CN103573355A - Exhaust gas heat recycling device - Google Patents
Exhaust gas heat recycling device Download PDFInfo
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- CN103573355A CN103573355A CN201310332131.5A CN201310332131A CN103573355A CN 103573355 A CN103573355 A CN 103573355A CN 201310332131 A CN201310332131 A CN 201310332131A CN 103573355 A CN103573355 A CN 103573355A
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- cylinder portion
- exhaust
- heat recovery
- inner cylinder
- valve body
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- 238000004064 recycling Methods 0.000 title abstract 7
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 18
- 238000011084 recovery Methods 0.000 claims description 97
- 239000000659 freezing mixture Substances 0.000 claims description 12
- 230000000712 assembly Effects 0.000 claims description 9
- 238000000429 assembly Methods 0.000 claims description 9
- 230000003068 static effect Effects 0.000 claims description 9
- 238000013459 approach Methods 0.000 claims description 4
- 238000003756 stirring Methods 0.000 claims description 4
- 239000003507 refrigerant Substances 0.000 abstract 2
- 239000000498 cooling water Substances 0.000 description 38
- 230000008676 import Effects 0.000 description 6
- 230000009286 beneficial effect Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 239000000446 fuel Substances 0.000 description 4
- 238000010438 heat treatment Methods 0.000 description 4
- 238000001816 cooling Methods 0.000 description 3
- 239000000203 mixture Substances 0.000 description 3
- 239000002826 coolant Substances 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- ZZUFCTLCJUWOSV-UHFFFAOYSA-N furosemide Chemical compound C1=C(Cl)C(S(=O)(=O)N)=CC(C(O)=O)=C1NCC1=CC=CO1 ZZUFCTLCJUWOSV-UHFFFAOYSA-N 0.000 description 1
- 230000002045 lasting effect Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy
- F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using heat
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
- F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D21/0001—Recuperative heat exchangers
- F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
- F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
-
- 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
- F01N2240/00—Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being
- F01N2240/36—Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being an exhaust flap
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
- F28F2250/06—Derivation channels, e.g. bypass
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- 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
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Exhaust Silencers (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
The exhaust gas heat recycling device includes an inner cylinder part. Refrigerant flows in the inner cylinder part. The exhaust gas heat recycling device also includes a middle cylinder part arranged outside the inner cylinder part in a predetermined distance from the inner cylinder part. A heat recycling flow path is formed between the middle cylinder part and the inner cylinder part, so that heat of exhaust gas can be recycled through the refrigerant passing through the inner cylinder part. The exhaust gas heat recycling device also includes an outer cylinder part arranged outside the middle cylinder part in a predetermined distance from the inner cylinder part. A bypass flow path is formed between the outer cylinder part and the middle cylinder part, so that diffluent exhaust gas can flow in the bypass flow path. The exhaust gas heat recycling device also includes an exhaust valve arranged in an upstream end in the flowing direction of exhaust gas in the middle cylinder, so that exhaust gas flowing can be switched between the heat recycling flow path and the bypass flow path.
Description
Technical field
The present invention relates to a kind of exhaust gas heat recovery device, this exhaust gas heat recovery device arrives the freezing mixtures such as cooling water such as motor by the exhaust heat recovery of motor.
Background technique
In the prior art, the exhaust gas heat recovery devices such as device of the exhaust heat of the known internal-combustion engine (for example motor car engine, hereinafter will be referred to as motor) such as recovery automobile.This exhaust gas heat recovery device is arranged in the intermediate portion of engine exhaust pipe, to carry out heat exchange coming between motor and the exhaust (gas of discharge) by outlet pipe and the cooling water of motor.For example, in order promptly motor to be carried out the object of warm-up operation, the exhaust heat reclaiming via the cooling water of motor is used to improve rapidly the temperature of the cooling water of motor when the state of cooling, and the exhaust heat reclaiming via the cooling water of motor is also used to car chamber to heat.
