b), is introduced into thecondensation unit 24 through theupper communication path 26 a. Awater vapor layer 251, where water vapor evaporated by theheat pipe 23 merges, is provided in the upper end of theevaporation side case 25, and an upper end of each evaporation unit sideheat pipe portion 23 b of theheat pipe 23 is fit and inserted into the lower surface of thiswater vapor layer 251. On the other hand, anintake portion 252, into which liquid phase pure water accumulated in areservoir portion 27 to be described later is introduced, is provided in the lower end of theevaporation side case 25, and the lower end of each heating unit sideheat pipe portion 23 a of theheat pipe 23 is fit and inserted into the upper surface of thisintake portion 252. Although theupper communication path 26 a is connected between thewater vapor layer 251 of theevaporation side case 25 and thecondensation unit 24, thelower communication path 26 b is connected between theintake portion 252 of theevaporation side case 25 and the reservoir portion 27 (to be described later). In this case, each heating unit sideheat pipe portion 23 a and each evaporation unit sideheat pipe portion 23 b are formed to respectively have the same diameter. - The
condensation unit 24 is divided into a two-layer structure by apartition 241, and carries out heat exchange between engine cooling water, introduced from theinlet port 31 of the cooling water path 3 on the side of anouter layer 241 a to the outside of thispartition 241, and water vapor introduced from thewater vapor layer 251 on the side of aninner layer 241 b to the inside of thepartition 241, thereby resulting in condensation of water vapor from which heat has been lost due to heat exchange with the engine cooling water from the vapor phase to the liquid phase of pure water. Engine cooling water that has undergone heat exchange with water vapor in thecondensation unit 24 flows out from the side of theouter layer 241 a of thecondensation unit 24 through theoutlet port 32 of the cooling water path 3. In this case, theinlet port 31 of the cooling water path 3 is located on the side of thewater vapor layer 251 on the side of theouter layer 241 a of thecondensation unit 24, and heat of the high-temperature water vapor immediately after being introduced from thewater vapor layer 251 is imparted thereto. - On the other hand, the
reservoir portion 27 is provided on the lower surface of thecondensation unit 24, and pure water that has entered the liquid phase as a result of heat exchange with engine cooling water in thecondensation unit 24 moves from thecondensation unit 24 into thereservoir portion 27 and is accumulated therein. Liquid phase pure water that has accumulated in thereservoir portion 27 is returned to theevaporation side case 25 through thelower communication path 26 b. In addition, avalve 271 for controlling the return the return of liquid phase pure water to thereservoir portion 27 in the lower portion of theevaporation side case 25 is provided at the connection with thelower communication path 26 b of thereservoir portion 27. Thisvalve 271 is opened and closed by an operatingportion 272 activated by negative pressure from the engine side, and as a result of being closed by the operation of the operatingportion 272 such as at completion of warming when heat exchange with engine cooling water in thecondensation unit 24 is no longer required, the movement of the pure water (water vapor) is controlled to allow the heat load to dissipate to a radiator. In this case, the pure water used for the working fluid of theexhaust heat recoverer 2 is sealed while maintaining a vacuum (reduced pressure) in the heat pipe 23 (heating unit sideheat pipe portions 23 a and evaporation unit sideheat pipe portions 23 b), thecondensation unit 24, thereservoir portion 27 and the upper andlower communication paths heat pipe 23,condensation unit 24,reservoir portion 27 and upper andlower communication paths - Flow rate retardation means 4 for retarding the flow rate of vapor phase pure water (water vapor) flowing in the form of water vapor through each of the evaporation unit side
heat pipe portions 23 b, is provided on the side of theevaporation unit 22 of theheat pipe 23. This flow rate retardation means 24 is provided with a mergingportion 23 c that merges pure water respectively heated by each heating unit sideheat pipe portion 23 a on the side of theevaporation unit 22. The upper end of each heating unit sideheat pipe portion 23 a is respectively connected to the lower end of this mergingportion 23 c. The lower end of each evaporation unit sideheat pipe portion 23 b is respectively connected to the upper end of the mergingportion 23 c located between mutually adjacent heating unit sideheat pipe portions 23 a, and is connected to the lower end of thewater vapor phase 251 by extending upward in the vertical direction. In addition,corrugated fins 23 d are joined between theevaporation side case 25 and the heating unit sideheat pipe portions 23 a and the evaporation unit sideheat pipe portions 23 b adjacent thereto, between mutually adjacent heating unit sideheat pipe portions 23 a, and between mutually adjacent evaporation unit sideheat pipe portions 23 b, and thecorrugated fins 23 d promote heat exchange between pure water and exhaust gas by increasing the heat transfer areas of the evaporation unit side and heating unit sideheat pipe portions portion 23 c is provided extending in roughly the horizontal direction (roughly horizontal direction orthogonal to the axis of the exhaust pipe) near the center of theexhaust pipe 1. In this case, the diagonal lines shown inFIG. 