CN101405484A - Exhaust gas heat recovery device - Google Patents
Exhaust gas heat recovery device Download PDFInfo
- Publication number
- CN101405484A CN101405484A CNA2007800092942A CN200780009294A CN101405484A CN 101405484 A CN101405484 A CN 101405484A CN A2007800092942 A CNA2007800092942 A CN A2007800092942A CN 200780009294 A CN200780009294 A CN 200780009294A CN 101405484 A CN101405484 A CN 101405484A
- Authority
- CN
- China
- Prior art keywords
- guiding channel
- cooling medium
- coolant guiding
- heat exchanger
- exhaust
- 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.)
- Granted
Links
- 238000011084 recovery Methods 0.000 title claims abstract description 110
- 239000002826 coolant Substances 0.000 claims abstract description 228
- 239000007789 gas Substances 0.000 claims description 77
- 239000002912 waste gas Substances 0.000 claims description 58
- 230000015572 biosynthetic process Effects 0.000 claims description 6
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 abstract description 38
- 230000005484 gravity Effects 0.000 abstract description 5
- 239000000498 cooling water Substances 0.000 description 147
- 238000001816 cooling Methods 0.000 description 35
- 238000011144 upstream manufacturing Methods 0.000 description 14
- 239000012212 insulator Substances 0.000 description 10
- 230000000694 effects Effects 0.000 description 9
- 230000008676 import Effects 0.000 description 8
- 230000000630 rising effect Effects 0.000 description 8
- 238000010438 heat treatment Methods 0.000 description 6
- 238000009413 insulation Methods 0.000 description 4
- 238000009835 boiling Methods 0.000 description 3
- 239000003054 catalyst Substances 0.000 description 3
- 239000000110 cooling liquid Substances 0.000 description 2
- 238000013022 venting Methods 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000002159 abnormal effect Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 239000000919 ceramic Substances 0.000 description 1
- 238000004140 cleaning Methods 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 230000001010 compromised effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 239000011491 glass wool Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000011347 resin Substances 0.000 description 1
- 229920005989 resin Polymers 0.000 description 1
- 229910052710 silicon Inorganic materials 0.000 description 1
- 239000010703 silicon Substances 0.000 description 1
- 125000006850 spacer group Chemical group 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 231100000331 toxic Toxicity 0.000 description 1
- 230000002588 toxic effect Effects 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
- 210000002268 wool Anatomy 0.000 description 1
Images
Classifications
-
- 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
Landscapes
- Exhaust Silencers (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
An exhaust heat recovery device with which a coolant medium in a heat exchanger can be prevented from reaching high temperatures is provided. An exhaust heat recovery system 10 is provided with an heat exchanger 18 that performs heat exchange between exhaust gas and a coolant medium; and a natural convection water pipe 56 whose one end is connected to an upper portion in the direction of gravity of an engine coolant water pipe 42 in the heat exchanger 18 and whose other end is connected to a lower portion in the direction of gravity of the engine coolant water pipe 42, and whose intermediate portion is positioned at the outer side of the heat exchanger 18.
Description
Technical field
The present invention relates to a kind of exhaust gas heat recovery device, its carry out the heat exchange between waste gas (as the waste gas of automobile) and the cooling liquid and reclaim as described in heat in the waste gas.
Background technique
Shown in the Japanese patent application that publication number is 2004-293395 and 2002-147291, the exhaust cooling-part that is used for motor is well-known, pipe and outer tube in wherein double pipe structure has, and be provided with gas exhausting valve at the upstream side of the inside of outer tube.Between pipe and the outer tube, it carried out the heat exchange between cooling water and the waste gas in vent gas cooler was arranged on.
Summary of the invention
In the technology of as above mentioning, when motor stopped, the cooling water in the cooling water passage in vent gas cooler stopped circulation.Because residual heat, the temperature of cooling water may rise to boiling.
The present invention makes according to above-mentioned situation, and a kind of exhaust gas heat recovery device is provided, and its temperature that can prevent the cooling liquid of heat exchanger inside raises.
To achieve these goals, the exhaust gas heat recovery device according to first scheme of the present invention comprises heat exchanger, the heat exchange between its execution waste gas and the cooling medium; And the natural convection passage, the one end is connected to the top on the gravitational direction of the coolant guiding channel in heat exchanger, and the other end is connected to the bottom on the gravitational direction of coolant guiding channel.
In the exhaust gas heat recovery device of first scheme, the coolant guiding channel of heat exchanger and natural convection passage constitute cooling medium because natural convection (being relative density difference) can circuit natural convection circulation route.The natural convection passage is connected to the upper and lower on the gravitational direction of coolant guiding channel.Because the temperature difference of the cooling medium in this natural convection circulation route, cooling medium circulates by the natural convection circulation route.Thus, even do not produce the structure that is forced to flow in the coolant guiding channel in heat exchanger, also can avoid near cooling medium the gathering high-temperature portion of heat exchanger.Correspondingly, cooling medium can not reach a high temperature.
By this way, utilize the exhaust gas heat recovery device of this programme, can prevent that the cooling medium of heat exchanger inside from reaching a high temperature.
Alternative plan of the present invention comprises the exhaust gas heat recovery device of first scheme, and wherein the intermediate portion of natural convection passage is positioned at the outside of heat exchanger.
In the exhaust gas heat recovery device according to alternative plan of the present invention, the intermediate portion of natural convection passage is positioned at the outside of heat exchanger.When cooling medium by natural convection circulation canal circulation time, heat is dispersed in the intermediate portion of natural convection passage.Thus, can prevent effectively that cooling medium from reaching a high temperature.
Third party's case of the present invention comprises first or the exhaust gas heat recovery device of alternative plan, wherein, and the heat-exchanging part that heat exchanger has the heat exchange carried out between waste gas and the cooling medium and forms around bypass member that along continuous straight runs is provided with.Heat exchanger is constructed at exhaust flow changeable through between the state of heat-exchanging part through the state and the exhaust flow of bypass.
In the exhaust gas heat recovery device of third party's case, cylindrical heat-exchanging part along continuous straight runs be formed at setting bypass member around.Coolant guiding channel is arranged in this heat-exchanging part so that it can carry out the heat exchange with waste gas.By this structure, be very big with respect to the exhausted air quantity in the heat exchanger of cooling medium amount.Even in having this structure of a lot of heats, also can prevent in natural convection circulation route (route) circuit cooling medium reach a high temperature and need not rely on cooling medium be forced to flow.
According to the exhaust gas heat recovery device of cubic case of the present invention, comprise heat exchanger, it carries out the heat exchange between waste gas and the cooling medium; And the natural convection passage, the one end is connected to the top on the gravitational direction of the coolant guiding channel in heat exchanger, and its other end is connected to the bottom on the gravitational direction of coolant guiding channel, and the intermediate portion is positioned at the outside of heat exchanger.
In the exhaust gas heat recovery device of cubic case, the coolant guiding channel of heat exchanger and natural convection passage constitute cooling medium because natural convection (being relative density difference) can circuit natural convection circulation route.The natural convection passage is connected to the upper and lower on the gravitational direction of coolant guiding channel.Because the intermediate portion of natural convection passage is positioned at the outside of heat exchanger, when cooling medium circulation time in the natural convection circulation canal, it is in the intermediate portion office of natural convection passage release heat, and is cooled.Though this structure can not produce in the coolant guiding channel of heat exchanger and be forced to flow, and can avoid near cooling medium the gathering high-temperature portion of heat exchanger, and cooling medium can not reach a high temperature yet.
By this way, utilize the exhaust gas heat recovery device of cubic case, can prevent that the cooling medium of heat exchanger inside from reaching a high temperature.
Exhaust gas heat recovery device according to the 5th scheme of the present invention, comprise heat exchanger, the heat-exchanging part that it has the heat exchange carried out between waste gas and the cooling medium and forms around bypass member that along continuous straight runs is provided with, and heat exchanger is constructed at exhaust flow changeable through between the state of heat-exchanging part through the state and the exhaust flow of bypass; And the natural convection passage, the one end is connected to the top on the gravitational direction of the coolant guiding channel in heat exchanger, and its other end is connected to the bottom on the gravitational direction of coolant guiding channel, and the intermediate portion is positioned at the outside of heat exchanger.