Now the actual exhaust gas heat recovery device using is divided into following two types roughly: at patent documentation 1(TOHKEMY 2010-31671 communique) in disclosed the first conventional art (all as shown in fig. 5) and at patent documentation 2(TOHKEMY 2001-30741 communique) in disclosed the second conventional art (not shown herein).About these two kinds of technology, consider cost etc., the conventional art of the first kind is main flow.
Exhaust heat recovery unit 100(Fig. 5 of the first conventional art) comprising: inner cylinder portion 101, it is formed for the bypass flow path (or flow path) 104 by exhaust; Outlet valve 102, its downstream side in inner cylinder portion 101 opens and closes bypass flow path 104; Urceolus portion 103, it is spaced apart and arranged in the outer circumferential side of inner cylinder portion 101; And heat exchange department (exhaust heat recovery stream or path 105 and 106 and cooling water stream or flow path 107 and 108), it is arranged between inner cylinder portion 101 and urceolus portion 103.
In order to reclaim exhaust heat, closed row air valve 102, the exhaust that imports to inner cylinder portion 101 sequentially flows to the first exhaust heat recovery stream 105 and the second exhaust heat recovery stream 106 of the periphery that is arranged at inner cylinder portion 101 by being formed on a large amount of aperture 109 of the sidepiece of inner cylinder portion 101, make in exhaust and flow through and carry out heat exchange between interior cooling water stream 107 and the cooling water of outer cooling water stream 108.
Due to the main purpose of exhaust heat recovery unit 100 being set, be warm-up the engine and heating car chamber when the engine start as mentioned above, therefore from engine start through after a certain scheduled time, once when the demand of preheating or heating reduces, just discharge (eliminating) exhaust.
When getting rid of exhaust heat, open valve 102, the exhaust that imports to inner cylinder portion 101 is directly discharged to downstream side, makes exhaust can not flow to the first heat recovery stream 105 and the second heat recovery stream 106.As a result, suppress the unnecessary rising of cooling water temperature, and prevented the pressure loss of exhaust.
On the other hand, in the exhaust gas heat recovery device (the hot storage system of vehicle) of the second conventional art, the chilled water unit of motor comprises heat recovery units and thermal accumulator.Heat recovery units is arranged so that can carry out mode, the part along two-part of the vent systems bifurcated from motor of heat exchange between the exhaust of discharging from motor and the cooling water of motor.
Yet, in traditional technology, still exist while making exhaust gas heat recovery device after exhaust gas heat recovery device meets the object of warm-up the engine and heating car chamber, at motor stable operation and high load operation and reclaim constantly exhaust heat to realize the demand that improves fuel efficiency.For example, this demand is applicable to be mounted with the situation of the vehicle of rankine cycle system, and in rankine cycle system, exhaust heat is recovered to cooling water consistently, and the heat of recovery is used as the thermal source of rankine cycle heater.
Yet, in the first conventional art and the second conventional art, if attempt to reclaim constantly exhaust heat when motor stable operation, there is following problem.
The first, cooling water is traveling the cooling meeting of wind and reduces heat recovery efficiency.
Namely, at motor, be arranged in the vehicle of front side, from vehicle front side, the lower surface through floor extends to rear side outlet pipe, so exhaust heat recovery unit 100 is disposed in the lower surface on floor.Yet, due to the Flow Structure Nearby of cooling water in the urceolus portion 103 of exhaust heat recovery unit 100, so the sailing by force producing when motor stable operation and high speed operation is easy to the cooling cooling water that has reclaimed exhaust heat.As a result, the thermal loss that causes exhaust heat recovery Efficiency Decreasing will be caused.The conventional art of Second Type also will cause this less desirable problem, because of but inconvenient.
The second, the pressure loss of exhaust and cooling water is large.