3 indicate liquid phase pure water, while the dots indicate water vapor (vapor phase pure water). Furthermore, the mergingportion 23 c not only merges pure water heated within each of the heating unit sideheat pipe portions 23 a, but rather when heat exchange with pure water is promoted due to increase in the amount of heat of the exhaust gas, also merges water vapor evaporated as a result of heating proceeding to the inside of each of the heating unit sideheat pipe portions 23 a. - In addition, the merging
portion 23 c on the side of theevaporation unit 22 is set to have a flow path cross-sectional area larger than the flow path cross-sectional area in each heating unit sideheat pipe portion 23 a. In other words, in contrast to seven heating unit sideheat pipe portions 23 a being arranged in the horizontal direction orthogonal to the direction of flow of exhaust gas, mergingportion 23 c is continuously provided extending between heating unit sideheat pipe portions 23 a on one side in the horizontal direction orthogonal to the direction of flow of exhaust gas (left edge ofFIG. 3 ) and heating unit sideheat pipe portions 23 a on the other side in the horizontal direction orthogonal to the direction of flow of exhaust gas (right edge ofFIG. 3 ), and as a result thereof, the cross-sectional area of the flow path orthogonal to the vertical direction of the mergingportion 23 c is set to be larger than the total cross-sectional area of the flow paths orthogonal to the vertical direction of each heating unit sideheat pipe portion 23 a of which seven are intermittently provided in the horizontal direction orthogonal to the direction of flow of exhaust gas. - On the other hand, the merging
portion 23 c on the side of theevaporation unit 22 is set to have a flow path cross-sectional area larger than the flow path cross-sectional area of each evaporation unit sideheat pipe portion 23 b. In other words, six evaporation unit sideheat pipe portions 23 b are arranged in the horizontal direction orthogonal to the direction of flow of exhaust gas, and as a result thereof, the flow path cross-sectional area of the mergingportion 23 c continuously provided extending between the heating unit sideheat pipe portions 23 a on both one side and the other side in the horizontal direction orthogonal to the direction of flow of exhaust gas is set to be larger than the total flow path cross-sectional area of each evaporation unit sideheat pipe portion 23 b of which six are intermittently provided in the horizontal direction orthogonal to the direction of flow of exhaust gas. The total cross-sectional area of flow paths orthogonal to the vertical direction of each of the heating unit sideheat pipe portions 23 a is set to be larger than the total cross-sectional area of flow paths orthogonal to the vertical direction of each of the evaporation unit sideheat pipe portions 23 b. - In this case, the lower end of each heating unit side
heat pipe portion 23 a is respectively connected to theintake portion 252 on the lower end of theevaporation side case 25, and the upper end thereof is connected to the lower end of the mergingportion 23 c by extending upward in the vertical direction. On the other hand, the lower end of each evaporation unit sideheat pipe portion 23 b is respectively connected to the mergingportion 23 c located between mutually adjacent heating unit sideheat pipe portions 23 a, and the upper end thereof is connected to the lower end of thewater vapor phase 251 on the upper end of theevaporation side case 25 by extending upward in the vertical direction. - Thus, in the above-mentioned first embodiment, the
heat pipe 23 causes the flow rate of pure water flowing through each of the heating unit sideheat pipe portions 23 a to be retarded in the mergingportion 23 c on the side of theevaporation unit 22 by the flow rate retardation means 4 provided with the mergingportion 23 c that merges pure water respectively heated by the seven heating unit sideheat pipe portions 23 a on the side of theheating unit 21 to the side of theevaporation unit 22. This is carried out to retard the flow rate of pure water merged from each of the heating unit sideheat pipe portions 23 a by retaining in the mergingportion 23 c having a large flow path cross-sectional area by causing pure water heated by each heating unit sideheat pipe portion 23 a to merge into the mergingportion 23 c on the side of theevaporation unit 22. Moreover, since the flow path cross-sectional area of the mergingportion 23 c is provided to be larger than the flow path cross-sectional area of each evaporation unit sideheat pipe portion 23 b, pure water that has merged from each heating unit sideheat pipe portion 23 a into the