In the exhaust gas heat recovery device of the 5th scheme, cylindrical heat-exchanging part forms around the bypass member of along continuous straight runs setting.Coolant guiding channel be arranged in this heat-exchanging part in case with waste gas exchanged heat.By this structure, be very big with respect to the exhausted air quantity in the heat exchanger of cooling medium amount.The coolant guiding channel of heat exchanger and natural convection passage constitute cooling medium because natural convection (being relative density difference) can circuit natural convection circulation route.The natural convection passage is connected to the upper and lower on the gravitational direction of coolant guiding channel.Because the intermediate portion of natural convection passage is positioned at the outside of heat-exchanging part (heat exchanger), when cooling medium circulation time in the natural convection circulation canal, it is in the intermediate portion office of natural convection passage release heat, and is cooled.Correspondingly, be not forced to flow though this structure can not produce in the coolant guiding channel of heat exchanger, cooling medium can not reach a high temperature.
By this way, utilize the exhaust gas heat recovery device of the 5th scheme, can prevent that the cooling medium of heat exchanger inside from reaching a high temperature.
The 6th scheme of the present invention is the exhaust gas heat recovery device of the 5th scheme, wherein an end of natural convection passage is connected to the upper lateral part on gravitational direction that is positioned at the bypass member top in the coolant guiding channel, and the other end is connected to the lower side on gravitational direction that is positioned at the bypass member below.
In the exhaust gas heat recovery device of the 6th scheme, the natural convection passage is connected to coolant guiding channel with it is positioned at upside and downside with respect to bypass channel part place.Based on this reason, the part that is not included in the natural convection circulation canal of cooling medium of coolant guiding channel becomes very little.Thus, the amount of circuit cooling medium increases in the natural convection circulation canal, and can prevent effectively that the cooling medium of heat exchanger inside from reaching a high temperature.
Exhaust gas heat recovery device according to the 7th scheme of the present invention, comprise in the exhaust gas heat recovery device of first to the 6th scheme any one, wherein coolant guiding channel comprises the part of cooling medium circulation route, cooling medium is circulated forcibly at this part place when carrying out heat exchange between waste gas and cooling medium, and an end and the other end of natural convection passage are connected to the coolant guiding channel part, when cooling medium is forced to circulation time in coolant guiding channel, become less than predetermined value at an end of described part place's natural convection passage and the pressure difference between the other end.
In the exhaust gas heat recovery device of the 7th scheme, when between waste gas and cooling medium, carrying out heat exchange, device running such as pump makes cooling medium be forced to circulation in the cooling medium circulation canal, and the cooling medium circulation canal comprises the coolant guiding channel of heat exchanger.Thus, can carry out effective heat exchange.On the other hand, if the cooling medium in the cooling medium circulation canal be forced to circulate (running that is pump) and stop, then the residual heat at the exhaust gas side place in the heat exchanger is transferred in the cooling medium of coolant guiding channel.Cooling medium is by the circulation of natural convection circulation canal, and this natural convection circulation canal is constructed to comprise above-mentioned coolant guiding channel and natural convection passage, thereby can prevent that cooling medium from reaching a high temperature.
Herein, one end of natural convection passage and the other end are (promptly, because the introduction part and the discharge portion of the cooling medium of natural convection) be connected to as the bottom, when being forced to be flowing in circulation time in the cooling medium circulation route, become less than predetermined value at an end of this part place natural convection passage and the pressure difference between the other end.Based on this reason,, suppressed cooling medium and flowed in the natural convection passage when generation is forced to circulation time.Therefore, when between waste gas and cooling medium, carrying out heat exchange, can prevent that heat contained in the cooling medium is discharged to the natural convection passage with being wasted.
According to of the present invention the from all directions the exhaust gas heat recovery device of case comprise in the exhaust gas heat recovery device of first to the 6th scheme any one, wherein coolant guiding channel comprises the part of cooling medium circulation route, when carrying out heat exchange between waste gas and cooling medium, cooling medium is circulated forcibly at this part place.
One end and the other end of natural convection passage is connected to be arranged in and is forced to circuit with the coolant guiding channel cooling medium and flows to part on the vertical plane.
In the exhaust gas heat recovery device of all directions case, when between waste gas and cooling medium, carrying out heat exchange, operating pumps etc. are operated and cooling medium is forced to circulation in the cooling medium circulation route, and this cooling medium circulation route comprises the coolant guiding channel of heat exchanger.Thus, can carry out effective heat exchange.On the other hand, if the cooling medium in the cooling medium circulation canal be forced to circulate (operation that is pump) and stop, then the residual heat at the exhaust gas side place in the heat exchanger is transferred in the cooling medium of coolant guiding channel.Cooling medium is by the circulation of natural convection circulation canal, and this natural convection circulation canal is constructed to comprise coolant guiding channel and natural convection passage, thereby can prevent that cooling medium from reaching a high temperature.
Herein, an end of natural convection passage and the other end (that is, because the introduction part and the discharge portion of the cooling medium of natural convection) are connected to be arranged in perpendicular to the coolant guiding channel cooling medium and are forced to position on the plane that circuit flows to.Based on this reason, because the introduction part and the pressure difference between the discharge portion of the cooling medium that the pump circulation of cooling medium causes are very little.Correspondingly, when producing pump circulation in the cooling medium circulation route, suppress cooling medium and flowed into the natural convection passage, be discharged into the natural convection passage with preventing heat waster contained in the cooling medium.
The exhaust gas heat recovery device of the 9th scheme comprises first in the exhaust gas heat recovery device of third party's case any one according to the present invention, wherein heat exchanger comprises: shell, and it has the coolant guiding channel that the exhaust passage of exhaust flow warp and cooling medium that contiguous exhaust passage is provided with are flowed through; First connecting passage, its end place on cooling medium of coolant guiding channel flows to is connected to the top on the gravitational direction of coolant guiding channel, and forms a distolateral part of natural convection passage one; Second connecting passage, its other end place on cooling medium of coolant guiding channel flows to is connected to the bottom on the gravitational direction of coolant guiding channel, and forms another distolateral part of natural convection passage; And heat insulating member, it makes the part that is positioned at shell of second connecting passage adiabatic mutually with waste gas.
In the exhaust gas heat recovery device of the 9th scheme, the waste gas of the exhaust passage of flowing through is carried out heat exchange with the cooling medium of the coolant guiding channel of flowing through in shell.Cooling medium flows to second connecting passage or flows to first connecting passage from second connecting passage from first connecting passage in coolant guiding channel, and portion and outer loop (being to circulate forcibly) in the enclosure.At this moment, the temperature (rising) of the cooling medium at the second connecting passage place by the heat insulating member thermal insulation is suppressed to the temperature that is lower than the cooling medium in the coolant guiding channel.
Then, when the pump circulation of cooling medium was stopped, the cooling medium of second connecting passage was because its relatively low temperature makes the relative density of its relative density greater than the cooling medium in the coolant guiding channel, owing to gravity produces downward flowing.At another distolateral place on cooling medium flows to of coolant guiding channel, cooling medium flows to the bottom of coolant guiding channel on gravitational direction.Because like this, produced the natural convection of cooling medium, prevented that cooling medium from reaching a high temperature to the first connecting passage side.In addition, by heat insulating member is set, can parts be set, can be maintained at low relatively temperature in the part of this parts place cooling medium in shell (that is, second connecting passage, it is the other end of natural convection passage) inside.Because like this, second connecting passage is covered by shell and protects.
Exhaust gas heat recovery device according to the tenth scheme of the present invention comprises heat exchanger, and heat exchanger comprises shell, and it has the coolant guiding channel that the exhaust passage of exhaust flow warp and cooling medium that contiguous exhaust passage is provided with are flowed through; First connecting passage, the top on the outside of the end place connection shell that its cooling medium at coolant guiding channel flows to and the gravitational direction of coolant guiding channel; Second connecting passage, the bottom on the outside of the other end place connection shell that its cooling medium at coolant guiding channel flows to and the gravitational direction of coolant guiding channel; And heat insulating member, it makes the part that is positioned at shell of second connecting passage adiabatic mutually with waste gas.
