CN110300878A - Heat exchanger - Google Patents
Heat exchanger Download PDFInfo
- Publication number
- CN110300878A CN110300878A CN201880011969.5A CN201880011969A CN110300878A CN 110300878 A CN110300878 A CN 110300878A CN 201880011969 A CN201880011969 A CN 201880011969A CN 110300878 A CN110300878 A CN 110300878A
- Authority
- CN
- China
- Prior art keywords
- fin
- heat exchanger
- air
- air flue
- coolant
- 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.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- 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
- F28D7/16—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 in parallel spaced relation
- F28D7/1684—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 in parallel spaced relation the conduits having a non-circular cross-section
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/001—Casings in the form of plate-like arrangements; Frames enclosing a heat exchange core
-
- 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
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
- F28D2021/0082—Charged air coolers
-
- 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
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/0081—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by a single plate-like element ; the conduits for one heat-exchange medium being integrated in one single plate-like element
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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
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
- F28F1/128—Fins with openings, e.g. louvered fins
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
- F28F1/424—Means comprising outside portions integral with inside portions
- F28F1/426—Means comprising outside portions integral with inside portions the outside portions and the inside portions forming parts of complementary shape, e.g. concave and convex
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/02—Tubular elements of cross-section which is non-circular
- F28F2001/027—Tubular elements of cross-section which is non-circular with dimples
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2215/00—Fins
- F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
- F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
- F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
- F28F3/027—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements with openings, e.g. louvered corrugated fins; Assemblies of corrugated strips
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
- F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
- F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
- F28F3/044—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being pontual, e.g. dimples
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The heat exchange of heat exchanger (1) progress air and coolant liquid.Air intake (131,171) is arranged in the side of heat exchanger (1), and supplies air to air flue.Air outlet slit (141,181) is arranged in the other side of heat exchanger (1), and air is discharged from air flue.The position in air outlet slit (141,181) side of heat exchanger (1) is arranged in coolant inlet (41,45), and supplies coolant liquid to coolant channels.The position in air intake (131,171) side of heat exchanger (1) is arranged in cooling liquid outlet (42,46), and coolant liquid is discharged from coolant channels.The region of air intake (the 131,171) side of the first fin (31) configuration in air flue.Big the second fin (32) of the first fin of thermal conductivity ratio is configured from air outlet slit (the 141,181) side in air flue towards air intake (131,171) side.
Description
Related application it is cross-referenced
The application based on Japanese patent application 2017-65497 filed on March 29th, 2017, make by contents
The application is introduced for reference.
Technical field
This disclosure relates to carry out the heat exchanger of the heat exchange of air and coolant liquid.
Background technique
It goes forward side by side the heat exchange of the coolant liquids such as the air such as gas or exhaust and cooling water of advancing conventionally, there is known being equipped on vehicle etc.
Heat exchanger.
Heat exchanger documented by patent document 1 is the opposite flow pattern for being configured to pressurized air and cooling water and flowing opposite to each other
Water-cooled intercooler.In general, intercooler is distinguished according to conditions such as the mounting spaces of vehicle using documented by patent document 1
The intercooler of the intercooler of opposite flow pattern and the positive AC type constituted in such a way that pressurized air and cooling water orthogonally flow.
Existing technical literature
Patent document
Patent document 1:EP1707911A1 specification
Summary of the invention
Typically for intercooler, as long as the identical condition of heat exchange performance, then compared with the intercooler of positive AC type,
The length of the air flue of the intercooler of opposite flow pattern is long, and flow path cross sectional area also forms smaller, therefore the pressure of air flue
Power loss becomes larger.If the pressure loss for the air flue that intercooler has is big, there are problems that reducing engine performance.
Assuming that keeping the spacing of the fin for the air flue for being set to intercooler thicker, then the pressure loss of air flue becomes
It is small, but heat exchange performance reduces.In contrast, if the spacing of the fin is made to become close, heat exchange performance is improved, but air flue
The pressure loss increase.
Being designed to provide for the disclosure a kind of can reduce air flue in the case where not reducing heat exchange performance
The heat exchanger of the pressure loss.
According to the disclosure viewpoint, a kind of heat exchanger for the heat exchange carrying out air and coolant liquid has:
Air intake, which is set to the side of heat exchanger, and supplies air to air flue；
Air outlet slit, which is set to the other side of heat exchanger, and air is discharged from air flue；
Coolant inlet, the coolant inlet are set to the position of the air outlet slit side of heat exchanger, and logical to coolant liquid
Road supplies coolant liquid；
Cooling liquid outlet, the cooling liquid outlet are set to the position of the air inlet side of heat exchanger, and logical from coolant liquid
Coolant liquid is discharged in road；
First fin, first fin are configured at the region of the air inlet side in air flue；And
Second fin, which configures in air flue from air outlet slit side towards air inlet side and heat transfer
Rate is bigger than the first fin.