mergingportion 23 c resists being rapidly introduced into each evaporation unit sideheat pipe portion 23 b having a small flow path cross-sectional area, thereby causing the flow rate of pure water to temporarily decrease in the mergingportion 23 c. As a result, the heat of exhaust gas easily acts on pure water for which the flow rate thereof has been retarded in the mergingportion 23 c on the side of theevaporation unit 22, and water vapor (vapor phase pure water) evaporated in the mergingportion 23 c on the side of theevaporation unit 22 is adequately reheated by the heat of the exhaust gas, thereby ensuring an adequate amount of heat. As a result, heat exchange with engine cooling water can be carried out efficiently by avoiding the heat of the water vapor being lost directly due to contact with thecold partition 241 and the like of thecondensation unit 24, particularly during cold starting when promotion of warming is required. - In addition, since the merging
portion 23 c of theevaporation unit 22 is provided extending in the horizontal direction near the center of theexhaust pipe 1, the heat of the exhaust gas that reaches the highest temperature near the center of theexhaust pipe 1 can be efficiently imparted to the pure water retained in the mergingportion 23 c, which is extremely advantageous in terms of improving the efficiency of heat exchange with engine cooling water. - Moreover, since the total flow path circumferential cross-sectional area of each of the heating unit side
heat pipe portions 23 a is set to be larger than the total flow path circumferential cross-sectional area of each of the evaporation unit sideheat pipe portions 23 b, the heat of exhaust gas aggressively and effectively acts on liquid phase pure water in each of the heating unit sideheat pipe portions 23 a due to the large flow path circumferential cross-sectional area thereof, thereby making it possible to efficiently heat the liquid phase pure water in each of the heating unit sideheat pipe portions 23 a. - Next, an explanation is provided of a second embodiment of the invention based on
FIG. 4 . - A different configuration is employed for the heat pipe in this second embodiment. Furthermore, other constituents with the exception of the heat pipe are the same as in the case of the above-mentioned first embodiment, like reference numerals are used to indicate like constituents, and a detailed explanation thereof is omitted.
- Namely, in this second embodiment, a heat pipe 28 allows the flow of a working fluid in the form of pure water there through, and is housed within the
evaporation side case 25 in the shape of a rectangular frame. A central portion of theevaporation side case 25 in which this heat pipe 28 is located is arranged so as to face an inside of theexhaust pipe 1. The heat pipe 28 is provided with a plurality of heating unit sideheat pipe portions 28 a on the side of the heating unit 21 (bottom ofFIG. 4 ) that heats pure water with heat of exhaust gas, and a plurality of evaporation unit sideheat pipe portions 28 b on the side of the evaporation unit 22 (top ofFIG. 4 ) that evaporates pure water heated by the heating unit sideheat pipe portions 28 a. This heat pipe 28 carries out heat exchange between pure water flowing through the inside of each heating unit sideheat pipe portion 28 a and each evaporation unit sideheat pipe portion 28 b, and exhaust gas discharged from an engine, thereby evaporating the pure water by heating. In this case, each of the heating unit sideheat pipe portions 28 a and each of the evaporation unit sideheat pipe portions 28 b are provided within theevaporation side case 25 extending in the vertical direction at prescribed intervals in the left and right directions, respectively. - The heat pipe 28 is provided with flow rate retardation means 5 for retarding the flow rate of vapor phase pure water (water vapor) flowing in the form of water vapor through each of the evaporation unit side
heat pipe portions 28 b. This flow rate retardation means 5 is provided with mergingportions 28 c having a roughly semi-circular cross-section orthogonal to the direction of flow of the exhaust gas that cause pure water respectively heated by each of the heating unit sideheat pipe portions 28 a to merge onto the side of theevaporation unit 22. In addition,corrugated fins 28 d are joined between theevaporation side case 25 and the heating unit sideheat pipe portions 28 a and the evaporation unit sideheat pipe portions 28 b adjacent thereto, between mutually adjacent heating unit sideheat pipe portions 28 a, and between mutually adjacent evaporation unit sideheat pipe portions 28 b, and thecorrugated fins 28 d promote heat exchange between pure water and exhaust gas by increasing the heat transfer area of the heat pipe 28. Each mergingportion 28 c is provided arranged in rows at prescribed intervals in respectively roughly the horizontal direction (roughly horizontal direction orthogonal to the axis of the exhaust pipe) near the center of theexhaust pipe 1. In this case, the diagonal lines shown in the heat pipe 28 inFIG. 4 indicate liquid phase pure water, while the dots indicate water vapor (vapor phase pure water). - In addition, the upper ends of each group of two each of the heating unit side
