CN100395444C - Intercooler - Google Patents
Intercooler Download PDFInfo
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- CN100395444C CN100395444C CNB2005100926241A CN200510092624A CN100395444C CN 100395444 C CN100395444 C CN 100395444C CN B2005100926241 A CNB2005100926241 A CN B2005100926241A CN 200510092624 A CN200510092624 A CN 200510092624A CN 100395444 C CN100395444 C CN 100395444C
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- radiating fin
- interstage cooler
- aforementioned
- pipeline
- swa
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- 238000002485 combustion reaction Methods 0.000 claims abstract description 13
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 claims description 45
- 239000010949 copper Substances 0.000 claims description 26
- 229910052802 copper Inorganic materials 0.000 claims description 26
- 239000000956 alloy Substances 0.000 claims description 19
- 229910045601 alloy Inorganic materials 0.000 claims description 19
- 230000003434 inspiratory effect Effects 0.000 claims description 15
- 239000012809 cooling fluid Substances 0.000 claims description 13
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 13
- 229910052782 aluminium Inorganic materials 0.000 description 13
- 239000004411 aluminium Substances 0.000 description 10
- 238000001816 cooling Methods 0.000 description 6
- 239000000463 material Substances 0.000 description 5
- 238000010586 diagram Methods 0.000 description 3
- VYZAMTAEIAYCRO-UHFFFAOYSA-N Chromium Chemical compound [Cr] VYZAMTAEIAYCRO-UHFFFAOYSA-N 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 229910052804 chromium Inorganic materials 0.000 description 1
- 239000011651 chromium Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
Images
Classifications
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- Y02T10/146—
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- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
An intercooler comprises: tubes 10 in which the suction air of an internal combustion engine flows; and inner fins 11 for dividing passages in the tubes into a plurality of minute passages 100, wherein the intercooler is characterized in that when a cross sectional area in one tube 10 is S, a total passage area of the minute passages 100 in one tube 10 is Swa and an equivalent circle diameter of one minute passage 100 is de (unit: mm), the most appropriate specification of the core of the intercooler is found when de/(S/Swa) is used as a parameter. For example, in the case of an intercooler in which the inner fins 11 are straight fins and the supercharging air pressure is not less than 200 kPa, when de/(S/Swa) is made to be 0.2 to 7.5, it is possible to provide an intercooler with high performance.
Description
Technical field
The present invention relates to the interstage cooler that the air (air-breathing) of burning usefulness that internal-combustion engine is sucked cools off.
Background technique
In the internal-combustion engine of the band pressurized machine that large truck is used, supercharging air pressure majority is set at about 180KPa at present.(in addition, the pressure of record all is gauge pressure in this manual).And the interstage cooler that uses under such condition is generally aluminum.(for example, opening flat 10-292996 communique) with reference to the spy
Yet, become strict in order to tackle large truck with internal-combustion engine exhaust restriction from now on, just studying the scheme that supercharging air pressure is increased, be accompanied by the resistance to pressure and the heat resistance that require interstage cooler therewith and significantly improve.
But, in the situation of the interstage cooler of aluminum and since aluminium become high temperature after intensity significantly descend, so need significantly improve thickness of slab.So, need the change material.
Summary of the invention
The objective of the invention is to be to provide a kind of and try to achieve as interstage cooler and can access high performance condition when supercharging air pressure is higher than present circumstances or the change material time, seek the interstage cooler of raising of the performance of interstage cooler thus.
In order to reach above-mentioned purpose, cooler in the present invention, it is configured in the downstream side to the inspiratory flow of the pressurized machine of the air-breathing pressurization of internal-combustion engine, be used to make air-breathing and cooling fluid to carry out heat exchange and cool off air-breathing, it possesses: the pipeline 10 that forms the stream of inspiratory flow in inside, the interior radiating fin 11 (inner fin) that promotes the heat exchange of air-breathing and cooling fluid with being configured in that streams with in the pipeline 10 in the pipeline 10 are divided into a plurality of threads road 100, at interior radiating fin 11 are straight radiating fin that its wall 110 of cutting apart thread road 100 extends straight along air-breathing flow direction, and supercharging air pressure is in the above interstage cooler of 200KPa, sectional area in 1 pipeline 10 is being made as S, the total flow path area on the thread road 100 of 1 pipeline 10 is made as Swa, round (quite round) diameter of the equivalent on 1 thread road 100 is made as de, and (unit: in the time of mm), revising diameter of equivalent circle de/ (S/Swa) is 0.2～7.5mm.