Inventor to the entrance from air flue to outlet be provided with same fin opposite flow pattern heat exchanger (with
Under, referred to as " previous heat exchanger ") investigate the change rate of the air themperature flowed in air flue.Its result it is found that
In previous heat exchanger, the change rate of air themperature becomes in predetermined range from air outlet slit side towards air inlet side
It obtains minimum.This is because in previous heat exchanger, in the air outlet slit side of air flue, the temperature of air and coolant liquid
Difference becomes smaller, and heat exchanger effectiveness reduces.
Therefore, in the heat exchanger of said one viewpoint, heat transfer is configured from air outlet slit side towards air inlet side
The second big fin of rate.The heat exchanger effectiveness in the region configured with the second fin is got higher as a result, the heat exchange of heat exchanger entirety
Performance improves.In addition, by the region that the first small fin of pyroconductivity is configured to air inlet side, the pressure of air flue
Loss is reduced.Therefore, if the heat of the heat exchange performance of the heat exchanger based on this viewpoint and previous heat exchanger is handed over
Transsexual to be set as identical condition, then the heat exchanger based on a viewpoint can reduce sky compared with previous heat exchanger
The pressure loss of gas access.In addition, if the heat exchanger based on a viewpoint keeps air logical relative to previous heat exchanger
The pressure loss on road is equal, then also can be improved the heat exchange performance of heat exchanger entirety.
Detailed description of the invention
Fig. 1 is the perspective view of the heat exchanger of first embodiment.
Fig. 2 is the exploded view of heat exchanger.
Fig. 3 is the figure of the partial cross section for the pipe for indicating that heat exchanger has.
Fig. 4 is an example for the fin that heat exchanger has.
Fig. 5 is an example for the fin that heat exchanger has.
Fig. 6 is an example for the fin that heat exchanger has.
Fig. 7 is an example for the fin that heat exchanger has.
Fig. 8 is an example for the fin that heat exchanger has.
Fig. 9 is the figure for indicating the state of temperature change of the air flowed in the air flue of previous heat exchanger
Table.
Figure 10 is the figure for indicating the state of temperature change of the air flowed in the air flue of previous heat exchanger
Table.
Figure 11 is to indicate that the temperature of the per unit length of the air flowed in the air flue of previous heat exchanger becomes
The chart of rate.
Figure 12 is to indicate that the temperature of the per unit length of the air flowed in the air flue of previous heat exchanger becomes
The chart of rate.
Figure 13 is the figure for indicating the experimental condition for the effect for confirming the heat exchanger of first embodiment.
Figure 14 is to indicate to flow in the heat exchanger and the previous respective air flue of heat exchanger of first embodiment
The chart of the state of the temperature change of dynamic air.
Figure 15 is to indicate to flow in the heat exchanger and the previous respective air flue of heat exchanger of first embodiment
The chart of the state of the pressure loss of dynamic air.
Figure 16 is the exploded view of the heat exchanger of second embodiment.
Figure 17 is the exploded view of the heat exchanger of third embodiment.
Specific embodiment
Hereinafter, being illustrated based on attached drawing to embodiment of the present disclosure.In addition, each embodiment below each other it
In, identical appended drawing reference is marked to part same to each other or equivalent to be illustrated.
(first embodiment)
First embodiment is illustrated referring to attached drawing.The heat exchanger of present embodiment is mounted in vehicle etc. and goes forward side by side
The water-cooled intercooler gone by air inlet and the heat exchange of the engine cooling water as coolant liquid after compressed.In detail and
Speech, the heat exchanger are to be configured to make air and coolant liquid opposite to each other in the water-cooled for the opposite flow pattern that the inside of shell is flowed
Cooler.
As shown in FIG. 1 to 3, heat exchanger 1 has shell 10, multiple pipes 20, the first fin 31 and second fin 32 etc..
These each components are formed by metals such as aluminium, and each component passes through the engagement such as soldering.
Shell 10 constitutes the shell of heat exchanger 1, has air flue and coolant channels on the inside of it.Shell 10 is by
One~the 4th plate 11~14 is constituted.First plate 11 and the second plate 12 all have side surface part 111,121, from the side surface part 111,121
The both ends upper surface part 112,122 and lower surface portion 113,123 that are extended vertically relative to side surface part 111,121.In addition,
In this specification, side surface part, upper surface part, lower surface portion term be term for explanation, be not offered as heat exchanger 1 and take
It is loaded in the direction of vehicle.