Namely, the exhaust side in exhaust heat recovery unit 100, exhaust flow to the first exhaust heat recovery stream 105 by aperture 109, and then, exhaust stream upstream side is turned back and is flow to the second exhaust heat recovery stream 106, and this can cause the pressure loss large.As a result, particularly when operating, high engine load can cause the reduction of output and fuel efficiency.In addition,, at cooling water side, because the cross section of interior cooling water stream 107 and outer cooling water stream 108 is narrow and small, so cooling water stands the large pressure loss and high pump load, this also causes the problem that fuel efficiency reduces.The second conventional art also will cause this reduction, because of but inconvenient.
In addition, though when exhaust gas heat recovery device be the type that reclaims constantly exhaust heat during in motor stable operation, still expect that exhaust gas heat recovery device can be in response to easily control the yield of exhaust heat from the requirement of rankine cycle system etc.
Summary of the invention
Consider that the above-mentioned situation running in prior art makes the present invention, the object of the present invention is to provide following exhaust gas heat recovery device: it can prevent from reclaiming hot amount because the impact of the wind that travels reduces, can reduce and carry out the exhaust of heat exchange and the pressure loss of freezing mixture, and can control simply the hot amount that reclaims.
According to the present invention, by providing following exhaust gas heat recovery device can realize above and other object, this exhaust gas heat recovery device comprises: inner cylinder portion, and freezing mixture flows in described inner cylinder portion; Intermediate cylinder portion, the compartment of terrain of the described inner cylinder portion regulation of its distance is arranged in the outside of described inner cylinder portion, is formed with heat recovery stream, so that the freezing mixture by described inner cylinder portion reclaims by the heat of the exhaust of importing between described intermediate cylinder portion and described inner cylinder portion; Urceolus portion, the compartment of terrain of the described intermediate cylinder of its distance portion regulation is arranged in the outside of described intermediate cylinder portion, between described urceolus portion and described intermediate cylinder portion, forms bypass flow path, and the exhaust of shunting is flowed in described bypass flow path; And outlet valve, it is arranged in the upstream extremity on the flow direction of the exhaust in described intermediate cylinder portion, to switch flowing of exhaust between described heat recovery stream and described bypass flow path.
In aspect above-mentioned, described exhaust gas heat recovery device can also comprise static mixer, and described static mixer is built in described inner cylinder portion and to stir described freezing mixture, it is flowed.
Preferably, described outlet valve can comprise valve body and be arranged on the valve body rod of the substantial middle position of described valve body, and described valve body rod is configured in the width direction of described intermediate cylinder portion or the substantial middle position in diametric(al).
Preferably, described outlet valve can comprise a plurality of valve assemblys of two-door structure form, described in each, valve assembly includes valve body and the valve body rod that is arranged on the end of described valve body, described valve body rod described in each in valve assembly is all configured in the width direction of described intermediate cylinder portion or the end in diametric(al), when described outlet valve is completely closed, by the described valve body of described valve assembly, block the upstream extremity on the flow direction of the exhaust in described intermediate cylinder portion, on the other hand, when described outlet valve is opened completely, the tip portion of the described valve body in described valve assembly is configured to approach described urceolus portion, roughly to block the upstream extremity on the flow direction of the exhaust in described bypass flow path.
According to the present invention with said structure and feature, the inner cylinder portion of coolant flow warp is sequentially covered by heat recovery stream and bypass flow path, wherein, described heat recovery stream forms by inner cylinder portion with intermediate cylinder portion, and described bypass flow path is formed by intermediate cylinder portion and urceolus portion.This amount that makes it possible to prevent the recovery heat that reclaimed by freezing mixture is because the impact of the wind that travels reduces.In addition,, because heat recovery stream forms straight line shape, so exhaust stream flows swimmingly in heat recovery stream, and in the inner cylinder portion of coolant flow warp, also guaranteed the section area of stream.This makes it possible to reduce the pressure loss of exhaust and freezing mixture.In addition, by adjusting the opening degree of outlet valve, adjust thus exhaust air flow to the flow in heat recovery stream, can control simply the heat recovery amount being reclaimed by freezing mixture.
Essence of the present invention, further feature and beneficial effect will be clearer from the following explanation made from reference to accompanying drawing.