In addition, be made as Th at stacked direction height with pipeline 10, the thickness of slab of pipeline 10 is made as tt, when the thickness of slab of interior radiating fin 11 was made as ti, the diameter of equivalent circle de in this specification was by de=4 * (Th-2 * tt-ti) * (d/2-ti)/{ 2 * [(Th-2 * tt-ti)+(d/2-ti)] } definition.
Yet the result that present inventors study knows that the supercharging air tightness of the motor output Ps of actual car and interstage cooler outlet side is proportional.So present inventors study the optimum specifications of trying to achieve the diffusing pipe of radiator heat (core) of interstage cooler from the relation of the diameter of equivalent circle de on supercharging air tightness and thread road.But as can be known: the value of the diameter of equivalent circle de of supercharging air tightness maximum changes along with the thickness of slab of interstage cooler, the radiator heat of trying to achieve interstage cooler as parameter with the value of the diameter of equivalent circle de optimum specifications of pipe and improper of loosing.
So, the result that present inventors further study, when confirming de/ (S/Swa) as parameter, the influence of radiating fin in the value of the de/ (S/Swa) of supercharging air tightness maximum is difficult to be subjected to.So, can be as parameter in the hope of the loose optimum specifications of pipe of the radiator heat of interstage cooler with de/ (S/Swa).
And, according to the present invention, at interior radiating fin is when straight radiating fin, supercharging air pressure are interstage cooler more than the 200KPa, because will revise diameter of equivalent circle de/ (S/Swa) is made as 0.2～7.5mm, can obtain the supercharging air tightness is peaked high performance interstage cooler more than 90%.
And, according to the present invention, at interior radiating fin is when straight radiating fin, supercharging air pressure are interstage cooler more than the 200KPa, because will revise diameter of equivalent circle de/ (S/Swa) is made as 0.3～4.5mm, can obtain the supercharging air tightness is peaked more high performance interstage cooler more than 95%.
Further, according to the present invention, at interior radiating fin is when straight radiating fin, supercharging air pressure are interstage cooler more than the 200KPa, because will revise diameter of equivalent circle de/ (S/Swa) is made as 0.5～3.5mm, can obtain the interstage cooler that the supercharging air tightness is peaked very high performance more than 97%.
In the present invention, in the downstream side configuration of the inspiratory flow of the pressurized machine of the air-breathing pressurization of giving internal-combustion engine and make air-breathing and cooling fluid carries out heat exchange and cools off air-breathing interstage cooler, it possesses the pipeline 10 that forms the stream of inspiratory flow in inside, with be configured in the pipeline 10 the interior radiating fin 11 that the streams in the pipeline 10 is divided into a plurality of threads road 100 and promotes the heat exchange of air-breathing and cooling fluid, at interior radiating fin 11 are straight radiating fin that its wall 110 of cutting apart thread road 100 extends straight along air-breathing flow direction, and in the interstage cooler that pipeline 10 and interior radiating fin 11 are made of copper or Cuprum alloy, when the sectional area in 1 pipeline 10 is made as S, the total flow path area on the thread road 100 of 1 pipeline 10 is made as Swa, the diameter of equivalent circle on 1 thread road 100 is made as de, and (unit: in the time of mm), revising diameter of equivalent circle de/ (S/Swa) is 0.2～7.5mm.
Thus, in the time of the interior radiating fin interstage cooler that to be straight radiating fin, pipeline and interior radiating fin be made of copper or Cuprum alloy, because will revise diameter of equivalent circle de/ (S/Swa) is made as 0.2～7.5mm, can obtain the supercharging air tightness is peaked high performance interstage cooler more than 90%.