In the state that the first plate 11 and the second plate 12 are oppositely disposed, the upper surface part 112 of the first plate 11 and the second plate 12,
122 end is engaged with each other, and the end of lower surface portion 113,123 is engaged with each other.Third plate 13 with by the first plate 11 and the second plate
12 are formed as the open side engagement of a side of the component of tubular.Multiple air intakes 131 are formed in the third plate 13.Another party
Face, the 4th plate 14 are engaged with the open side of the another party for the component for being formed as its square tube shape.It is formed in the 4th plate 14 multiple
Air outlet slit 141.
The inside of shell 10 is provided with multiple pipes 20.Multiple pipes 20 are formed as flat tubular, in the inside of shell 10
It is laminated at predetermined spaced intervals.The opening of one side of pipe 20 is engaged with multiple air intakes 131 of third plate 13.Pipe 20 it is another
The opening of one side is engaged with the air outlet slit 141 of the 4th plate 14.Therefore, in the present embodiment, it is formed in the interior of multiple pipes 20
The flow path of side is air flue.Air is supplied from the air intake 131 for the side for being set to shell 10 to air flue.In air
The air flowed in access is discharged from the air outlet slit 141 for the other side for being set to shell 10.
The inside of pipe 20 is provided with inner fin 30 (that is, air flue fin 30).In the present embodiment, inner fin
30 are made of the first fin 31 and the second fin 32.First fin 31 is configured at the area of 131 side of air intake in air flue
Domain.In Fig. 3, the length of air flue is recorded as Lt, the length of the first fin 31 is recorded as L1, by the second fin 32
Length is recorded as L2.The length L2 of second fin 32 is 40% or less the length Lt of air flue.That is, the second fin 32 configures
In following range: the range is the air flue than 141 side of slave air outlet slit in air flue towards 131 side of air intake
The 0% of length Lt is big and below 40%.
The pyroconductivity of the first fin of thermal conductivity ratio 31 of second fin 32 is big.As the first fin 31 and the second fin
32, can using plain fin 34 shown in Fig. 4, the fin 35 shown in fig. 5 with shutter, offset fin shown in fig. 6 36,
Various fins such as wave-shaped fins 37 shown in Fig. 7, fin 38 winged shown in Fig. 8.First fin 31 and the second wing
Piece 32 can be variety classes, be also possible to identical type.Relative to the spacing of fin of the first fin 31, make the second fin 32
Spacing of fin is close, so as to increase the heet transfer rate of the second fin 32.Alternatively, the type relative to the first fin 31,
The type of second fin 32 can be set as the big type of pyroconductivity.
The inlet tube 41 as coolant inlet is bonded in the first plate 11 for constituting shell 10.Inlet tube 41 is arranged in shell
The position of 141 side of air outlet slit of body 10.On the other hand, the outlet 42 as cooling water outlet is bonded in the second plate 12.
The position of 131 side of air intake of shell 10 is arranged in outlet 42.Therefore, in the present embodiment, it is formed in shell 10
The flow path in inside and the outside of multiple pipes 20 is coolant channels.Coolant liquid is supplied from inlet tube 41 to coolant channels.Cold
But the coolant liquid flowed in liquid access is discharged from outlet 42.In addition, being provided with fin 40 in coolant channels, (i.e. coolant liquid is logical
Road fin 40).
According to above structure, which is able to carry out the air flowed in air flue and in coolant channels
The heat exchange of the coolant liquid of middle flowing.
In addition, intercooler is in order to improve the boost pressure of the air inlet supplied into the cylinder of engine, it is desirable that reduce air
The pressure loss of access.
In general, in a heat exchanger, if keeping the spacing for the fin for being set to air flue thicker, the pressure of air flue
Loss becomes smaller, but heat exchange performance reduces.In contrast, if becoming the spacing of the fin for the air flue for being set to heat exchanger
Close, then heat exchange performance improves, but the pressure loss of air flue increases.That is, the heat exchange performance of heat exchanger and air are logical
The pressure loss on road has correlativity.Therefore, as long as can be realized the pressure for making air flue relative to previous heat exchanger
Power lose it is equal, make heat exchange performance improve heat exchanger structure, then with this configuration, can make heat exchange performance with
Past heat exchanger is same, reduces the pressure loss of air flue.In addition, in the present specification, previous heat exchanger refers to
The heat exchanger of same fin is provided with from the entrance of air flue to outlet.
Firstly, by experiment and simulation (hereinafter referred to as test) to have investigated the air in previous heat exchanger logical by inventor
The state of the temperature change of the air flowed in road.It the results are shown in Fig. 9~Figure 12.In addition, in the chart of Fig. 9~Figure 12
In, for marking the line of appended drawing reference A~E, the line for being labelled with identical appended drawing reference indicates identical test result.