heat pipe portions 28 a are respectively connected to each mergingportion 28 c on the side of theevaporation unit 22, while the lower end of a single evaporation unit sideheat pipe portion 28 b is connected to each mergingportion 28 c on the side of theevaporation unit 22. Each mergingportion 28 c on the side of theevaporation unit 22 is set to have a flow path cross-sectional area larger than the flow path cross-sectional area of each heating unit sideheat pipe portion 28 a. In other words, in contrast to the two heating unit sideheat pipe portions 28 a being arranged intermittently in the horizontal direction orthogonal to the direction of flow of exhaust gas interposed between thecorrugated fins 28 d, each mergingportion 28 c is provided continuously extending between the two heating unit sideheat pipe portions 28 a, and as a result, the flow path cross-sectional area of the mergingportions 28 c is set to be larger than the total flow path cross-sectional area of each of the two heating unit sideheat pipe portions 28 a provided intermittently in the horizontal direction orthogonal to the direction of flow of exhaust gas. - On the other hand, each merging
portion 28 c on the side of theevaporation unit 22 is set to have a flow path cross-sectional area larger than the flow path cross-sectional area of each of the evaporation unit sideheat pipe portion 28 b. In other words, the flow path cross-sectional area of the mergingportion 28 c provided continuously extending between two heating unit sideheat pipe portions 28 a is set to be larger than the flow path cross-sectional area of a single evaporation unit sideheat pipe portion 28 b connected to the upper end of this mergingportion 28 c. The total flow path cross-sectional area of the two heating unit sideheat pipe portions 28 a is set to be twice as large as the flow path cross-sectional area of the single evaporation unit sideheat pipe portion 28 b. - In this case, the lower ends of each group of two heating unit side
heat pipe portions 28 a are respectively connected to theintake portion 252 on the lower end of theevaporation side case 25, and the upper ends thereof are connected to the lower ends of the mergingportions 28 c by extending upward in the vertical direction. On the other hand, the lower end of each evaporation unit sideheat pipe portion 28 b is respectively connected to the upper end of the mergingportion 28 c located between a group of two heating unit sideheat pipe portions 28 a, and the upper end thereof is connected to the lower end of thewater vapor layer 251 on the upper end of theevaporation side case 25 by extending upward in the vertical direction. In addition, together with six of the heating unit sideheat pipe portions 28 a being arranged on the side of theheating unit 21, three evaporation unit sideheat pipe portions 28 b are arranged on the side of theevaporation unit 22. - Thus, in this second embodiment, the heat pipe 28 retards the flow rate of pure water passing through each of the heating unit side
heat pipe portions 28 a in each of the mergingportions 28 c on the side of theevaporation unit 22 by the flow rate retardation means 5 provided with the mergingportions 28 c merging pure water respectively heated by each group of two heating unit sideheat pipe portions 28 a on the side of theheating unit 21 to the side of theevaporation unit 22. This is because the flow rate of pure water merged from each heating unit sideheat pipe portion 28 a is retarded as a result of being retained in each mergingportion 28 c having a large flow path cross-sectional area since pure water heated two each of the heating unit sideheat pipe portions 28 a is caused to merge in each mergingportion 28 c on the side of theevaporation unit 22. Moreover, since the flow path cross-sectional area of each mergingportion 28 c is set to be larger than the flow path cross-sectional area of a single evaporation unit sideheat pipe portion 28 b, pure water that has merged from each heating unit sideheat pipe portion 28 a into each mergingportion 28 c resists being rapidly introduced into each evaporation unit sideheat pipe portion 28 b having a small flow path cross-sectional area, thereby causing the flow rate of pure water to temporarily decrease in the mergingportions 28 c. As a result, the heat of exhaust gas easily acts on pure water for which the flow rate thereof has been retarded in each mergingportion 28 c on the side of theevaporation unit 22, and water vapor (vapor phase pure water) evaporated in each mergingportion 28 c on the side of theevaporation unit 22 is adequately reheated by the heat of the exhaust gas, thereby ensuring an adequate amount of heat. As a result, heat exchange with engine cooling water can be carried out efficiently by avoiding the heat of the water vapor being lost directly due to contact with thecold partition 241 and the like of thecondensation unit 24, particularly during cold starting when promotion of warming is required. - In addition, since each merging