And, according to the present invention, in the time of the interior radiating fin interstage cooler that to be straight radiating fin, pipeline and interior radiating fin be made of copper or Cuprum alloy, because will revise diameter of equivalent circle de/ (S/Swa) is made as 0.3～4.5mm, can obtain the supercharging air tightness is peaked more high performance interstage cooler more than 95%.
Further, according to the present invention, in the time of the interior radiating fin interstage cooler that to be straight radiating fin, pipeline and interior radiating fin be made of copper or Cuprum alloy, because will revise diameter of equivalent circle de/ (S/Swa) is made as 0.5～3.5mm, can obtain the interstage cooler that the supercharging air tightness is peaked very high performance more than 97%.
In the present invention, in the downstream configuration of the inspiratory flow of the pressurized machine of the air-breathing pressurization of giving internal-combustion engine and make air-breathing and cooling fluid carries out heat exchange and cools off air-breathing interstage cooler, it possesses the pipeline 10 that forms the stream of inspiratory flow in inside, with be configured in the pipeline 10 the interior radiating fin 11 that the streams in the pipeline 10 is divided into a plurality of threads road 100 and promotes the heat exchange of air-breathing and cooling fluid, at interior radiating fin 11 are its wall 110 of cutting apart thread road 100 is staggered configuration along air-breathing flow direction biasing radiating fin, and supercharging air pressure is in the above interstage cooler of 200KPa, sectional area in 1 pipeline 10 is being made as S, the total flow path area on the thread road 100 of 1 pipeline 10 is made as Swa, the diameter of equivalent circle on 1 thread road 100 is made as de, and (unit: in the time of mm), revising diameter of equivalent circle de/ (S/Swa) is 0.4～9.5mm.
Thus, when interior radiating fin for biasing radiating fin, supercharging air pressure is interstage cooler more than the 200KPa, because will revise diameter of equivalent circle de/ (S/Swa) is made as 0.4～9.5mm, can obtain the supercharging air tightness is peaked high performance interstage cooler more than 90%.
And, according to the present invention, when interior radiating fin for biasing radiating fin, supercharging air pressure is interstage cooler more than the 200KPa, because will revise diameter of equivalent circle de/ (S/Swa) is made as 0.6～7.2mm, can obtain the supercharging air tightness is peaked more high performance interstage cooler more than 95%.
Further, according to the present invention, when interior radiating fin for biasing radiating fin, supercharging air pressure is interstage cooler more than the 200KPa, because will revise diameter of equivalent circle de/ (S/Swa) is made as 0.8～6.2mm, can obtain the interstage cooler that the supercharging air tightness is peaked very high performance more than 97%.
In the present invention, in the downstream side configuration of the inspiratory flow of the pressurized machine of the air-breathing pressurization of giving internal-combustion engine and make air-breathing and cooling fluid carries out heat exchange and cools off air-breathing interstage cooler, it possesses the pipeline 10 that forms the stream of inspiratory flow in inside, with be configured in the pipeline 10 the interior radiating fin 11 that the streams in the pipeline 10 is divided into a plurality of threads road 100 and promotes the heat exchange of air-breathing and cooling fluid, at interior radiating fin 11 are its wall 110 of cutting apart thread road 100 is staggered configuration along air-breathing flow direction biasing radiating fin, and in the interstage cooler that pipeline 10 and interior radiating fin 11 are made of copper or Cuprum alloy, when the sectional area in 1 pipeline 10 is made as S, the total flow path area on the thread road 100 of 1 pipeline 10 is made as Swa, the diameter of equivalent circle on 1 thread road 100 is made as de, and (unit: in the time of mm), revising diameter of equivalent circle de/ (S/Swa) is 0.4～9.5mm.
Thus, in the time of the interstage cooler that constitutes by copper or Cuprum alloy for biasing radiating fin, pipeline and interior radiating fin when interior radiating fin, because will revise diameter of equivalent circle de/ (S/Swa) is made as 0.4～9.5, can obtain the supercharging air tightness is peaked high performance interstage cooler more than 90%.
And, according to the present invention, in the time of the interstage cooler that constitutes by copper or Cuprum alloy for biasing radiating fin, pipeline and interior radiating fin when interior radiating fin, because will revise diameter of equivalent circle de/ (S/Swa) is made as 0.6～7.2mm, can obtain the supercharging air tightness is peaked more high performance interstage cooler more than 95%.