In the exhaust gas heat recovery device of the tenth scheme, carry out the heat exchange between the cooling medium of the waste gas of the exhaust passage of flowing through and the coolant guiding channel in the shell of flowing through in the enclosure.Cooling medium flows to second connecting passage or flows to first connecting passage from second connecting passage from first connecting passage in coolant guiding channel, in the inside and outside circulation (circulation forcibly) of shell.At this moment, the temperature (rising) of the cooling medium at the second connecting passage place by the heat insulating member thermal insulation is suppressed to the temperature that is lower than the cooling medium in the coolant guiding channel.
Then, when cooling medium be forced to circulation when being stopped, the cooling medium of second connecting passage is because its relatively low temperature makes the relative density of its relative density greater than the cooling medium in the coolant guiding channel, because that gravity produces is downward mobile.At another distolateral place on cooling medium flows to of coolant guiding channel, cooling medium flows to the bottom on gravitational direction of coolant guiding channel.Because like this, produced the natural convection of cooling medium, prevented that cooling medium from reaching a high temperature to the first connecting passage side.In addition,, can parts be set, can be maintained at low relatively temperature in the part of this parts place cooling medium in shell (that is, second connecting passage) inside by heat insulating member is set.Because like this, second connecting passage is hidden and protects by shell.
By this way, by the exhaust gas heat recovery device of the tenth scheme, can prevent that the cooling medium of heat exchanger inside from reaching a high temperature.
The 11 scheme of the present invention is the exhaust gas heat recovery device of the 9th or the tenth scheme, and when when the direction of exhaust-gas flow is seen, second connecting passage removes that part after the part that penetrates shell forms fully and coolant guiding channel is overlapping.
In the exhaust gas heat recovery device of the 11 scheme, when when the direction of exhaust-gas flow is seen, second connecting passage of removing after the part that penetrates shell is overlapping with coolant guiding channel fully, and can not hinder the mobile of waste gas, so can suppress the increase of exhaust back pressure.
The 12 scheme of the present invention is the exhaust gas heat recovery device of the 11 scheme, and wherein, when when the direction of exhaust-gas flow is seen, the part that second connecting passage is removed after the part that penetrates shell has the sectional shape identical with the sectional shape of coolant guiding channel.
In the exhaust gas heat recovery device of the 12 scheme, when when the direction of exhaust-gas flow is seen, second connecting passage of removing after the part that penetrates shell has the sectional shape identical with the sectional shape of coolant guiding channel, and can when keeping low-temperature cooling media, keep above-mentioned back pressure to suppress effect, so that produce the natural convection of cooling medium.
The 13 scheme of the present invention is the 11 or the exhaust gas heat recovery device of the 12 scheme, and wherein coolant guiding channel forms coaxially cylindrical around the exhaust passage.
In the exhaust gas heat recovery device of the 13 scheme, for example, coolant guiding channel is formed on the inner tubal wall that limits the exhaust passage and is arranged on coaxially between the outer tube wall in the outside of inner tubal wall.Second connecting passage is arranged on the either side of coolant guiding channel in the axial direction.When cooling medium be forced to circulation when being stopped because low-temperature cooling media flows to the cylindrical bottom portion that forms of second connecting passage, can not be stuck in the natural convection passage so cooling medium flows.Thereby the temperature that can prevent the cooling medium in the shell effectively increases.
The exhaust gas heat recovery device of the tenth cubic case of the present invention is any one in the exhaust gas heat recovery device of the 11 to the 13 scheme, and wherein second connecting passage upwards is arranged on the downstream side of coolant guiding channel at exhaust flow.
In the exhaust gas heat recovery device of the tenth cubic case, after heat was absorbed, because the heat exchange between waste gas and the cooling medium, waste gas contacted with second connecting passage, thereby the heat that second connecting passage absorbs from waste gas is very little.Can make that the temperature of the cooling medium that second connecting passage is interior is lower.
The exhaust gas heat recovery device of the 15 scheme of the present invention is any one in the exhaust gas heat recovery device of the 9th to the tenth cubic case, and wherein second connecting passage is cut apart plate by utilization and cut apart the other end of coolant guiding channel on cooling medium flows to and form.
In the exhaust gas heat recovery device of the 15 scheme, the coolant guiding channel and second connecting passage are formed as one, and, do not have spacer portion between second connecting passage of coolant guiding channel and exhaust flow warp that is.Correspondingly, the area of contact of second connecting passage and waste gas is little, can make the cooling medium in second connecting passage remain on lower temperature.
Description of drawings
Fig. 1 is perpendicular to the formation that the is used for exhaust heat recovery axial sectional view according to the heat exchanger of the exhaust heat recovery system of the first embodiment of the present invention;
Fig. 2 is used for the axial, cross-sectional view of the formation of exhaust heat recovery according to the heat exchanger of the exhaust heat recovery system of the first embodiment of the present invention;
Fig. 3 is the system flow chart that illustrates according to the general structure of the exhaust heat recovery system of the first embodiment of the present invention;
Fig. 4 is perpendicular to the formation that the is used for exhaust heat recovery axial sectional view according to the optional example of the heat exchanger of the exhaust heat recovery system of the first embodiment of the present invention;
Fig. 5 A is the axial, cross-sectional view that is used for the heat exchanger according to a second embodiment of the present invention of exhaust heat recovery;
Fig. 5 B is the sectional view along Fig. 5 A center line 5B-5B;
Fig. 6 is the system flow chart that adopts the exhaust heat recovery system of heat exchanger according to a second embodiment of the present invention;
Fig. 7 A is the axial, cross-sectional view that the heat exchanger of a third embodiment in accordance with the invention is shown; And
Fig. 7 B is the sectional view along Fig. 7 A center line 7B-7B.
Embodiment
Aforesaid exhaust gas heat recovery device according to the present invention shows the effect preferably aspect the temperature rising of its cooling medium in preventing heat exchanger (being shell).
To the exhaust heat recovery system 10 that be used as according to the exhaust gas heat recovery device of first example embodiment of the present invention be described to Fig. 3 in conjunction with Fig. 1.Notice that when using the term of similar upstream and downstream, this is illustrated in the upstream/downstream side that exhaust flow makes progress in the following description.In addition, upwards (UP) arrow among each figure and downward (LO) arrow are illustrated respectively in upside and the downside (being the direction up and down of vehicle body) on the gravitational direction.
Fig. 3 shows the general structure of exhaust heat recovery system 10 with flow chart.As shown in the figure since with the heat exchange of engine cooling water, exhaust heat recovery system 10 reclaims the heat in the waste gas of internal-combustion engine 12 of automobiles.The heat that reclaims is used to heat or accelerate the warming-up of motor 12.
Formation is connected to motor 12 with the outlet pipe 14 of the exhaust route that waste gas is derived.On the exhaust route of outlet pipe 14, set gradually catalyst converter 16, exhaust heat recovery heat exchanger 18 (hereinafter referred to as " heat exchanger 18 ") and main baffler 20 from upstream side.Catalyst converter 16 is constructed to utilize the catalyzer 16A that is arranged on wherein to clean the waste gas of flowing through.Main baffler 20 is constructed to reduce the exhaust sound that will be produced during to air through the toxic emission of cleaning.
As shown in Figure 2, heat exchanger 18 comprises the interior pipe 26 and the outer tube 28 of the cylindrical and coaxial setting of each self-forming, and is provided with the shell 30 that forms the exhaust-gas flow parts.In addition, shell 30 is provided with the circular cone cylinder 32 that connects the part that is positioned at catalyst converter 16 sides of the upstream extremity 28A of outer tube 28 and outlet pipe 14 with the diameter greater than the diameter of outlet pipe 14; And the circular cone cylinder 34 of the part that is positioned at main baffler 20 sides of the downstream 28B of connection outer tube 28 and outlet pipe 14.
Following parts are formed on the inside of shell 30, exhaust entrance head 36, and it is circular cone cylinder 32 volume inside; Exhaust heat exchange route 38, the heat-exchanging part of the cylindrical space that forms between pipe 26 and the outer tube 28 in it is formed on; Bypass channel 22, it is the inner space of interior pipe 26, wherein is provided with passage switching valve 24; And exhaust outlet head 40, it is as exchanging parts and being circular cone cylinder 34 volume inside.