Accompanying drawing explanation
In the accompanying drawings:
Fig. 1 represent first embodiment of the invention, the exhaust gas heat recovery device in non-heat recovery state, wherein, (A) of Fig. 1 is the longitdinal cross-section diagram of exhaust gas heat recovery device, (B) of Fig. 1 is along the sectional view of the line I-I intercepting of Fig. 1 (A);
Fig. 2 represent first embodiment of the invention, the exhaust gas heat recovery device in heat recovery state, wherein, (A) of Fig. 2 is the longitdinal cross-section diagram of exhaust gas heat recovery device, (B) of Fig. 2 is along the sectional view of the line II-II intercepting of Fig. 2 (A);
Fig. 3 represent second embodiment of the invention, the exhaust gas heat recovery device in non-heat recovery state, wherein, (A) of Fig. 3 is the longitdinal cross-section diagram of exhaust gas heat recovery device, and (B) of Fig. 3 is along the sectional view of the line III-III intercepting of Fig. 3 (A);
Fig. 4 represent second embodiment of the invention, the exhaust gas heat recovery device in heat recovery state, wherein, (A) of Fig. 4 is the longitdinal cross-section diagram of exhaust gas heat recovery device, (B) of Fig. 4 is along the sectional view of the line VI-VI intercepting of Fig. 4 (A); And
Fig. 5 is the sectional view that the exhaust heat recovery unit of first kind conventional art is shown.
Embodiment
Below, embodiments of the present invention are described with reference to the accompanying drawings.
[the first mode of execution (Fig. 1 and Fig. 2)]
Referring to Fig. 1 and Fig. 2, the first mode of execution of the present invention is described.
See figures.1.and.2, the exhaust gas heat recovery device 10 of present embodiment roughly comprises inner cylinder portion 11, intermediate cylinder portion 12, urceolus portion 13 and outlet valve 14.The exhaust recovery device 10 with above structure for when engine start and motor stable operation and the high load operation constantly by the heat recovery of the exhaust Zi in unshowned motor (gas of discharge) 1 to freezing mixture (being the cooling water 2 of motor in the present embodiment), the heat reclaiming is used to warm-up the engine and heating car chamber, and the thermal source that is used as rankine cycle heater.
For example, inner cylinder portion 11 forms cylindric, and cooling water 2 flows and the built-in static mixer 15 of inner cylinder portion 11 in inner cylinder portion 11.Static mixer 15 is by engaging a plurality of right twist blade 15A that reverse to the right and forming to the left handed twist blade 15B of left handed twist, and right twist blade and left handed twist blade be alternate configurations in the axial direction.The right twist blade 15A of adjacency and the angle between left handed twist blade 15B are for example 90 degree.Therefore, in inner cylinder portion 11, mobile cooling water 2 stirs by the static mixer 15 being built in inner cylinder portion 11.
For example, intermediate cylinder portion 12 also forms cylindric, and intermediate cylinder portion 12 is disposed at the outer circumferential side of inner cylinder portion 11 apart from the compartment of terrain of inner cylinder portion 11 regulations.Heat recovery stream 16 is formed between intermediate cylinder portion 12 and inner cylinder portion 11.Heat recovery stream 16 is constructed such that the cooling water 2 in inner cylinder portion 11 reclaims the heat of the exhaust 1 importing by heat exchange operation (will only be called heat exchange hereinafter).
For example, urceolus portion 13 also forms cylindric, and urceolus portion 13 is disposed at the outer circumferential side of intermediate cylinder portion 12 apart from the compartment of terrain of intermediate cylinder portion 12 regulations.Bypass flow path 17 is formed between urceolus portion 13 and intermediate cylinder portion 12, makes not import in heat recovery stream 16 and the exhaust 1 of shunting is flowed in bypass flow path 17.