Further, according to the present invention, in the time of the interstage cooler that constitutes by copper or Cuprum alloy for biasing radiating fin, pipeline and interior radiating fin when interior radiating fin, because will revise diameter of equivalent circle de/ (S/Swa) is made as 0.8～6.2mm, can obtain the interstage cooler that the supercharging air tightness is peaked very high performance more than 97%.
And, according to the present invention,, the thickness of slab of interior radiating fin 11 is lower than 0.15mm because being made as, when can guarantee the necessary strength of interior radiating fin, can in high performance scope, use.
In addition, the corresponding relation between the concrete mechanism that puts down in writing in the symbolic representation of above-mentioned each mechanism mode of execution described later.
The present invention, as described below, can fully be understood the explanation preferred embodiment of invention by the reference accompanying drawing.
Description of drawings
Fig. 1 is the plan view of the interstage cooler of the 1st mode of execution.
Fig. 2 is the enlarged view of the A portion of Fig. 1.
Fig. 3 is the sectional view along the B-B line of Fig. 2.
The loose figure of result of calculation of performance of pipe 1 of radiator heat when Fig. 4 is the straight radiating fin of use of expression the 1st mode of execution.
The loose figure of result of calculation of performance of pipe 1 of radiator heat when Fig. 5 is the use biasing radiating fin of expression the 1st mode of execution.
Fig. 6 is the plotted curve of relation of stress (S) number of occurrence anti-with it of expression the 2nd mode of execution.
Fig. 7 be expression the 2nd mode of execution interior radiating fin 11 thickness of slab ti and add the performance plot of the relation between the stress of the sticking part of radiating fin 11 within it.
Fig. 8 is the figure of the result of calculation of the performance of the interstage cooler during the thickness of slab ti of radiating fin 11 in the change of expression the 2nd mode of execution.
Embodiment
(the 1st mode of execution)
Below, the 1st mode of execution of the present invention is illustrated.Fig. 1 is the plan view of the interstage cooler of the 1st mode of execution, and Fig. 2 is the enlarged view of the A portion of Fig. 1, and Fig. 3 is the sectional view along the B-B line of Fig. 2.
The interstage cooler of present embodiment is configured in downstream one side of the inspiratory flow of the pressurized machine (not have diagram) to the air-breathing pressurization of internal-combustion engine (not diagram), and makes and air-breathingly carry out heat exchange and cool off air-breathing with cooling air.In addition, cooling air is suitable with cooling fluid of the present invention.
As Fig. 1～shown in Figure 3, the radiator heat of the interstage cooler pipe 1 that looses possesses: stacked a plurality of configurations and form in inside the stream of inspiratory flow flat pipeline 10, be configured in interior radiating fin 11 in the pipeline 10, be configured in the outer radiating fin 12 (out fin) between the stacked pipeline 10.
Constitute the parts of the diffusing pipe 1 of radiator heat, promptly pipeline 10, interior radiating fin 11 and outer radiating fin 12 all are to be made of copper or Cuprum alloy.More specifically, the parts that constitute the diffusing pipe 1 of radiator heat preferably use the high material of hot strength, and the Cuprum alloy that for example adds chromium is fit to.
Outer radiating fin 12 is hummock and engages with pipeline 10, and promotes in 10 mobile cooling airs of pipeline and mobile heat exchange between air-breathing pipeline 10 in.In addition, in the radiating fin 12, cause thermal boundary layer to be grown up for the mobile confusion that prevents air outside, the vent window (not diagram) that its part starts blind shaped is set.
Interior radiating fin 11 is hummock and engages with pipeline 10, and promote cooling air and air-breathing between heat exchange.In addition, interior radiating fin 11 has a plurality of walls 110 of the subtend face of connecting tube 10, by this wall 110 stream in the pipeline 10 is divided into a plurality of threads road 100.In addition, in interior radiating fin 11, vent window is not set.