Fig. 9~Figure 12 indicates the test result tested as follows: using previous heat exchanger, makes the sky of air intake
The air for 5 temperature that temperature degree is 100 °~200 ° flows in air flue, is reduced to the air themperature of air outlet slit
Scheduled target temperature (such as 45 DEG C).Fig. 9 indicates the change of air themperature corresponding with the position of air flue in this experiment
Change.Figure 10 is related to the horizontal axis of the chart of Fig. 9, and air intake is set as 0%, and air outlet slit is set as 100%, is shown with percentage
The each position of air flue.
Figure 11 is to indicate air themperature shown in the chart of Fig. 9 with the rate of temperature change of the per unit length of air flue
The figure of variation.Figure 12 is related to the horizontal axis of the chart of Figure 11, and air intake is set as 0%, air outlet slit is set as 100%, with hundred
The each position for dividing rate to show air flue.
As shown in the part of the label symbol X of Figure 12 surrounded as single dotted broken line, it is known that, in previous heat exchanger,
At 40% position of the length of the air flue from air outlet slit side towards air inlet side, the change rate pole of air themperature
It is small.The reason for this is that the temperature difference of air and coolant liquid becomes smaller in the air outlet slit side of air flue, therefore heat exchanger effectiveness drops
It is low.
Therefore, in the heat exchanger of present embodiment, the second big fin of the first fin of thermal conductivity ratio is configured at
40% range of the length of air flue of the slave air outlet slit side towards air inlet side in air flue, it is true by testing
Recognize its effect.By at this time experimental condition and the results are shown in Figure 13~Figure 15.
The primary condition of test is as follows.
The air themperature of air intake: Tg1=130 DEG C
The pressure of the air of air intake: Pg1=220kPa-a
The flow of the air supplied to air flue: Gg=200g/s
The water temperature of the cooling water of coolant inlet: Tw1=35 DEG C
The flow of the cooling water supplied to coolant channels: Gw=10L/min
Figure 13 is the figure that specific experimental condition is described in the schematic diagram for the heat exchanger for being equivalent to present embodiment.
As shown in figure 13, longitudinal for the inside dimension of the flowing path section of air flue: Ht=130mm, laterally: Wt=60mm, length:
Lt=215mm.
First fin is plain fin, spacing of fin: Fp=1.5mm.The length L1 setting of first fin enters from air
Mouthful towards air outlet slit side air flue length Lt 60% in the range of.
Second fin is offset fin, spacing of fin: Fp=1.5mm.The length L2 setting of first fin goes out from air
Mouthful towards air inlet side air flue length Lt 40% in the range of.
In addition, the heet transfer rate for the first fin that the heat exchanger of present embodiment has has than previous heat exchanger
Fin heet transfer rate it is small.In addition, the heet transfer rate for the second fin that the heat exchanger of present embodiment has is than previous
The heet transfer rate for the fin that heat exchanger has is big.
Figure 14 and Figure 15 indicates the result of the test carried out under experimental condition shown in Figure 13.In Figure 14 and Figure 15,
The temperature change that air corresponding with the position of the air flue of the heat exchanger of present embodiment is indicated with solid line M, with dotted line N
Indicate the variation of air themperature corresponding with the position of the air flue of previous heat exchanger.In addition, the figure of Figure 14 and Figure 15
Air intake is set as 0% by the horizontal axis of table, and air outlet slit is set as 100%, and each position of air flue is shown with percentage.
As shown in figure 14, in the range of 60% of the length from air intake to air flue, the heat of present embodiment is handed over
The air themperature of parallel operation becomes the state higher than the air themperature of previous heat exchanger.But in the length of air flue
60% between air outlet slit, and the air themperature of the heat exchanger of present embodiment becomes the Air Temperature than previous heat exchanger
Spend low state.The temperature Tg2 of the air outlet slit of the heat exchanger of present embodiment becomes 37.6 DEG C, previous heat exchanger
The temperature Tg2 of air outlet slit becomes 41.4 DEG C.Therefore, the temperature Tg2 ratio of the air outlet slit of the heat exchanger of present embodiment with
The temperature of the air outlet slit of past heat exchanger is 3.8 DEG C low.
As shown in figure 15, in the range of 60% of the length from air intake to air flue, the heat of present embodiment is handed over
The pressure loss of the air flue of parallel operation is smaller than the pressure loss of the air flue of previous heat exchanger.But it is logical in air
The 60% of the length on road is between air outlet slit, and the pressure loss of the air flue of the heat exchanger of present embodiment is than previous
The pressure loss of the air flue of heat exchanger is big.As a result, the sky of the heat exchanger of the present embodiment at air outlet slit
The pressure loss of gas access is roughly the same with the pressure loss of the air flue of previous heat exchanger.