In addition, outlet valve 14 has discoid valve body 18 and the valve body rod 19 that is arranged on the approximate center position (for example, diametrical position) of valve body 18.Outlet valve 14 is arranged in the upstream extremity on the flow direction of the exhaust 1 in intermediate cylinder portion 12.More specifically, the upstream extremity on the flow direction of the exhaust 1 of the valve body rod 19 of outlet valve 14 in intermediate cylinder portion 12 can be supported on the diametric(al) of intermediate cylinder portion 12 or the approximate center position on width direction (being diametric(al) D in the present embodiment) rotationally.
As shown in Fig. 1 (A) and Fig. 1 (B), intermediate cylinder portion 12 has upstream side opening end, the valve body 18 of outlet valve 14 is vertically arranged in this upstream side open end with the axle center O of intermediate cylinder portion 12, and in this configuration, the opening of outlet valve 14 is set to complete closed state.According to this configuration of valve body 18, the exhaust 1 that imports to urceolus portion 13 is deflated valve body 18 obstructions of valve 14, make exhaust 1 can not flow to the recovery stream 16 in intermediate cylinder portion 12, but the bypass flow path 17 that roughly all the exhaust 1 of amount is flowed through in urceolus portion 13 as shown in the arrow A of Fig. 1 (A).Therefore, the heat of exhaust 1 is recycled to the cooling water in inner cylinder portion 11 hardly.
When the valve body 18 of outlet valve 14 is during in the parallel position of the axle center O with intermediate cylinder portion 12, the opening of outlet valve 14 is set to full open position (Fig. 2).In this case, respectively as shown in the arrow B and arrow C of Fig. 2 (A), the exhaust 1 that imports to urceolus portion 13 flow through the heat recovery stream 16 in intermediate cylinder portion 12 and the bypass flow path 17 of flowing through in urceolus portion 13, the heat of the exhaust 1 of the heat recovery stream 16 of flowing through is recycled at the interior mobile cooling water 2 of inner cylinder portion 11 by heat exchange operation.
According to the state of the axle center O quadrature from intermediate cylinder portion 12 to the opening degree that is set as the outlet valve 14 of assigned position in the scope of the state parallel with axle center O, exhaust 1 in urceolus portion 13 flow to the heat recovery stream 16 in intermediate cylinder portion 12, and the heat of exhaust 1 is recycled to cooling water mobile in inner cylinder portion 11 2 by heat exchange operation.
According to the structure of above-mentioned the first mode of execution, realized following beneficial effect (1) to (5).
(1) the heat recovery stream 16 that the inner cylinder portion 11 that cooling water 2 is flowed through is formed by inner cylinder portion 11 and intermediate cylinder portion 12 covers, and the bypass flow path 17 that heat recovery stream 16 is further formed by intermediate cylinder portion 12 and urceolus portion 13 covers.Therefore, can prevent that the recovery heat that reclaimed by cooling water 2 is because the impact of the wind that travels in urceolus portion 13 flows outside reduces.As a result, improved the reuse efficiency of exhaust heat.
(2) the heat recovery stream 16 being formed by inner cylinder portion 11 and intermediate cylinder portion 12 forms straight line shape, exhaust 1 is flowed reposefully in heat recovery stream 16, and this stream have enough large section area with built-in static mixer 15 in the inner cylinder portion 11 of being flowed through at cooling water 2.Therefore, can reduce both pressure losses of exhaust 1 and cooling water 2.As a result, can prevent from reducing output and fuel efficiency when motor stable operation and high load operation.Therefore, provide the heat recovering device 10 that carries out lasting heat recovery while being adapted at motor stable operation and high load operation.
(3) by adjusting the opening degree of outlet valve 14, can adjust the flow that flows into the exhaust 1 in heat recovery stream 16, therefore, can easily control by the heat recovery amount reclaiming at the interior mobile cooling water 2 of inner cylinder portion 11.As a result, when the heat from exhaust gas recovery is used as the thermal source of rankine cycle heater, can control the desired heat of rankine cycle heater.