Be arranged on the inside of the exhaust heat exchange route 38 of shell 30 as the engine cooling water pipe 42 of the passage of cooling medium, and form heat-exchanging part 35, and form engine cooling hydrothermal exchange route 44 (hereinafter referred to as " heat exchange route 44 ") as the runner of the engine cooling water in the heat exchanger 18.In this example embodiment, as shown in Figure 1, engine cooling water pipe 42 has four layers of round column structure that form bicylindrical shape heat exchange route 44.After, comprise that the part of heat exchange route 44 in the outside of engine cooling water pipe 42 will be called as outside cylinder 42A, comprise that the part of heat exchange route 44 of the inboard of engine cooling water pipe 42 will be called as inboard cylinder 42B.
The outside cylinder 42A of engine cooling water pipe 42 and the upstream side of inboard cylinder 42B on the engine cooling current direction partly pass outer tube 28 and are connected to set inlet 46, and the downstream side part on the engine cooling current direction is passed outer tube 28 and is connected to set outlet 48.Among this model embodiment, compare with outlet 48, inlet 46 is arranged on the downstream side of exhaust heat exchange route 38, and heat exchanger 18 is contraflow heat exchangers.
Exhaust heat recovery system 10 also is provided with preceding Heater core 50 and the back Heater core 52 that the heat recovery of engine cooling water is used for heater, and makes engine cooling water circuit between preceding Heater core 50 and back Heater core 52 add hot water channel 54.Preceding Heater core 50 and back Heater core 52 be arranged in parallel.Heat exchanger 18 is arranged on the downstream side of back Heater core 52 in adding hot water channel 54.That is to say that inlet 46 is arranged on back Heater core 52 sides that add among the hot water channel 54, outlet 48 is arranged on the upstream side of the motor 12 that adds among the hot water channel 54.In this example embodiment, heat exchanger 18 is arranged in the engine cooling water system parallel with preceding Heater core 50 and connects with back Heater core 52.
Correspondingly, in exhaust heat recovery system 10, this system is designed to flow owing to the direction of arrow that the water pump that turns round along with the operation of motor 12 (not shown) makes engine cooling water mark on the hot water channel 54 along adding of Fig. 3.Thus, when from the high temperature flow heated water of motor 12 during through preceding Heater core 50 and back Heater core 52, water has experienced heat exchange, and the heat of recovery is used for heater.Engine cooling water in the cooling of Heater core 52 places, back is imported into heat exchanger 18, and (that is, depends on the control of ECU) where necessary and make itself and waste gas exchanged heat.This system is designed so that the same engine cooling water of flowing through preceding Heater core 50 of the engine cooling water of the heat exchanger 18 of flowing through turns back to motor 12 together.In this way, from the angle of engine warm-up, heat exchanger 18 is constructed to the heater as heated engine cooling water before engine cooling water imports motor 12.
The heat exchanger 18 that comprises exhaust heat recovery system 10 is provided with natural convection water pipe 56, and natural convection water pipe 56 connects the upper and lower on gravitational direction of outside cylinder 42A, and the intermediate portion is positioned at the outside of shell 30.More specifically, the main structure of natural convection water pipe 56 partly is that cooling water imports parts 56A, the part of interior pipe 26 (bypass channel 22) downside of cylinder 42A outside it is connected to; Cooling water discharge portion 56B, it is connected to the part of the high side of interior pipe 26 (bypass channel 22) of outside cylinder 42A; And the hot release 56C of portion, it passes outer tube 28 and is positioned at the outside that shell 30 is a heat exchanger 18.
Thus, in exhaust heat recovery system 10, natural convection water pipe 56 and import parts 56A and basic part between the cooling water discharge portion 56B on the gravitational direction of outside cylinder 42A constitutes the first annular natural convection circulation route 58 at cooling water.In this model embodiment, as shown in Figure 1, natural convection water pipe 56 (being natural convection circulation route 58) is with respect to the left and right sides setting of interior pipe 26.Equally, as shown in Figure 2, along exhaust flow to being provided with a plurality of natural convection water pipes 56.
When seeing from the side, the cooling water that each in the above-mentioned natural convection water pipe 56 has on the axial plane orthogonal that is arranged on engine cooling water pipe 42 (outside cylinder 42A) imports parts 56A and cooling water discharge portion 56B.More particularly, when side view is seen, connect straight line L that cooling water imports the imagination of parts 56A and cooling water discharge portion 56B be set to be basically perpendicular to engine cooling water pipe 42 axially.
Herein, by outside cylinder 42A, from 46 inflows and totally originally even that enter the mouth from 46 side outlets, 48 side groups that enter the mouth from exporting 48 engine cooling waters that flow out.Correspondingly, this device is constructed to, make at engine cooling water that owing to the water pump effect that adds among the hot water channel 54 that comprises engine cooling water pipe 42 is forced to circulation time the cooling water on the above-mentioned straight line L that is arranged on imagination imports between parts 56A and the cooling water discharge portion 56B (when seeing from the side) does not almost have pressure difference.That is to say that pressure difference or pressure ratio are still in setting value.Thus, owing to the water pump effect is forced to circulation time, can prevent engine cooling current direction natural convection water pipe 56.
In addition, a pair of upper and lower connecting tube parts 42C that each outside cylinder 42A is connected to inboard cylinder 42B is arranged on the engine cooling water pipe 42, is positioned at the position on the direction that makes each natural convection water pipe 56 be arranged on flow of cooling water.Thus, in the exhaust heat recovery system 10, the basic left side of inboard cylinder 42B or right-hand part, natural convection water pipe 56 and half part that partly is connected with natural convection water pipe 56 with inboard cylinder 42B that is included among the cylinder 42A of the outside form the second natural convection circulation route 60.Natural convection circulation route 60 comprises the thermal release 56C in the outside that is positioned at heat exchanger 18, and parallel with the first natural convection circulation route 58.
In addition, exhaust heat recovery system 10 is designed so that when this system is in the exhaust heat recovery pattern space between interior pipe 26 and inboard cylinder 42B in the exhaust heat exchange route 38 is as the exhaust passage.Under normal mode, this space is as the heat insulation air layer that bypass channel 22 (high-temp waste gas is flowed through wherein) and heat exchange route 44 are separated mutually.
Next, will the effect of first example embodiment be described.
As above in Gou Zao the exhaust heat recovery system 10, when the temperature of engine cooling water was hanged down, behind firm ato unit 12, ECU closed based on driving passage switching valve 24 as the needs of accelerating warming-up, and bypass channel 22 is closed.That is to say that the exhaust heat recovery pattern is selected.When this thing happens, the waste gas of motor 12 was imported into the exhaust heat exchange route 38 of heat exchanger 18 and does not flow to bypass channel 22.Between waste gas that imports exhaust heat exchange route 38 and engine cooling water, carry out heat exchange, and waste gas makes the engine cooling water heating.Thus, accelerated the warming-up of motor 12.
On the other hand, if the temperature of engine cooling water rises and surpasses threshold value, then ECU operating walk way switching valve 24 is opened, and bypass channel 22 is opened.That is to say, ECU from the exhaust heat recovery mode switching to normal mode.When this happens, the waste gas bypass channel 22 of mainly flowing through.Simultaneously in this case, because the action of motor 12 (being water pump), engine cooling water is comprising the circulation among the hot water channel 54 that adds of engine cooling water pipe 42.
When motor 12 stopped, the action of water pump stopped then, and owing to the circulation that is forced to of water pump shutting engine down cooling water stops.Though these have taken place, the condition of high temperature that stops the interior pipe 26 (bypass channel 22) of back heat exchanger 18 at motor 12 is kept a period of time.Be transferred to engine cooling water in the engine cooling water pipe 42 from the heat of this high temperature bypass channel 22.
In the exhaust heat recovery system 10, be provided with the top of cylinder 42A outside connecting and the natural convection water pipe 56 of bottom, make the part of natural convection water pipe 56 and outside cylinder 42A form the first natural convection circulation route 58.In addition, the left side of the part of natural convection water pipe 56, outside cylinder 42A and inboard cylinder 42B or right-hand part form the second natural convection circulation route 60.Because in proportion difference, make the natural convection shown in the arrow A n of the engine cooling water generates Fig. 1 in natural convection circulation route 58 and the natural convection circulation route 60 in the upside of circulation route 58 and circulation route 60 and the engine cooling water generates between the downside.Proportion difference is because the temperature difference of engine cooling water causes, and this temperature difference stops the heat of back from the engine cooling water transmission of bypass channel 22 to engine cooling water pipe 42 owing to the operation of water pump.The engine cooling water of thermal release 56C of flowing through in this circulation is cooled by the heat exchanger with air.Thus, the abnormal intensification and the boiling of engine cooling water have been prevented.