According to above-mentioned test result, it may be said that the heat exchanger of present embodiment plays function and effect below.That is, this reality
The heat exchanger of mode is applied relative to previous heat exchanger, the pressure loss of air flue can be made equal, improves heat exchange
The heat exchange performance of device entirety.As described above, the heat exchange performance of heat exchanger is to the pressure loss of air flue with related
Relationship.Therefore, if the heat exchange performance of the heat exchanger of present embodiment and previous heat exchanger is set as identical item
Part, then the heat exchanger of present embodiment can reduce the pressure loss of air flue compared with previous heat exchanger.
In addition, the heat exchanger of present embodiment can be in the first fin 31 and the second fin 32 using different types of
Heat exchanger.Thereby, it is possible to keep the heet transfer rate of the second fin 32 bigger than the heet transfer rate of the first fin 31.
Make the spacing of fin of the second fin 32 relative to the first fin in addition, the heat exchanger of present embodiment can use
The close heat exchanger of 31 spacing of fin.Thereby, it is possible to make heat transmitting of the heet transfer rate of the second fin 32 than the first fin 31
Rate is big.
In addition, the heat exchanger of present embodiment can also be by changing the spacing of fin and type and the of the first fin 31
The spacing of fin and type of two fins 32, to keep the pyroconductivity of the first fin of thermal conductivity ratio 31 of the second fin 32 big.
(second embodiment)
Second embodiment is illustrated.Second embodiment changes heat exchanger 1 relative to first embodiment
Air flue and coolant channels etc. structure.
As shown in figure 16, the heat exchanger 1 of second embodiment has shell 10, multiple pipes 20, the first fin 31, centre
Fin 33 and the second fin 32 etc..
Shell 10 constitutes the shell of heat exchanger 1, has air flue and coolant channels on the inside of it.Shell 10 is by
One duct board 15, second pipe plate 16, the first riveted plating 17 and the second riveted plating 18 are constituted.First pipe plate 15 and second pipe
Plate 16 all have side surface part 151,161, extend vertically from the both ends of the side surface part 151,161 relative to side surface part 151,161
Upper surface part 152,162 and lower surface portion 153,163.In addition, in the present specification, side surface part, upper surface part, lower surface portion
Term be term for explanation, be not offered as the direction that heat exchanger 1 is equipped on vehicle.In first pipe plate 15 and second
In the state that the side surface part 151,161 of duct board 16 is opposite each other, the upper table of first pipe plate 15 and second pipe plate 16
The end of face 152,162 is engaged with each other, and the end of lower surface portion 153,163 is engaged with each other.First riveted plating 17 with by first
Duct board 15 and second pipe plate 16 are formed as the open side engagement of a side of the component of tubular.In first riveted plating 17 formation
There is air intake 171.On the other hand, the second riveted plating 18 and the opening of the another party for the component for being formed as its square tube shape flank
It closes.Air outlet slit 181 is formed in second riveted plating 18.
The inside of shell 10 is provided with multiple pipes 20.Multiple pipes 20 are formed as flat tubular, in the inside of shell 10
It is laminated at predetermined spaced intervals.Air flue is formed between multiple pipe 20.That is, the air flue of second embodiment
It is formed at the flow path of the inside of shell 10 and the outside of multiple pipes 20.
Air flue is provided with outer fin 30 (that is, air flue fin 30).In this second embodiment, outer fin
30 (that is, air flue fins 30) are made of the first fin 31, central fins 33 and the second fin 32.The configuration of first fin 31
The region of 171 side of air intake in air flue.Central fins 33 are configured at the downstream side of the first fin 31.Second fin
32 configurations than 181 side of slave air outlet slit in air flue towards 171 side of air intake air flue length it is 0% big
And in 40% range below.
The first fin of thermal conductivity ratio 31 of second fin 32 and the pyroconductivity of central fins 33 are big.As the first fin
31, the second fin 32, central fins 33, can using as Fig. 4~plain fin shown in Fig. 8 34, the fin 35 with shutter,
Various fins such as offset fin 36, wave-shaped fins 37, fin 38 winged.First fin 31, the second fin 32 and in
Between fin 33 both can be respectively different types, or identical type.Relative to the first fin 31 and central fins
33 spacing of fin keeps the spacing of fin of the second fin 32 close, so as to increase the heet transfer rate of the second fin 32.Or
Person, can also be relative to the first fin 31 and the type of central fins 33, the type for keeping 32 pyroconductivity of the second fin big.