portion 28 c of theevaporation unit 22 is provided extending in the horizontal direction near the center of theexhaust pipe 1, the heat of the exhaust gas that reaches the highest temperature near the center of theexhaust pipe 1 can be efficiently imparted to the pure water retained in each mergingportion 28 c, which is extremely advantageous in terms of improving the efficiency of heat exchange with engine cooling water. - Moreover, since the total flow path cross-sectional area of each of the six heating unit side
heat pipe portions 28 a is set to be larger than the total flow path cross-sectional area of each of the three evaporation unit sideheat pipe portions 28 b, the heat of exhaust gas aggressively and effectively acts on liquid phase pure water in each of the heating unit sideheat pipe portions 28 a due to the large flow path cross-sectional area thereof, thereby making it possible to efficiently heat the liquid phase pure water in each of the heating unit sideheat pipe portions 28 a. - Furthermore, the invention is not limited to the each of the above-mentioned embodiments, but rather includes various other variations thereof. For example, although the flow path cross-sectional areas of the merging
portions evaporation unit 22 is set to be larger than the flow path cross-sectional areas of each of the evaporation unit sideheat pipe portions evaporation unit 22 or on the upstream side of each evaporation unit side heat pipe portion, that restricts flow path cross-sectional area. In this case, working fluid that has merged from each heating unit side heat pipe portion into the merging portion further resists being introduced into the evaporation unit side heat pipe portion having a restricted flow path cross-sectional area, and the heat of exhaust gas acts even more reliably on working fluid for which the flow rate thereof has been further decreased in the merging portion. - In addition, although the previously described first embodiment employs a configuration in which each of the evaporation unit side
heat pipe portions 23 b and each of the heating unit sideheat pipe portions 23 a are respectively formed to the same diameter, and the number of the evaporation unit sideheat pipe portions 23 b is one fewer than the number of the heating unit sideheat pipe portions 23 a, namely six, and therefore the total flow path cross-sectional area of the six evaporation unit sideheat pipe portions 23 b is set to be smaller than the total flow path cross-sectional area of the seven heating unit sideheat pipe portions 23 a, if the total flow path cross-sectional area of each of the evaporation unit side heat pipe portions is set to be smaller than the total flow path cross-sectional area of each of the heating unit side heat pipe portions, it is not necessary for each of the evaporation unit side heat pipe portions and each of the heating unit side heat pipe portions to respectively have the same diameter, and the difference in the numbers of evaporation unit side heat pipe portions and heating unit side heat pipe portions is not limited thereto. - In addition, in the previously described second embodiment, although each of the evaporation unit side
heat pipe portions 28 b and each of the heating unit sideheat pipe portions 28 a are respectively formed to the same diameter, and the upper ends of each group of two heating unit sideheat pipe portions 28 a are connected to the lower end of a single evaporation unit sideheat pipe portion 28 b through the mergingportions 28 c, and therefore the flow path cross-sectional area of a single evaporation unit sideheat pipe portion 28 b is set to be roughly half the total flow path cross-sectional area of each group of two heating unit sideheat pipe portions 28 a, if the total flow path cross-sectional area of the evaporation unit side heat pipe portion is set to be smaller than the total flow path cross-sectional area of the heating unit side heat pipe portions, it is not necessary for each evaporation unit side heat pipe portion and each heating unit side heat pipe portion to be respectively formed to the same diameter, and the difference in the numbers of evaporation unit side heat pipe portions and heating unit side heat pipe portions is not limited thereto. - In addition, although the
valve 271 for controlling the return of liquid phase pure water to thereservoir portion 27 is provided in the connection with thelower communication path 26 b of thereservoir portion 27 in the embodiments, the location at which this valve is provided is not limited thereto, but rather it may be provided at any location provided the movement of water vapor to the condensation unit is controlled when the valve is closed such as at completion of warming when heat exchange with engine cooling water is no longer necessary in the condensation unit. - In addition, although engine cooling water is applied as the target of heat exchange that carries out heat exchange with exhaust gas in the
exhaust heat recoverer 2 in the embodiments, engine oil or transmission oil and the like may also be a target of heat exchange. - Moreover, although pure water is applied as the working fluid in the embodiments, working fluids other then water, such as alcohols or fluorocarbons, may also be applied.