Length direction both end sides at pipeline 10 is provided with the connection pipe hydroecium 2,3 that extends and be communicated with each pipeline 10 along the stacked direction of pipeline 10.The entrance part 20 of one side's connection pipe hydroecium 2 is connected on the pressurized machine, and will supply with from air-breathing the distribution to each pipeline 10 that the pressurized machine pressurized delivered is come.The export department 30 of the opposing party's connection pipe hydroecium 3 is connected on the intakeport (port) of internal-combustion engine, will be reclaimed and be sent to the intakeport of internal-combustion engine by the air-breathing set that pipeline 10 flows out. Connection pipe hydroecium 2,3 constitutes by copper or Cuprum alloy.
According to present embodiment,, when can improve hot strength,, thickness of slab can be done thin because copper has about 2 times intensity of aluminium owing to use copper or Cuprum alloy with material as interstage cooler.
So, for the interstage cooler of the present embodiment of above-mentioned formation, the thickness of slab ti by calculating radiating fin 11 in the change (with reference to Fig. 3, unit: the radiator heat in the time of mm) loose pipe 1 performance and try to achieve, carry out the loose research of optimum specifications of pipe 1 of radiator heat.
This research is to carry out under following condition.At first, the specification of interstage cooler is as follows.Interior radiating fin 11 is straight radiating fin that its wall 110 extends straight along the air-breathing flow direction in pipeline 10.
The width of the diffusing pipe 1 of radiator heat is 596.9mm, highly is 886mm, and thickness is 56mm.In addition, the loose width of pipe 1 of radiator heat be the size of the paper left and right directions of Fig. 1, and the loose height of pipe 1 of radiator heat be the size of the paper above-below direction of Fig. 1, and radiator heat is diffusing manages the size that 1 thickness is the direction vertical with the paper of Fig. 1.
The height Th (with reference to Fig. 3) of pipeline 10 is 5.9mm, and thickness is 56mm, and thickness of slab tt (with reference to Fig. 3) is 0.3mm.In addition, duct height Th is the size of the paper above-below direction of Fig. 1, and the thickness of pipeline 10 is the size of the direction vertical with the paper of Fig. 1.The inter fin space of outer radiating fin 12 is 4.0mm, and thickness of slab is 0.05mm.
And the condition of the Performance Calculation of the diffusing pipe 1 of radiator heat is as follows.Temperature at the cooling air in the moment that flows into interstage cooler is 30 ℃, the wind speed of cooling air is 8m/s, temperature at the supercharging gas (air-breathing) that joins the entrance part 20 of managing hydroecium 2 is 180 ℃, pressure at the supercharging gas that joins the entrance part 20 of managing hydroecium 2 is 200KPa, and the mass flow rate of supercharging gas is 2000Kg/hr.
Fig. 4 represents the Performance Calculation result of the diffusing pipe 1 of radiator heat, and the longitudinal axis is the density p by the supercharging gas behind the interstage cooler, and transverse axis is studied the correction diameter of equivalent circle of employing for present inventors.In addition, the sectional area of the face vertical with respect to the inspiratory flow direction in 1 pipeline 10 is made as S, the total flow path area on the thread road 100 of 1 pipeline 10 is made as Swa, and the diameter of equivalent circle on 1 thread road 100 is made as de, and (unit: in the time of mm), the correction diameter of equivalent circle is de/ (S/Swa).
As shown in Figure 4, when the correction diameter of equivalent circle is made as parameter, supercharging air tightness ρ is the influence of the thickness of slab ti of radiating fin 11 in the value of peaked correction diameter of equivalent circle is difficult to be subjected to, so, can try to achieve the optimum specifications of the diffusing pipe 1 of radiator heat as parameter with revising diameter of equivalent circle.
Particularly, interior radiating fin 11 is straight radiating fin, when supercharging air pressure is the above interstage cooler of 200KPa, perhaps interior radiating fin is straight radiating fin, in the time of interstage cooler that pipeline 10 and interior radiating fin 11 are made of copper or Cuprum alloy, because will revise diameter of equivalent circle is made as 0.2～7.5, supercharging air tightness ρ becomes peaked more than 90%, because will revise diameter of equivalent circle is made as 0.3～4.5, supercharging air tightness ρ becomes peaked more than 95%, be made as 0.5～3.5 by revising diameter of equivalent circle, and that supercharging air tightness ρ becomes is peaked more than 97%.