Because the upper and lower with respect to bypass channel 22 of outside cylinder 42A utilizes natural convection water pipe 56 to connect, so it is less not form the part of natural convection circulation route 58 among the cylinder 42A of the outside.Correspondingly, the amount of the engine cooling water that circulates in natural convection circulation route 58 and be cooled at thermal release 56C place increases.Thus, prevented the rising of engine cooling water temperature effectively.In exhaust heat recovery system 10, when motor 12 is stopped, can prevents the rising of engine cooling water temperature by the natural convection circulation, and not use power as electric motor.
Note, the cooling water of natural convection water pipe 56 import parts 56A and cooling water discharge portion 56B be arranged among the cylinder 42A of the outside with cooling water flow (or when seeing from the side along the straight line L of the imagination among Fig. 2) on (axial direction) vertical plane.In other words, when engine cooling water is forced to circulation time by adding hot water channel's 54 experience, there is not pressure difference between cooling water importing parts 56A and the cooling water discharge portion 56B.Owing to this reason, in the exhaust heat recovery system 10, no matter in the exhaust heat recovery pattern still under the situation at normal mode, engine cooling water does not all flow into natural convection water pipe 56.Therefore, when shutting engine down 12 as mentioned above, it when the heat at heat release portion 56C place discharges the waste or unnecessary cooling of the engine cooling water that causes, has realized preventing the function of engine cooling water temperature rising when preventing owing to motor 12 operation.
The exhaust heat recovery system 10 of first example embodiment according to the present invention, owing to be provided with bypass channel 22 at intermediate portion, it is big that venting capacity becomes.In this structure, when motor 12 cut out, the temperature of engine cooling water may uprise, and still, can prevent that the temperature of the cooling water in the engine cooling water pipe 42 from rising.
Note, in the above-mentioned example embodiment, show the example that engine cooling water pipe 42 forms bicylindrical shape heat exchange routes 44, still, the present invention is not therefore and restricted.For instance, as shown in Figure 4, engine cooling water pipe 42 also can be configured to form single cylindrical heat exchange route 44.In this case, natural convection circulation route 58 is formed with natural convection water pipe 56 and produces single convection current route (seeing arrow B).
Next, another example embodiment of the present invention will be described.Note, have with first example embodiment in the part and assembly of essentially identical structure adopt the mark identical with first example embodiment, and omission is to its explanation.
(second example embodiment)
Fig. 6 shows the flow chart of conduct according to the general structure of the exhaust heat recovery system 70 of the exhaust gas heat recovery device of second example embodiment.As shown in the figure, the difference of the exhaust heat recovery system 70 and first example embodiment is heat exchanger.The heat exchanger 18 of first example embodiment is provided with towards the outstanding natural convection water pipe 56 in the outside of outer tube 28.In contrast, exhaust heat recovery heat exchanger 72 (hereinafter referred to as " heat exchanger 72 ") does not have natural convection water pipe 56.
Shown in Fig. 5 A and Fig. 5 B, in the heat exchanger 72, to make axial direction be substantially horizontal (as the fore-and-aft direction of vehicle) to pipe 26 in being provided with.Interior pipe 26 passes the center axial region of outer tube 28, and outer tube 28 is defined as shell separately.In pipe 26 be connected to outlet pipe 14 at the two ends of axial direction.Interior pipe 26 also can be constructed to the part of outlet pipe 14.In addition, heat exchanger 72 is provided with circular cone cylinder 32, the periphery of pipe 26 in the upstream extremity of circular cone cylinder 32 is fixed on airtight conditions, and the downstream of circular cone cylinder 32 is connected to the upstream extremity 28A of outer tube 28.Heat exchanger 72 also is provided with circular cone cylinder 34, the periphery of pipe 26 in the downstream of circular cone cylinder 34 is fixed on airtight conditions, and the upstream extremity of circular cone cylinder 34 is connected to the downstream 28B of outer tube 28.
Be formed with in the heat-exchanging part 35 in the heat exchanger 72: exhaust entrance head 36, it is the space between interior pipe 26 and the circular cone cylinder 32; Exhaust heat exchange route 38, it is the cylindrical space that is formed between interior pipe 26 and the outer tube 28; Exhaust outlet head 40, it is the space between interior pipe 26 and the circular cone cylinder 34.The inside of interior pipe 26 is as above-mentioned bypass channel 22.In the heat exchanger entrance hole 26A that is arranged on the inside portion of circular cone cylinder 32 and is connected to exhaust entrance head 36 is formed on the pipe 26, in the heat exchanger outlet hole 26B that is arranged on the inside portion of circular cone cylinder 34 and is connected to exhaust outlet head 40 is formed on the pipe 26.
Water-cooling tube 74 is arranged on the inside of exhaust heat exchange route 38, and it comprises the cooling water heat exchange route 76 (hereinafter referred to as " heat exchange route 76 ") as the engine cooling water channel in the heat exchanger 72.In this example embodiment, water-cooling tube 74 forms cylindrical heat exchange route 76 in the inboard of twin-tub.Be connected to water-cooling tube 74 as the cooling water inlet of first connecting passage pipe 78 at the upstream side of cooling water flow on (promptly being forced to the circuit direction).Cooling water inlet pipe 78 passes outer tube 28 and connects cooling water inlet 76A and the external lateral portion of outer tube 28 (promptly describe after a while add hot water channel 54).Cooling water inlet 76A is positioned at the topmost part of cylindrical heat exchange route 76 on gravitational direction that axial direction is a substantially horizontal.
Equally, coolant outlet 76B is positioned at water-cooling tube 74 in the downstream side of cooling water flow on (promptly being forced to the circuit direction).Coolant outlet 76B is positioned at the foot of water-cooling tube 74 on gravitational direction, its opening towards exhaust flow to upstream side.Cooling water outlet pipe 80 as second connecting passage is connected on the coolant outlet 76B.Cooling water outlet pipe 80 is constructed ringwise and is made the internal diameter and the external diameter of its internal diameter and external diameter and water-cooling tube 74 be complementary.Cooling water outlet pipe 80 be constructed to be included in exhaust flow to downside and water-cooling tube 74 coaxial settings endless tube 82, pass outer tube 28 and be connected the topmost part of endless tube 82 on gravitational direction and the outlet 84 of the outside of outer tube 28.Correspondingly, the coolant outlet 76B of heat exchange route 76 is connected to the outside of outer tube 28 by cooling water outlet pipe 80.
When from exhaust flow to upstream side when seeing, the global shape of endless tube 82 and water-cooling tube 74 are overlapping, make endless tube 82 be hidden in water-cooling tube 74 (promptly not having visible part) behind fully.In this example embodiment, endless tube 82 and separates with the downstream of water-cooling tube 74 near marginal between exhaust heat exchange route 38 and the exhaust outlet head 40 a little.
Be arranged on the cooling water outlet pipe 80 and have heat-insulating structure as the thermal insulator 86 of heat insulating member.Thermal insulator 86 is set to cross over basically each the entire circumference in the internal surface of the endless tube 82 that forms cooling water outlet pipe 80 and outlet 84, and thermal insulator 86 is with the inside and waste gas thermal insulation mutually of cooling water outlet pipe 80.Notice that thermal insulator 86 can also be arranged on the outer surface of cooling water outlet pipe 80 (being arranged on simultaneously on internal surface and the outer surface), still, the whole external shape and the water-cooling tube 74 that are preferably thermal insulator 86 are overlapping.For thermal insulator 86, can use as silicon, heat stable resin, glass wool or remain on the material of ceramic wool on the steel plate etc.