Claims (12)
1.-2. (canceled)
3. The heat pipe according to claim 12 , wherein a flow path cross-sectional area orthogonal to the vertical direction of the merging portion is larger than a flow path cross-sectional area orthogonal to the vertical direction of the plurality of heating unit side heat pipe portions.
4. The heat pipe according to claim 12 , wherein a flow path cross-sectional area orthogonal to the vertical direction of the merging portion is larger than a flow path cross-sectional area orthogonal to the vertical direction of the evaporation unit side heat pipe portion.
5. The heat pipe according to claim 12 , further comprising throttling portion which is provided between the merging portion and the evaporation unit side heat pipe portion and which restricts the flow path cross-sectional area orthogonal to the vertical direction.
6. The heat pipe according to claim 12 , wherein the merging portion is provided near the center of an exhaust pipe through which the exhaust gas flows.
7. The heat pipe according to claim 12 , wherein the cross-section of the merging portion orthogonal to the direction of flow of the exhaust gas is in the shape of a semi-circular arc.
8. The heat pipe according to claim 12 , wherein the working fluid further heated by the evaporation unit is a vapor phase working fluid.
9. The heat pipe according to claim 12 , wherein the evaporation unit is arranged higher than the heating unit in the vertical direction.
10. An exhaust heat recoverer comprising:
the heat pipe according to claim 12 ; and
a condensation unit into which is introduced the working fluid further heated by the evaporation unit and in which the introduced working fluid is cooled.
11. (canceled)
12. A heat pipe comprising;
a heating unit that is provided with a heating unit side heat pipe portion that heats a working fluid using heat of exhaust gas discharged from an engine;
an evaporation unit that is provided with an evaporation unit side heat pipe portion through which the working fluid flows, and that further heats the working fluid heated by the heating unit side heat pipe portion using heat of the exhaust gas; and
flow rate retardation unit that retards the flow rate of the working fluid flowing into the evaporation unit side heat pipe portion,
wherein:
the heating unit side heat pipe portion is provided in plurality; and
the flow rate retardation unit is provided with a merging portion that merges the working fluid respectively heated by the plurality of heating unit side heat pipe portions, on the evaporation unit side.
13. The heat pipe according to claim 12 , wherein:
the flow rate retardation unit is arranged to be connected to both one end of the evaporation unit side heat pipe portion and one end of the heating unit side heat pipe portion;
the one end of the evaporation unit side heat pipe portion is an end on the side of the heating unit; and
the one end of the heating unit side heat pipe portion is an end on the side of the evaporation unit.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2007301577A JP4450056B2 (en) | 2007-11-21 | 2007-11-21 | Exhaust heat recovery unit |
JP2007-301577 | 2007-11-21 | ||
PCT/IB2008/003563 WO2009066177A2 (en) | 2007-11-21 | 2008-11-20 | Heat pipe, exhaust heat recoverer provided therewith |
Publications (1)
Publication Number | Publication Date |
---|---|
US20100282445A1 true US20100282445A1 (en) | 2010-11-11 |
Family
ID=40627186
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/743,925 Abandoned US20100282445A1 (en) | 2007-11-21 | 2008-11-20 | Heat pipe, exhaust heat recoverer provided therewith |
Country Status (8)
Country | Link |
---|---|
US (1) | US20100282445A1 (en) |
EP (1) | EP2220452B1 (en) |
JP (1) | JP4450056B2 (en) |