Then, when using the biasing radiating fin, carry out the research of the optimum specifications of the diffusing pipe 1 of radiator heat as interior radiating fin 11.So-called biasing radiating fin, well-known, refer to wall 110 and be staggered configuration along the air-breathing flow direction in pipeline 10.In addition, other condition is identical with above-mentioned research example.
Fig. 5 represents its result of calculation, interior radiating fin 11 is the biasing radiating fin, when supercharging air pressure is the above interstage cooler of 200KPa, perhaps, interior radiating fin is the biasing radiating fin, in the time of interstage cooler that pipeline 10 and interior radiating fin 11 are made of copper or Cuprum alloy, because will revise diameter of equivalent circle is made as 0.4～9.5, supercharging air tightness ρ becomes peaked more than 90%, because will revise diameter of equivalent circle is made as 0.6～7.2, supercharging air tightness ρ becomes peaked more than 95%, is made as 0.8～6.2 owing to will revise diameter of equivalent circle, and supercharging air tightness ρ becomes peaked more than 97%.
(the 2nd mode of execution)
Then, the 2nd mode of execution of the present invention is illustrated according to Fig. 6～Fig. 8.For part prosign mark and the omission explanation same with above-mentioned the 1st mode of execution.
In the present embodiment,, use the biasing radiating fin as interior radiating fin 11, in the interstage cooler that pipeline 10 and interior radiating fin 11 are made of copper or Cuprum alloy, the internal result that studies of the thickness of slab ti of radiating fin 11 draws the scope of suitable thickness of slab ti.
Fig. 6 is the plotted curve of the relation of the expression stress (S) and the anti-number of occurrence (N) thereof, and the longitudinal axis is a stress amplitude, and transverse axis is the several repeatedly N till fracture.
At first, try to achieve the fatigue limit of copper and aluminium by Fig. 6.So-called fatigue limit can be thought the maximum value of the stress that do not rupture ad infinitum repeatedly even be.In addition, because fatigue limit does not exist in aluminium, in the present embodiment, with copper and aluminium together repeatedly 10
7There is not the maximum stress of fracture to be made as fatigue limit behind the number of times.
And, in Fig. 6,, calculate the result of the design stress of copper and aluminium respectively by the fatigue limit of before having tried to achieve, be 80MPa in the time of copper, in the time of aluminium 30MPa.
Yet, in inner radiator 11, produce maximum stress at sticking part with the inwall of pipeline 10.So from stress that is added in this sticking part and the design stress that had before drawn, when trying to achieve for copper and aluminium separately in the limit of thickness of slab of radiating fin 11.
The thickness of slab ti of the interior radiating fin 11 when pressing the 200KPa load in Fig. 7 represents and add the performance plot of the relation of the stress of the sticking part of radiating fin 11 within it, the longitudinal axis is the stress of radiating fin 11 and sticking parts pipeline 10 inwalls in being added in, and transverse axis is the thickness of slab ti of interior radiating fin 11.
As shown in Figure 7, the design stress in the time of owing to copper is 80MPa, and the limit thickness of slab of interior radiating fin 11 is 0.02mm.Relative therewith, because the design stress for the aluminium time is 30MPa, the limit thickness of slab of interior radiating fin 11 is 0.15mm.
For this reason, the performance of the interstage cooler when calculating the thickness of slab ti of radiating fin 11 in the change draws.Fig. 8 represents the originally result of calculation of the performance of the interstage cooler of the 2nd mode of execution, and the longitudinal axis is the density p by the supercharging gas behind the interstage cooler, and transverse axis is the thickness of slab ti of interior radiating fin 11.
As shown in Figure 8, when the thickness of slab ti of interior radiating fin 11 is lower than 0.15mm, exist interstage cooler to become high performance scope.And the performance of interstage cooler does thin can obtain high performance interstage cooler by the thickness of slab ti with interior radiating fin 11.
But interior radiating fin 11 is when being made of aluminium, because the thickness of slab limit is that 0.15mm does not have practicability.So interior radiating fin 11 is made of copper, and, be made as by thickness of slab ti and be lower than 0.15mm interior radiating fin 11, when can guarantee the necessary strength of interstage cooler, can use becoming high performance scope.