In the above-mentioned heat exchanger 72, make this structure and make when managing 26 (bypass channels 22) in passage switching valve 24 cuts out, this has realized hot-swap feature because waste gas flows in exhaust heat exchange route 38.Pipe is 26 the time in passage switching valve 24 is opened, mainly flow through bypass channel 22 and realized the exhaust gas bypass function of waste gas.Notice that the exhaust heat that is provided with water-cooling tube 74 exchanges the flow resistance of the flow resistance (pressure loss) of route 38 greater than the bypass channel of opening 22.This structure makes in passage switching valve 24 is opened does not almost have exhaust flow to exhaust heat exchange route 38 under the situation of pipe 26.
The same with exhaust heat recovery system 10, exhaust heat recovery system 70 also is provided with preceding Heater core 50 and the back Heater core 52 that the heat that reclaims in the engine cooling water is used for heater, and before engine cooling water is recycled to Heater core 50 and back Heater core 52 add hot water channel 54.Preceding Heater core 50 and back Heater core 52 are arranged on the motor 12 abreast.Heat exchanger 72 is arranged on the downstream side that adds the back Heater core 52 among the hot water channel 54.That is to say that cooling water inlet pipe 78 is arranged on back Heater core 52 sides that add among the hot water channel 54, and the export department 84 of cooling water outlet pipe 80 is arranged on the upstream side of the motor 12 that adds among the hot water channel 54.In this example embodiment, Heater core 50 be arranged in parallel and connects with back Heater core 5 before heat exchanger 72 was parallel in the engine cooling water system.
Correspondingly, in the exhaust heat recovery system 70, this system is designed so that engine cooling water flows in the direction shown in the arrow on the hot water channel 54 that adds of Fig. 6.Thus, this structure is: the high temperature flow heated water of the motor 12 of flowing through through preceding Heater core 50 and after during Heater core 52, the heat that described water has experienced heat exchange and recovery is used for heater.Engine cooling water in the cooling of Heater core 52 places, back is imported into heat exchanger 72, and with waste gas exchanged heat.The engine cooling water of heat exchanger 72 of flowing through turns back to motor 12 together with the engine cooling water of Heater core 50 before flowing through.In this way, for heating operation, heat exchanger 72 is as the Preheating unit of warm-up the engine cooling water before launched machine 12 heating of engine cooling water.
In this example embodiment, the circuit that is forced to that is used for engine cooling water adds " the natural convection passage " of hot water channel 54 corresponding to the part of the natural convection circulation route that is formed for making engine cooling water experience natural convection.
Next, will the effect of second example embodiment be described.
In the exhaust heat recovery system 70 of as above structure, when the temperature of engine cooling water is low, behind firm ato unit 12, ECU based on as heating or accelerate the needs of warming-up motor 12 and drive passage switching valve 24 and close, bypass channel 22 is closed.That is to say that the exhaust heat recovery pattern is selected.The waste gas of motor 12 is directed in the exhaust heat exchange route 38 of heat exchanger 72 and does not flow to bypass channel 22.Carry out the waste gas of importing exhaust heat exchange route 38 and the heat exchange between the engine cooling water in heat exchanger 72, waste gas is heated engine cooling water.Thus, heating is accelerated or motor 12 warming-ups.
On the other hand, if the temperature of engine cooling water rises and surpasses threshold value, then ECU operating walk way switching valve 24 is opened, and bypass channel 22 is opened.That is to say, ECU from the exhaust heat recovery mode switching to normal mode.When this thing happens, the waste gas bypass channel 22 of mainly flowing through.Equally in this case, because the effect (being water pump) of motor 12, engine cooling water circulates by the hot water channel 54 that adds who comprises water-cooling tube 74.
When motor 12 stopped, the action of water pump stopped then, and owing to the circulation that is forced to of water pump shutting engine down cooling water stops.After motor 12 stopped, the condition of high temperature of the interior pipe 26 of heat exchanger 72 (bypass channel 22) kept a period of time.Come the heat of high temperature bypass channel 22 since then to be transferred to engine cooling water in the water-cooling tube 74.
In the exhaust heat recovery system 72,80 places are provided with thermal insulator 86 at cooling water outlet pipe.Based on this reason, engine cooling water temperature the cooling water outlet pipe 80 (less relatively from the heat of waste gas acquisition herein) is lower than the temperature of the engine cooling water in the heat exchange route 76, and its relative density is higher than the relative density (at this, water pump operation stops final vacuum heat and is transmitted from bypass channel 22) of the engine cooling water in the heat exchange route 76.Correspondingly, the engine cooling water in the cooling water outlet pipe 80 is downward flowing owing to gravity produces, and flow to heat exchange route 76 lowest part in the vertical from the 76B of coolant outlet portion.Thus, the engine cooling water in the heat exchange route 76 is pushed out, and produces flowing to the 76A of cooling water inlet portion.That is to say, the natural convection of engine cooling water takes place in the inside of heat exchanger 72 (outer tube 28).
In this way, because the natural convection (circulation) of engine cooling water takes place when motor 12 is stopped, so avoided the excessive temperature of engine cooling water to raise and boiling.Especially in heat exchanger 72, so big owing to being provided with bypass channel 22 venting capacities at intermediate portion.In this structure, engine cooling water temperature may uprise when motor 12 cuts out, and still, by cooling water outlet pipe 80 (mainly being endless tube 82) and thermal insulator 86 are set, can prevent the high temperature of cooling water in the water-cooling tube 74.
In addition, in the heat exchanger 72, compare with the structure that is forced to circulate that produces engine cooling water, do not consume electric power with operative installations when motor 12 stops (for example, electric pump).Based on this reason, when the excessive temperature of avoiding engine cooling water increases and seethes with excitement, can not influence fuel consumption.
In addition, when when the direction of exhaust-gas flow is seen, in the heat exchanger 72, the sectional shape of the sectional shape of endless tube 82 and water-cooling tube 74 is basic identical, and the back that endless tube 82 is hidden in water-cooling tube 74 makes endless tube 82 can not hinder exhaust-gas flow.Correspondingly, comprise by setting and the cooling water outlet pipe 80 of endless tube 82 prevented the increase of exhaust-gas flow back pressure.In addition, because the sectional shape of the sectional shape of endless tube 82 and heat exchange route 76 mates substantially, so can in the residual quantity that increases the cryogenic engine cooling water, keep suppressing the above-mentioned effect of back pressure.
In the heat exchanger 72, because heat exchange route 76 forms columniform shape, system 70 is constructed to make when forming engine cooling water channel (being single in this example embodiment) on the loop direction of engine cooling water, keeps required surface area.Based on this reason,, and can prevent the rising of cooling water temperature in the heat-exchanging part 35 (outer tube 28) effectively because natural convection makes the stagnation that engine cooling water unlikely takes place.
Equally, in the heat exchanger 72 because endless tube 82 with respect to water-cooling tube 74 be positioned at exhaust flow to the downstream side, so the thermal change that the waste gas from endless tube 82 obtains is few.Based on this reason, can further reduce the temperature of the engine cooling water of endless tube 82 inside.Correspondingly, when stopping, motor 12 can accelerate natural convection.
In the heat exchanger 72, by thermal insulator 86 is set, the relative density that is arranged on the engine cooling water in the endless tube 82 in the outer tube 28 becomes big relatively.Compare by the structure that water-cooling tube 74 is arranged on the outside of outer tube 28 with the part of cooling water passage, prevented endless tube 82 during vehicle is advanced because slungshot etc. are compromised.That is to say that endless tube 82 is protected by outer tube 28.
(the 3rd example embodiment)
Next, be used as the exhaust heat recovery heat exchanger 90 (hereinafter referred to as " heat exchanger 90 ") of formation with reference to Fig. 7 explanation according to the exhaust heat exchanger of the exhaust heat recovery system of the 3rd example embodiment of the present invention.
Fig. 7 A shows the sectional view of heat exchanger 90.Fig. 7 B illustrates along the sectional view of the line 7B-7B among Fig. 7 A.As shown in the figure, heat exchanger 90 is endless tube 82 with heat exchanger 72 differences according to second example embodiment of the present invention, cooling water outlet pipe 80 is the unitary part of separating with water-cooling tube 74 herein, and heat exchanger 90 comprises the ring pipe route 92 that is wholely set with water-cooling tube 74.