(4) the built-in stirring cooling water 2 of inner cylinder portion 11 make the mobile static mixer of cooling water 2 15, thereby improved the exhaust 1 of heat recovery stream 16 and the efficiency of the heat exchange between the cooling water 2 in inner cylinder portion 11 in inner cylinder portion 11 outsides of flowing through.Therefore, can increase the heat reclaiming from exhaust 1 by cooling water 2.
(5) outlet valve 14 is arranged in the upstream extremity place on the flow direction of the exhaust 1 in intermediate cylinder portion 12, in this state, and the mediate approximate center position of diametric(al) D of a portion 12 of the valve body rod 19 that is arranged on the approximate center position of valve body 18.Therefore, during heat recovery stream 16 in exhaust 1 flows into intermediate cylinder portion 12, thereby exhaust 1 is stirred and is entered turbulent condition by valve body 18 and valve body rod 19.The heat that as a result, can be increased in the exhaust 1 that enters turbulent condition in heat recovery path 16 is recycled to the heat recovery amount at the interior mobile cooling water 2 of inner cylinder portion 11.
[the second mode of execution (Fig. 3 and Fig. 4)]
Referring to Fig. 3 and Fig. 4, the second mode of execution is described.More specifically, (A) of Fig. 3 illustrates longitudinal section second embodiment of the invention, the exhaust gas heat recovery device in non-heat recovery state, and (B) of Fig. 3 is along the sectional view of the line III-III of Fig. 3 (A).(A) of Fig. 4 is the longitudinal section that the exhaust gas heat recovery device of (B) in (A) heat recovery state, Fig. 3 and Fig. 3 is shown, and (B) of Fig. 4 is along the sectional view of the line IV-IV of Fig. 4 (A).
In the second mode of execution shown in Fig. 3 and Fig. 4, represented by identical reference character with composition member in the first mode of execution or corresponding composition member or the element of element, to simplify or to omit the explanation to this composition member or element.
The exhaust gas heat recovery device 20 of the second mode of execution and the difference of the first mode of execution are: intermediate cylinder portion 21 and urceolus portion 22 form rectangular drum like, and outlet valve 23 comprises a plurality of valve assemblys 24.
In the present embodiment, each valve assembly 24 is provided with square tabular valve body 25 and is arranged on the valve body rod 26 of valve body 25 ends, and the valve assembly 24 of present embodiment is for example with the configuration of two-door structure form, to form thus a pair of valve assembly 24 of outlet valve 23.
In above structure, the upstream extremity place on the flow direction of the exhaust 1 of the valve body rod 26 of each valve component 24 in intermediate cylinder portion 21 is configured in the width direction of intermediate cylinder portion 21 or the end in diametric(al) (being width direction W in present embodiment).
More specifically, the valve body rod 26 of the valve body of a valve assembly 24 rod 26 and another valve assembly 24 is disposed at respectively the upper contrary end of width direction W of intermediate cylinder portion 21, makes these valve assemblys 24 form two-door structure.
In addition the valve body 25 that, forms all valve assemblys 24 of outlet valve 23 is designed such that the cross section of the stream at the upstream extremity place on the area of valve body 25 and flow direction that shape is equal to or greater than the exhaust 1 in intermediate cylinder portion 21.Therefore,, when outlet valve 23 is completely closed ((A) of Fig. 3 and (B) of Fig. 3), the cross section of the stream at the upstream extremity place on the flow direction of the exhaust 1 in intermediate cylinder portion 21 is blocked by the valve body 25 of all valve assemblys 24.In this configuration, as shown in the arrow P of Fig. 3 (A), flow through bypass flow path 17 and can not flow to heat recovery stream 16 of the exhaust 1 that imports to urceolus portion 22.
As shown in Fig. 4 (A) and Fig. 4 (B), the valve body 25 that forms all valve assemblys 24 of outlet valve 23 is configured to have the tip portion 25A that approaches urceolus portion 22 when outlet valve 23 is opened completely, makes upstream extremity on the flow direction of the exhaust 1 in bypass flow path 17 almost by total blockage.Therefore, when outlet valve 23 is opened completely, although the exhaust 1 in urceolus portion 22 can not flow in bypass flow path 17, as shown in the arrow Q of Fig. 4 (A), exhaust 1, by valve body 25 guiding of valve assembly 24, makes roughly all exhausts 1 of amount flow into heat recovery stream 16.