Multiple pipes 20 of stacking are connected in the stacking direction each other by least two access 43,44.It is formed in first
The opening portion being connected to the access 43 of 181 side of air outlet slit in two opening portions of duct board 15 is for multiple pipes 20
Supply the coolant inlet 45 of coolant liquid.On the other hand, it is formed in entering in two opening portions of first pipe plate 15 with air
The opening portion that the access 44 of 171 sides of mouth is connected to is for the cooling liquid outlet 46 from multiple pipes 20 discharge coolant liquid.Therefore,
The coolant channels of two embodiments are formed at the flow path of the inside of multiple pipes 20.According to above structure, 1 energy of heat exchanger
Enough carry out the heat exchange of the air flowed in air flue Yu the coolant liquid flowed in coolant channels.
In Figure 16, the length of air flue is recorded as Lt, the length of the first fin 31 is recorded as L1, by the second wing
The length of piece 32 is recorded as L2, and the length of central fins 33 is recorded as L3.The length L2 of second fin 32 is air flue
40% or less length Lt.In this second embodiment, the second fin 32 is also disposed in than the slave air outlet slit in air flue
181 sides towards 171 side of air intake air flue length it is 0% big and in 40% range below.Therefore, second implements
Mode can also play the function and effect being the same as the above first embodiment.
(third embodiment)
Third embodiment is illustrated.Third embodiment changes outer fin 30 relative to second embodiment
A part of the structure of (that is, air flue fin 30) and pipe 20, other are identical as second embodiment, therefore only to
The different part of two embodiments is illustrated.
As shown in figure 17, in the third embodiment, 171 side of air intake in air flue is formed with not set wing
The aptery panel region 39 of piece.The outer wall for the pipe 20 that the aptery panel region 39 is exposed is provided with multiple recess portions 391 or protrusion 392.
Recess portion 391 is, for example, dent, and protrusion 392 is, for example, rib.The shape of dent or rib, size, number, are not limited to documented by Figure 17
Shape, size, number can use various shape, size, number.In addition it is also possible to which recess portion is only arranged in the outer wall in pipe 20
391 or protrusion 392 in a side.
In the third embodiment, aptery panel region 39 is formed by 171 side of air intake in air flue, it can
Reduce the pressure loss of air flue.In addition, the air of 171 side of air intake of air flue and the temperature difference of coolant liquid are big,
Therefore the reduction for forming heat exchanger effectiveness caused by aptery panel region 39 is smaller.
In addition, in the third embodiment, by the way that recess portion 391 is arranged in the outer wall for being exposed to the pipe 20 of aptery panel region 39
Or protrusion 392, it is able to suppress the reduction of the heat exchanger effectiveness as caused by aptery panel region 39.
In addition, in the third embodiment, the second fin 32 is also disposed in than 181 side of slave air outlet slit in air flue
0% towards the length of the air flue of 171 side of air intake is big and in 40% range below.Therefore, third embodiment
Also function and effect identical with first and second above-mentioned embodiment can be played.
(other embodiments)
The disclosure is not limited to above-mentioned embodiment, can suitably change.In addition, the respective embodiments described above are not
It is independent of each other and is, it, can be appropriately combined other than the case where cannot obviously combining.In addition, in the respective embodiments described above,
The element of embodiment is constituted in addition to obvious necessary situation etc. of especially expressing that be in necessary situation and principle be considered as
Except, the element that is certainly not required to.In addition, in the respective embodiments described above, in for the constituent element for referring to embodiment
In the case where the numerical value such as number, numerical value, amount, range, in addition to especially express be obviously be limited in necessary situation and principle it is specific
The situation of number etc. except, be not limited to the specific number.In addition, in the respective embodiments described above, referring to constituent element
Deng shape, positional relationship etc. whens, be limited to specific shape, positional relationship etc. the case where in addition to especially expressing and in principle
Except situation etc., it is not limited to its shape, positional relationship etc..
(1) in the respective embodiments described above, the example that heat exchanger 1 is applied to water-cooled intercooler is said
It is bright, but not limited to this.Heat exchanger 1 carries out air and cooling such as can be applied to cooler for recycled exhaust gas or heat extraction recover
The various heat exchangers of the heat exchange of liquid.
(2) in the respective embodiments described above, illustrate that heat exchanger 1 has the case where shell 10, but not limited to this.In heat
Exchanger 1 such as the case where the inside of the air inlet pipe or exhaust pipe that are set to engine under, what shell was certainly not required to wants
Part.