Specifically, what ring pipe route 92 was provided with the downstream side that is positioned at water-cooling tube 74 cuts apart plate 94, and ring-like thus pipeline line 92 is formed the engine cooling water route (second connecting passage) that separates with heat exchange route 76.Cut apart that plate 94 forms ring part so that corresponding, and its lowest part along continuous straight runs is cut off with the sectional shape of heat exchange route 76 (water-cooling tube 74).Enter export department 84 from the upwardly extending part of the topmost part of ring part.Thus, ring pipe route 92 is connected by forming the 76B of coolant outlet portion by portion (cutoffportion) of cutting apart plate 94 with heat exchange route 76.
By endless tube 82, thermal insulator 86 is arranged on the ring pipe route 92 that forms by this way.Except heat exchanger 90, other structure is identical with the relative configurations of heat exchanger 72.
Correspondingly, according to the heat exchanger 90 of the 3rd example embodiment of the present invention, can obtain and heat exchanger 72 identical functions and identical effect according to second example embodiment.In addition, in the heat exchanger 90, because ring pipe route 92 is integrally formed with water-cooling tube 74, so do not form the slit of exhaust flow warp between water-cooling tube 74 and ring pipe route 92, these are different with the heat exchanger 72 in second example embodiment.Therefore, the area of contact between ring pipe route 92 and the waste gas diminishes.Based on this reason, ring pipe route 92 further reduces from the heat that waste gas obtains, and can keep the low temperature of the engine cooling water in the ring pipe route 92.
Note, in the above-mentioned second and the 3rd example embodiment, show the cooling water inlet pipe 78 entrance part cooling water outlet pipes 80 that are forced to circulate for engine cooling water and be the example of export department (being parallel stream dynamic formula heat exchanger), still, the present invention is not limited thereto.For instance, this system can make, and is forced to the circuit engine cooling water and discharges from export department's 84 importings of cooling water outlet pipe 80 and from cooling water inlet pipe 78.
In addition, in the above-mentioned second and the 3rd example embodiment, show heat exchange route 76 and be formed at example on the single water-cooling tube 74, still, the present invention is not therefore and restricted.For instance, heat exchange route 76 can form the coaxial cylinder of a plurality of e, maybe can form a plurality of straight tubes.
In addition, in the above-mentioned second and the 3rd example embodiment, show the inside that bypass channel 22 is formed on the interior pipe 26 that comprises heat exchanger 72, still, the present invention is not therefore and restricted.For instance, bypass channel 22 can be set to be positioned at a plurality of parallel pipeline of heat exchanger 72 1 sides.Equally, the present invention can be used in the exhaust gas heat recovery device of not establishing bypass channel 22.
Claims (15)
1, a kind of exhaust gas heat recovery device comprises:
Heat exchanger, it carries out the heat exchange between waste gas and the cooling medium; And
Natural convection passage, one end are connected to the top on the gravitational direction of the coolant guiding channel in described heat exchanger, and the other end is connected to the bottom on the gravitational direction of described coolant guiding channel.
2, exhaust gas heat recovery device as claimed in claim 1, the intermediate portion of wherein said natural convection passage is positioned at the outside of described heat exchanger.
3, exhaust gas heat recovery device as claimed in claim 1 or 2, wherein said heat exchanger has the heat-exchanging part of the heat exchange carried out between described waste gas and the described cooling medium and formation around bypass member that along continuous straight runs is provided with, and described heat exchanger is constructed at described exhaust flow changeable through between the state of described heat-exchanging part through the state and the described exhaust flow of described bypass.
4, a kind of exhaust gas heat recovery device comprises:
Heat exchanger, it carries out the heat exchange between waste gas and the cooling medium; And
Natural convection passage, one end are connected to the top on the gravitational direction of the coolant guiding channel in described heat exchanger, and the other end is connected to the bottom on the gravitational direction of described coolant guiding channel, and intermediate portion is positioned at the outside of described heat exchanger.
5, a kind of exhaust gas heat recovery device comprises:
Heat exchanger, the heat-exchanging part that it has the heat exchange carried out between waste gas and the cooling medium and forms around bypass member that along continuous straight runs is provided with, and described heat exchanger is constructed at described exhaust flow changeable through between the state of described heat-exchanging part through the state and the described exhaust flow of described bypass; And
The natural convection passage, the one end is connected to the top on the gravitational direction that is arranged on the coolant guiding channel in the described heat exchanger, and the other end is connected to the bottom on the gravitational direction of described coolant guiding channel, and intermediate portion is positioned at the outside of described heat exchanger.
6, as claim 3 or 5 described exhaust gas heat recovery devices, one end of wherein said natural convection passage is connected to the upper lateral part on gravitational direction that is positioned at described bypass member top in the described coolant guiding channel, and the other end is connected to the lower side on gravitational direction that is positioned at described bypass member below.
7, as each described exhaust gas heat recovery device in the claim 1 to 6, wherein said coolant guiding channel comprise the cooling medium circulation route as the bottom: when as described in waste gas and as described in when carrying out heat exchange between the cooling medium as described in part place cooling medium circulated forcibly, and a described end of described natural convection passage and the described the other end be connected to described coolant guiding channel as the bottom: when cooling medium as described in be forced to circulation time in the coolant guiding channel, state a described end of natural convection passage and the pressure difference between the described the other end in described part place and become less than predetermined value.
8, as each described exhaust gas heat recovery device in the claim 1 to 6, wherein said coolant guiding channel comprise the cooling medium circulation route as the bottom: when as described in waste gas and as described in when carrying out heat exchange between the cooling medium as described in part place cooling medium circulated forcibly, and a described end of described natural convection passage and the described the other end are connected to be in and are forced to circuit with cooling medium described in the described coolant guiding channel and flow to position on the vertical plane.
9, as each described exhaust gas heat recovery device in the claim 1 to 3, wherein said heat exchanger comprises:
Shell, it has the coolant guiding channel that the exhaust passage of described exhaust flow warp and described cooling medium that contiguous described exhaust passage is provided with are flowed through;
First connecting passage, the end place that its described cooling medium at described coolant guiding channel flows to is connected to the top on the gravitational direction of described coolant guiding channel, and forms a distolateral part of described natural convection passage one;
Second connecting passage, the other end place that its described cooling medium at described coolant guiding channel flows to is connected to the bottom on the gravitational direction of described coolant guiding channel, and forms another distolateral part of described natural convection passage; And
Heat insulating member, it makes the part that is positioned at described shell of described second connecting passage adiabatic mutually with described waste gas.
10, a kind of exhaust gas heat recovery device comprises:
Heat exchanger, described heat exchanger comprises:
Shell, it has the coolant guiding channel that the exhaust passage of exhaust flow warp and cooling medium that contiguous described exhaust passage is provided with are flowed through;
First connecting passage, the end place that its described cooling medium at described coolant guiding channel flows to is communicated with the top on the gravitational direction of the outside of described shell and described coolant guiding channel;
Second connecting passage, the other end place that its described cooling medium at described coolant guiding channel flows to is communicated with the bottom on the gravitational direction of the outside of described shell and described coolant guiding channel; And
Heat insulating member, it makes the part that is positioned at described shell of described second connecting passage adiabatic mutually with described waste gas.
11, as claim 9 or 10 described exhaust gas heat recovery devices, wherein, when when the direction of described exhaust-gas flow is seen, the part that described second connecting passage is removed after the part that penetrates described shell forms overlapping with described coolant guiding channel fully.
12, exhaust gas heat recovery device as claimed in claim 11, wherein, when when the direction of described exhaust-gas flow is seen, the described part that described second connecting passage is removed after the described part that penetrates described shell has the sectional shape identical with the sectional shape of described coolant guiding channel.
13, as claim 11 or 12 described exhaust gas heat recovery devices, wherein said coolant guiding channel forms and centers on the cylindrical of described exhaust passage coaxially.
14, as each described exhaust gas heat recovery device in the claim 11 to 13, wherein said second connecting passage upwards is arranged on the downstream side of described coolant guiding channel at described exhaust flow.
15, as each described exhaust gas heat recovery device in the claim 9 to 14, wherein said second connecting passage is by cutting apart the other end of described coolant guiding channel and form with cutting apart plate on described cooling medium flows to.