In addition, in the present embodiment, heat recovery stream 16 is also formed between inner cylinder portion 11 and intermediate cylinder portion 21, and bypass flow path 17 is formed between intermediate cylinder portion 21 and urceolus portion 22.
According to the structure of above-mentioned the second mode of execution and configuration, except the beneficial effect (1) identical with the first mode of execution is to (4), also realized following beneficial effect (6).
(6) when outlet valve 23 is opened completely, the tip portion 25A of the valve body 25 in all valve assemblys 24 approaches urceolus portion 22, and the upstream extremity on the flow direction of the exhaust 1 in bypass flow path 17 is roughly blocked by the valve body 25 of all valve assemblys 24.Therefore, the flow set of the exhaust 1 of the interior side inflow bypass flow path 17 from urceolus portion 22 can be become be roughly zero, thus the whole exhausts 1 in urceolus portion 22 be guided to heat recovery stream 16.As a result, can increase significantly the heat recovery amount that cooling water mobile in inner cylinder portion 11 2 reclaims from exhaust 1.
Be also noted that, the invention is not restricted to above-mentioned mode of execution, in the situation that not departing from scope of the present invention, can make many other change or modification.
For example, in the first mode of execution and the second mode of execution, can on the outer surface of inner cylinder portion 11, arrange such as fin etc. concavo-convex further to increase the heat recovery amount from exhaust 1.In addition, inner cylinder portion 11, intermediate cylinder portion 12 and 21 and the sectional shape of urceolus portion 13 and 22 can be any one in circle and polygonal.
Claims (4)
1. an exhaust gas heat recovery device, it comprises:
Inner cylinder portion, freezing mixture flows in described inner cylinder portion;
Intermediate cylinder portion, the compartment of terrain of the described inner cylinder portion regulation of its distance is arranged in the outside of described inner cylinder portion, is formed with heat recovery stream, so that the freezing mixture by described inner cylinder portion reclaims by the heat of the exhaust of importing between described intermediate cylinder portion and described inner cylinder portion;
Urceolus portion, the compartment of terrain of the described intermediate cylinder of its distance portion regulation is arranged in the outside of described intermediate cylinder portion, between described urceolus portion and described intermediate cylinder portion, forms bypass flow path, and the exhaust of shunting is flowed in described bypass flow path; And
Outlet valve, it is arranged in the upstream extremity on the flow direction of the exhaust in described intermediate cylinder portion, to switch flowing of exhaust between described heat recovery stream and described bypass flow path.
2. exhaust gas heat recovery device according to claim 1, is characterized in that, described exhaust gas heat recovery device also comprises static mixer, and described static mixer is built in described inner cylinder portion and to stir described freezing mixture, it is flowed.
3. exhaust gas heat recovery device according to claim 1 and 2, it is characterized in that, described outlet valve comprises valve body and is arranged on the valve body rod of the substantial middle position of described valve body, and described valve body rod is configured in the width direction of described intermediate cylinder portion or the substantial middle position in diametric(al).