(3) in above-mentioned second embodiment, the fin of the air flue of heat exchanger 1 is set to according to the first fin
31, central fins 33, the sequence of the second fin 32, pyroconductivity is big, but not limited to this.The sky for the fin that heat exchanger 1 has
The heet transfer rate that gas exports the second fin 32 of 181 sides is maximum.It, can also be by such as in the structure of second embodiment
According to central fins 33, the sequence of the first fin 31, the second fin 32, spacing of fin or wing are changed in such a way that pyroconductivity becomes larger
The type of piece.
(conclusion)
The first viewpoint according to shown in part or all of above embodiment carries out the heat exchange of air and coolant liquid
Heat exchanger have air intake, air outlet slit, coolant inlet, cooling liquid outlet, the first fin and the second fin.Air
Entrance is set to the side of heat exchanger, supplies air to air flue.Air outlet slit is set to the other side of heat exchanger, from
Air is discharged in air flue.Coolant inlet is set to the position of the air outlet slit side of heat exchanger, supplies to coolant channels
Coolant liquid.Cooling liquid outlet is set to the position of the air inlet side of heat exchanger, and coolant liquid is discharged from coolant channels.First
Fin is configured at the region of the air inlet side in air flue.The second big fin of the first fin of thermal conductivity ratio is logical from air
Air outlet slit side in road is configured towards air inlet side.
According to the second viewpoint, the length of the first fin in air flue is longer than the second fin.
According to third viewpoint, the length of the second fin (32) be in the length than air flue 0% it is big and 40% with
Under range.
According to the 4th viewpoint, heat exchanger is water-cooled intercooler.
According to the 5th viewpoint, the type of the type of the first fin and the second fin is different type.Relative to the first wing
The pyroconductivity of the type of piece, the type of the second fin is big.It is not of the same race by being used in the first fin and the second fin as a result,
The fin of class can make the pyroconductivity of the first fin of thermal conductivity ratio of the second fin big.
According to the 6th viewpoint, the type of the first fin and the second fin is created as making hot transmitting and keeping shape different
The different type of rate.
Keep the spacing of fin of the second fin closeer relative to the spacing of fin of the first fin according to the 7th viewpoint.As a result,
The pyroconductivity of the first fin of thermal conductivity ratio of the second fin can be made big.
According to the 8th viewpoint, heat exchanger is also equipped with multiple pipes of stacking.A side in air flue or coolant channels
It is formed at the flow path of the inside of multiple pipes.Another party in air flue or coolant channels is formed at the outside of multiple pipes
Flow path.
According to the 9th viewpoint, the region other than the region in addition to being provided with the second fin in air flue is formed with not
The aptery panel region of fin is set.The heat exchanger can reduce the pressure damage of air flue using aptery panel region as a result,
It loses.In addition, the air of the air inlet side of air flue and the temperature difference of coolant liquid are big, therefore led because forming aptery panel region
The reduction of the heat exchanger effectiveness of cause is smaller.
According to the tenth viewpoint, the outer wall for the pipe for being exposed to aptery panel region is provided with recess portion or protrusion.Thereby, it is possible to press down
Make the reduction because of heat exchanger effectiveness caused by forming aptery panel region.
According to the 11st viewpoint, heat exchanger is also equipped with shell (10), which constitutes the shell of heat exchanger,
The inside of the shell has air flue and coolant channels.
Claims (11)
1. a kind of heat exchanger carries out the heat exchange of air and coolant liquid, which is characterized in that have:
Air intake (131,171), which is set to the side of the heat exchanger, and supplies sky to air flue
Gas；
Air outlet slit (141,181), which is set to the other side of the heat exchanger, and arranges from the air flue
Air out；
Coolant inlet (41,45), the coolant inlet are set to the position of the air outlet slit side of the heat exchanger, and
Coolant liquid is supplied to coolant channels；
Cooling liquid outlet (42,46), the cooling liquid outlet are set to the position of the air inlet side of the heat exchanger, and
Coolant liquid is discharged from the coolant channels；
First fin (31), first fin are configured at the region of the air inlet side in the air flue；And
Second fin (32), second fin is in the air flue from the air outlet slit side towards the air inlet side
Configuration, and the first fin described in thermal conductivity ratio is big.
2. heat exchanger according to claim 1, which is characterized in that
The length of first fin in the air flue is longer than second fin.
3. heat exchanger according to claim 1 or 2, which is characterized in that
The length of second fin 0% in the length than the air flue is big and in 40% range below.
4. heat exchanger according to any one of claim 1 to 3, which is characterized in that
The heat exchanger is water-cooled intercooler.
5. heat exchanger according to any one of claim 1 to 4, which is characterized in that
First fin and second fin are variety classes,
Relative to the type of first fin, the pyroconductivity of the type of second fin is big.