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2006072704A JP2007247556A (en) | 2006-03-16 | 2006-03-16 | Exhaust heat recovery device |
| JP072704/2006 | 2006-03-16 | ||
| JP2006115819A JP4407666B2 (en) | 2006-04-19 | 2006-04-19 | Exhaust heat exchanger |
| JP115819/2006 | 2006-04-19 | ||
| PCT/JP2007/055327 WO2007105815A1 (en) | 2006-03-16 | 2007-03-12 | Exhaust gas heat recovery device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101405484A true CN101405484A (en) | 2009-04-08 |
| CN101405484B CN101405484B (en) | 2010-12-15 |
Family
ID=38592109
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2007800092942A Expired - Fee Related CN101405484B (en) | 2006-03-16 | 2007-03-12 | Exhaust gas heat recovery device |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2007247556A (en) |
| CN (1) | CN101405484B (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102086821A (en) * | 2009-12-04 | 2011-06-08 | 现代自动车株式会社 | Exhaust heat recovery device |
| CN102383903A (en) * | 2010-08-09 | 2012-03-21 | 通用汽车环球科技运作有限责任公司 | Hybrid powertrain system including an internal combustion engine and a stirling engine |
| CN103089372A (en) * | 2011-10-29 | 2013-05-08 | 刘莞欣 | Heat exchange silencer |
| CN103628959A (en) * | 2012-08-22 | 2014-03-12 | 现代自动车株式会社 | Structure of exhaust pipe for exhaust heat recovery |
| CN103670617A (en) * | 2012-09-13 | 2014-03-26 | 通用汽车环球科技运作有限责任公司 | Electrically heated catalyst with waste heat recovery |
| CN105102903A (en) * | 2014-03-06 | 2015-11-25 | 金正燮 | Fan heater for heating using waste heat of exhaust gas |
| CN106870077A (en) * | 2017-03-03 | 2017-06-20 | 禹伟 | A kind of gas turbine of energy-conserving and environment-protective |
| CN108431383A (en) * | 2015-12-14 | 2018-08-21 | 沃尔沃卡车集团 | Internal combustion engine system |
| CN115453084A (en) * | 2022-08-02 | 2022-12-09 | 山东大学 | Multi-field coupling device capable of realizing sensing and applying of force and heat flow of partitions and test method |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5108462B2 (en) * | 2007-11-07 | 2012-12-26 | 国立大学法人 東京大学 | Heat recovery equipment |
| KR101575267B1 (en) | 2010-08-27 | 2015-12-07 | 현대자동차 주식회사 | Heat exchanger for exhaust heat withdrawal of vehicle |
| KR101241211B1 (en) * | 2010-12-09 | 2013-03-13 | 현대자동차주식회사 | Heat exchanger for exhaust heat withdrawal of vehicle |
| JP6295792B2 (en) * | 2014-04-04 | 2018-03-20 | 日産自動車株式会社 | Engine exhaust system |
| JP6295898B2 (en) * | 2014-09-10 | 2018-03-20 | 日産自動車株式会社 | Engine waste heat recovery system |
| KR101611096B1 (en) * | 2014-11-17 | 2016-04-08 | 현대자동차주식회사 | Heat exchanger for exhaust gas |
| DE112016002290T5 (en) | 2015-05-21 | 2018-03-01 | Ngk Insulators, Ltd. | Heat exchange component |
| KR101807017B1 (en) * | 2015-12-11 | 2017-12-08 | 현대자동차 주식회사 | Exhaust system for vehicle |
| CN114486269B (en) * | 2022-04-15 | 2022-06-24 | 中国飞机强度研究所 | Engine driving temperature control system for aircraft testing laboratory and design method thereof |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58221381A (en) * | 1982-06-17 | 1983-12-23 | Ebara Corp | Waste heat retrieving type heat exchanger |
| JPH064019Y2 (en) * | 1987-01-27 | 1994-02-02 | 本田技研工業株式会社 | Control device for exhaust heat exchanger |
| GB9823669D0 (en) * | 1998-10-30 | 1998-12-23 | Serck Heat Transfer Limited | Exhaust gas cooler |
-
2006
- 2006-03-16 JP JP2006072704A patent/JP2007247556A/en active Pending
-
2007
- 2007-03-12 CN CN2007800092942A patent/CN101405484B/en not_active Expired - Fee Related
Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102086821A (en) * | 2009-12-04 | 2011-06-08 | 现代自动车株式会社 | Exhaust heat recovery device |
| CN102383903B (en) * | 2010-08-09 | 2014-08-06 | 通用汽车环球科技运作有限责任公司 | Hybrid powertrain system including an internal combustion engine and a stirling engine |
| CN102383903A (en) * | 2010-08-09 | 2012-03-21 | 通用汽车环球科技运作有限责任公司 | Hybrid powertrain system including an internal combustion engine and a stirling engine |
| CN103089372A (en) * | 2011-10-29 | 2013-05-08 | 刘莞欣 | Heat exchange silencer |
| CN103089372B (en) * | 2011-10-29 | 2015-05-13 | 刘莞欣 | Heat exchange silencer |
| CN103628959A (en) * | 2012-08-22 | 2014-03-12 | 现代自动车株式会社 | Structure of exhaust pipe for exhaust heat recovery |
| CN103628959B (en) * | 2012-08-22 | 2017-07-28 | 现代自动车株式会社 | Exhaust pipe structure for reclaiming exhaust heat |
| CN103670617A (en) * | 2012-09-13 | 2014-03-26 | 通用汽车环球科技运作有限责任公司 | Electrically heated catalyst with waste heat recovery |
| CN103670617B (en) * | 2012-09-13 | 2016-05-18 | 通用汽车环球科技运作有限责任公司 | There is the electrical heating catalyst of Waste Heat Recovery |
| CN105102903A (en) * | 2014-03-06 | 2015-11-25 | 金正燮 | Fan heater for heating using waste heat of exhaust gas |
| CN108431383A (en) * | 2015-12-14 | 2018-08-21 | 沃尔沃卡车集团 | Internal combustion engine system |
| US10704447B2 (en) | 2015-12-14 | 2020-07-07 | Volvo Truck Corporation | Internal combustion engine system |
| CN108431383B (en) * | 2015-12-14 | 2022-01-04 | 沃尔沃卡车集团 | Internal combustion engine system |
| CN106870077A (en) * | 2017-03-03 | 2017-06-20 | 禹伟 | A kind of gas turbine of energy-conserving and environment-protective |
| CN115453084A (en) * | 2022-08-02 | 2022-12-09 | 山东大学 | Multi-field coupling device capable of realizing sensing and applying of force and heat flow of partitions and test method |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2007247556A (en) | 2007-09-27 |
| CN101405484B (en) | 2010-12-15 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101405484B (en) | Exhaust gas heat recovery device | |
| CA2709252C (en) | Cogeneration apparatus | |
| KR101317373B1 (en) | Heat exchanger | |
| JP2007032561A (en) | Exhaust gas heat recovery device | |
| US20090038302A1 (en) | Exhaust gas heat recovery device | |
| KR101367320B1 (en) | Structure of exhaust pipe for exhaust-heat recovery | |
| CN101506483A (en) | Heat accumulation system for vehicle | |
| CN102055043A (en) | Battery and battery module | |
| ZA200705222B (en) | Heat exchanger | |
| KR101093666B1 (en) | Exhaust heat recovery apparatus | |
| JP2006314180A (en) | Thermal power generator | |
| JP2007285264A (en) | Heat exchanger | |
| JP4407666B2 (en) | Exhaust heat exchanger | |
| JP4844600B2 (en) | Exhaust heat recovery unit | |
| KR20130012998A (en) | Exhaust heat recovery device for atf warmup | |
| CN103939190A (en) | Engine cooling circulation system for auxiliary heating through exhaust pipe | |
| KR100621459B1 (en) | Heat exchanger for withdrawing heat of exhaust gas | |
| JP2017166403A (en) | Exhaust heat recovery device | |
| CN201006707Y (en) | Motorcycle oil-water refrigerating mechanism | |
| JP5707123B2 (en) | Heat exchange unit and manufacturing method thereof | |
| CN201931963U (en) | Passenger car exhaust afterheat heater | |
| JP2007247554A (en) | Exhaust heat recovery device | |
| JP2008133783A (en) | Exhaust heat recovery device | |
| KR101014535B1 (en) | Heat exchanger with cap having fuel cooling pipe | |
| KR101031255B1 (en) | Diesel oil cooler for ship |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20101215 Termination date: 20140312 |