4. exhaust gas heat recovery device according to claim 1 and 2, it is characterized in that, described outlet valve comprises a plurality of valve assemblys of two-door structure form, described in each, valve assembly includes valve body and the valve body rod that is arranged on the end of described valve body, described valve body rod described in each in valve assembly is all configured in the width direction of described intermediate cylinder portion or the end in diametric(al), when described outlet valve is completely closed, by the described valve body of described valve assembly, block the upstream extremity on the flow direction of the exhaust in described intermediate cylinder portion, on the other hand, when described outlet valve is opened completely, the tip portion of the described valve body in described valve assembly is configured to approach described urceolus portion, roughly to block the upstream extremity on the flow direction of the exhaust in described bypass flow path.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012-176351 | 2012-08-08 | ||
| JP2012176351A JP2014034922A (en) | 2012-08-08 | 2012-08-08 | Exhaust heat recovery device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103573355A true CN103573355A (en) | 2014-02-12 |
| CN103573355B CN103573355B (en) | 2016-01-20 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310332131.5A Expired - Fee Related CN103573355B (en) | 2012-08-08 | 2013-08-01 | Exhaust gas heat recovery device |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP2014034922A (en) |
| CN (1) | CN103573355B (en) |
| DE (1) | DE102013107868B4 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107002542A (en) * | 2014-12-03 | 2017-08-01 | 双叶产业株式会社 | Exhaust gas heat recovery device |
| CN108026821A (en) * | 2016-01-22 | 2018-05-11 | 双叶产业株式会社 | Exhaust gas heat recovery device |
| CN110391701A (en) * | 2018-04-19 | 2019-10-29 | 铃木株式会社 | Rotating electric machine |
| CN111602024A (en) * | 2018-01-15 | 2020-08-28 | 株式会社电装 | Heat storage device |
| CN116517662A (en) * | 2023-05-06 | 2023-08-01 | 徐州瑞田工程机械有限公司 | Tail gas separation and filtration device and application method thereof |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6227450B2 (en) * | 2014-03-14 | 2017-11-08 | フタバ産業株式会社 | Heat recovery unit |
| CN109000493A (en) * | 2018-08-27 | 2018-12-14 | 瑞安市阀门厂 | Compact high efficient vertical heat exchanging device |
| CN112360605B (en) * | 2020-10-30 | 2021-10-26 | 中国重型汽车集团有限公司 | Multistage formula tail gas aftertreatment device |
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- 2012-08-08 JP JP2012176351A patent/JP2014034922A/en active Pending
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- 2013-07-23 DE DE102013107868.0A patent/DE102013107868B4/en active Active
- 2013-08-01 CN CN201310332131.5A patent/CN103573355B/en not_active Expired - Fee Related
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| DE29714478U1 (en) * | 1997-08-13 | 1997-10-09 | Heinrich Gillet Gmbh & Co Kg, 67480 Edenkoben | Heat exchangers in exhaust systems of internal combustion engines |
| EP0942156A1 (en) * | 1998-03-11 | 1999-09-15 | Ecia - Equipements Et Composants Pour L'industrie Automobile | Exhaust heat exchanger device |
| US6330910B1 (en) * | 1999-03-03 | 2001-12-18 | Easton Bennett | Heat exchanger for a motor vehicle exhaust |
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| CN107002542A (en) * | 2014-12-03 | 2017-08-01 | 双叶产业株式会社 | Exhaust gas heat recovery device |
| CN107002542B (en) * | 2014-12-03 | 2019-08-02 | 双叶产业株式会社 | Exhaust gas heat recovery device |
| CN108026821A (en) * | 2016-01-22 | 2018-05-11 | 双叶产业株式会社 | Exhaust gas heat recovery device |
| CN111602024A (en) * | 2018-01-15 | 2020-08-28 | 株式会社电装 | Heat storage device |
| CN110391701A (en) * | 2018-04-19 | 2019-10-29 | 铃木株式会社 | Rotating electric machine |
| CN110391701B (en) * | 2018-04-19 | 2021-05-25 | 铃木株式会社 | Rotating electrical machine |
| CN116517662A (en) * | 2023-05-06 | 2023-08-01 | 徐州瑞田工程机械有限公司 | Tail gas separation and filtration device and application method thereof |
| CN116517662B (en) * | 2023-05-06 | 2024-02-06 | 江苏乾景环保科技有限公司 | Tail gas separation and filtration device and application method thereof |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102013107868A1 (en) | 2014-02-13 |
| CN103573355B (en) | 2016-01-20 |
| JP2014034922A (en) | 2014-02-24 |
| DE102013107868B4 (en) | 2024-02-08 |
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