6. heat exchanger according to claim 5, which is characterized in that
The type of first fin and second fin is following type: being formed as making hot transmitting and keeping shape different
Rate is different.
7. heat exchanger according to any one of claim 1 to 6, which is characterized in that
Relative to the spacing of fin of first fin, keep the spacing of fin of second fin closeer.
8. heat exchanger according to any one of claim 1 to 7, which is characterized in that
Multiple pipes (20) of stacking are also equipped with,
A side in the air flue or the coolant channels is formed at the flow path of the inside of multiple pipes,
Another party in the air flue or the coolant channels is formed at the flow path in the outside of multiple pipes.
9. heat exchanger according to any one of claim 1 to 8, which is characterized in that
The region other than the region in addition to being provided with second fin in the air flue is formed with not set fin
Aptery panel region (39).
10. heat exchanger according to claim 9, which is characterized in that
Multiple pipes (20) of stacking are also equipped with,
The outer wall for the pipe for being exposed to the aptery panel region is provided with recess portion (391) or protrusion (392).
11. heat exchanger according to any one of claim 1 to 10, which is characterized in that
The heat exchanger is also equipped with shell (10), which constitutes the shell of the heat exchanger, in the inside of the shell
With the air flue and the coolant channels.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2017065497A JP2018169073A (en) | 2017-03-29 | 2017-03-29 | Heat exchanger |
| JP2017-065497 | 2017-03-29 | ||
| PCT/JP2018/006454 WO2018180058A1 (en) | 2017-03-29 | 2018-02-22 | Heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN110300878A true CN110300878A (en) | 2019-10-01 |
Family
ID=63677579
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201880011969.5A Pending CN110300878A (en) | 2017-03-29 | 2018-02-22 | Heat exchanger |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP2018169073A (en) |
| CN (1) | CN110300878A (en) |
| DE (1) | DE112018001666T5 (en) |
| WO (1) | WO2018180058A1 (en) |
Families Citing this family (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102017219433B4 (en) * | 2017-10-30 | 2022-08-11 | Hanon Systems | Heat exchanger for an internal combustion engine |
| JP7552027B2 (en) | 2019-03-19 | 2024-09-18 | 富士電機株式会社 | Heat exchanger |
| KR102137254B1 (en) * | 2020-01-23 | 2020-07-23 | 국방과학연구소 | Heat exchanger for heat radiating of antenna |
| EP4023996A1 (en) * | 2020-12-29 | 2022-07-06 | Valeo Autosystemy SP. Z.O.O. | Heat exchanger |
| EP4023988A1 (en) * | 2020-12-29 | 2022-07-06 | Valeo Autosystemy SP. Z.O.O. | Heat exchanger |
| EP4023993A1 (en) * | 2020-12-29 | 2022-07-06 | Valeo Autosystemy SP. Z.O.O. | A heat exchanger |
| DE112021007339T5 (en) | 2021-07-21 | 2024-01-11 | Hitachi Astemo, Ltd. | HEAT EXCHANGER, POWER CONVERSION DEVICE WITH HEAT EXCHANGER AND PRODUCTION METHOD FOR INNER RIB FOR HEAT EXCHANGER |
| CN114229253B (en) * | 2021-12-27 | 2023-04-07 | 北京阿玛西换热设备制造有限公司 | Constant temperature base for waste heat recovery |
| EP4212812B1 (en) * | 2022-01-14 | 2024-10-30 | Valeo Autosystemy SP. Z.O.O. | Heat exchanger for air cooling |
| EP4212815A1 (en) * | 2022-01-14 | 2023-07-19 | Valeo Autosystemy SP. Z.O.O. | Heat exchanger for air cooling |
| KR102647807B1 (en) * | 2022-07-11 | 2024-03-14 | 성균관대학교산학협력단 | Thermoelectric generator and manufacturing method for the same |
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- 2018-02-22 DE DE112018001666.8T patent/DE112018001666T5/en not_active Withdrawn
- 2018-02-22 CN CN201880011969.5A patent/CN110300878A/en active Pending
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| CN101400960A (en) * | 2006-03-10 | 2009-04-01 | 贝洱两合公司 | Heat exchanger for a motor vehicle |
| CN101441041A (en) * | 2007-11-22 | 2009-05-27 | 株式会社电装 | Heat exchanger |
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Also Published As
| Publication number | Publication date |
|---|---|
| WO2018180058A1 (en) | 2018-10-04 |
| DE112018001666T5 (en) | 2020-01-30 |
| JP2018169073A (en) | 2018-11-01 |
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Application publication date: 20191001 |