CN (1) | CN101868687B (en) |
AT (1) | ATE505701T1 (en) |
DE (1) | DE602008006264D1 (en) |
RU (1) | RU2438084C1 (en) |
WO (1) | WO2009066177A2 (en) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20160334169A1 (en) * | 2015-05-12 | 2016-11-17 | Benteler Automobiltechnik Gmbh | Motor vehicle heat exchanger system |
US20160334170A1 (en) * | 2015-05-12 | 2016-11-17 | Benteler Automobiltechnik Gmbh | Motor vehicle heat exchanger system |
US20160333843A1 (en) * | 2015-05-12 | 2016-11-17 | Benteler Automobiltechnik Gmbh | Motor vehicle heat exchanger system |
US20160332506A1 (en) * | 2015-05-12 | 2016-11-17 | Benteler Automobiltechnik Gmbh | Motor vehicle heat transfer system |
US10996002B2 (en) | 2016-10-12 | 2021-05-04 | Denso Corporation | Evaporator |
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JP2006284144A (en) * | 2005-04-04 | 2006-10-19 | Denso Corp | Exhaust heat recovery device |
CN2802421Y (en) * | 2005-06-21 | 2006-08-02 | 王磊 | Heat pipe radiator for electronic refrigeration |
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JP2007278623A (en) * | 2006-04-07 | 2007-10-25 | Denso Corp | Exhaust heat recovery system |
-
2007
- 2007-11-21 JP JP2007301577A patent/JP4450056B2/en not_active Expired - Fee Related
-
2008
- 2008-11-20 DE DE602008006264T patent/DE602008006264D1/en active Active
- 2008-11-20 US US12/743,925 patent/US20100282445A1/en not_active Abandoned
- 2008-11-20 AT AT08852095T patent/ATE505701T1/en not_active IP Right Cessation
- 2008-11-20 EP EP08852095A patent/EP2220452B1/en not_active Not-in-force
- 2008-11-20 CN CN2008801172686A patent/CN101868687B/en not_active Expired - Fee Related
- 2008-11-20 WO PCT/IB2008/003563 patent/WO2009066177A2/en active Application Filing
- 2008-11-20 RU RU2010120430/06A patent/RU2438084C1/en not_active IP Right Cessation
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US5329993A (en) * | 1992-01-14 | 1994-07-19 | Sun Microsystems, Inc. | Integral heat pipe, heat exchanger and clamping plate |
US5309457A (en) * | 1992-12-22 | 1994-05-03 | Minch Richard B | Micro-heatpipe cooled laser diode array |
US6575230B1 (en) * | 1996-01-29 | 2003-06-10 | Denso Corporation | Cooling apparatus using boiling and condensing refrigerant |
US6612293B2 (en) * | 2001-07-23 | 2003-09-02 | Avl List Gmbh | Exhaust gas recirculation cooler |
US20070074854A1 (en) * | 2003-01-21 | 2007-04-05 | Mitsubishi Electric Corporation | Vapor-lift pump heat transport apparatus |
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US20160334169A1 (en) * | 2015-05-12 | 2016-11-17 | Benteler Automobiltechnik Gmbh | Motor vehicle heat exchanger system |
US20160334170A1 (en) * | 2015-05-12 | 2016-11-17 | Benteler Automobiltechnik Gmbh | Motor vehicle heat exchanger system |
US20160333843A1 (en) * | 2015-05-12 | 2016-11-17 | Benteler Automobiltechnik Gmbh | Motor vehicle heat exchanger system |
US20160332506A1 (en) * | 2015-05-12 | 2016-11-17 | Benteler Automobiltechnik Gmbh | Motor vehicle heat transfer system |
US10309348B2 (en) * | 2015-05-12 | 2019-06-04 | Benteler Automobiltechnik Gmbh | Motor vehicle heat exchanger system |
US10996002B2 (en) | 2016-10-12 | 2021-05-04 | Denso Corporation | Evaporator |
Also Published As
Publication number | Publication date |
---|---|
EP2220452A2 (en) | 2010-08-25 |
WO2009066177A2 (en) | 2009-05-28 |
RU2438084C1 (en) | 2011-12-27 |
CN101868687B (en) | 2012-07-18 |
ATE505701T1 (en) | 2011-04-15 |
CN101868687A (en) | 2010-10-20 |
JP2009127903A (en) | 2009-06-11 |
EP2220452B1 (en) | 2011-04-13 |
JP4450056B2 (en) | 2010-04-14 |
DE602008006264D1 (en) | 2011-05-26 |
WO2009066177A3 (en) | 2009-07-16 |
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Legal Events
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