(other mode of execution)
In the above-described first embodiment, the parts that constitute the diffusing pipe 1 of radiator heat adopt copper or Cuprum alloy system, but the parts that constitute the diffusing pipe 1 of radiator heat adopt the interstage cooler of the material beyond copper or the Cuprum alloy, even for example adopt the interstage cooler of aluminum, the present invention can be suitable for.
The present invention when selected specific mode of execution is illustrated for explanation, does not break away from the basis of basic conception of the present invention and scope as can be known, and those skilled in the art can carry out a plurality of distortion in addition.
Claims (16)
1. interstage cooler, the downstream side that it is configured in to the inspiratory flow of the pressurized machine of the air-breathing pressurization of internal-combustion engine is used to make air-breathing and cooling fluid carries out heat exchange and cools off air-breathingly, it is characterized in that:
Possess: form for the pipeline of the stream of inspiratory flow in inside and be configured in that being used in the aforementioned pipeline is divided into a plurality of threads road with the stream in the aforementioned pipeline and the interior radiating fin that promotes the heat exchange of air-breathing and cooling fluid;
Radiating fin straight radiating fin that to be the wall that is used for cutting apart aforementioned thread road extend straight along air-breathing flow direction and supercharging air pressure are the interstage cooler more than the 200KPa in aforementioned,
When the sectional area in 1 aforementioned pipeline is made as S, with the total flow path area on the aforementioned thread road of 1 aforementioned pipeline be made as Swa, when the diameter of equivalent circle on 1 aforementioned thread road is made as de, revising diameter of equivalent circle de/ (S/Swa) is 0.2～7.5mm, and wherein de unit is mm.
2. interstage cooler as claimed in claim 1 is characterized in that: revising diameter of equivalent circle de/ (S/Swa) is 0.3～4.5mm.
3. interstage cooler as claimed in claim 1 is characterized in that: revising diameter of equivalent circle de/ (S/Swa) is 0.5～3.5mm.
4. interstage cooler as claimed in claim 1 is characterized in that, the thickness of slab of aforementioned interior radiating fin is below the 0.15mm.
5. interstage cooler as claimed in claim 1 is characterized in that:
Aforementioned pipeline and aforementioned interior radiating fin are made of copper or Cuprum alloy.
6. interstage cooler as claimed in claim 5 is characterized in that, revising diameter of equivalent circle de/ (S/Swa) is 0.3～4.5mm.
7. interstage cooler as claimed in claim 5 is characterized in that, revising diameter of equivalent circle de/ (S/Swa) is 0.5～3.5mm.
8. interstage cooler as claimed in claim 5 is characterized in that, the thickness of slab of aforementioned interior radiating fin is below the 0.15mm.
9. interstage cooler, the downstream side that it is configured in to the inspiratory flow of the pressurized machine of the air-breathing pressurization of internal-combustion engine is used to make air-breathing and cooling fluid carries out heat exchange and cools off air-breathingly, it is characterized in that:
Possess: form for the pipeline of the stream of inspiratory flow in inside and be configured in that being used in the aforementioned pipeline is divided into a plurality of threads road with the stream in the aforementioned pipeline and the interior radiating fin that promotes the heat exchange of air-breathing and cooling fluid;
To be the wall that is used for cutting apart aforementioned thread road be the biasing radiating fin of staggered configuration and supercharging air pressure along air-breathing flow direction to radiating fin is interstage cooler more than the 200KPa in aforementioned,
When the sectional area in 1 above-mentioned pipeline is made as S, with the total flow path area on the aforementioned thread road of 1 aforementioned pipeline be made as Swa, when the diameter of equivalent circle on 1 aforementioned thread road is made as de, revising diameter of equivalent circle de/ (S/Swa) is 0.4～9.5mm, and wherein de unit is mm.
10. interstage cooler as claimed in claim 9 is characterized in that, revising diameter of equivalent circle de/ (S/Swa) is 0.6～7.2mm.
11. interstage cooler as claimed in claim 9 is characterized in that, revising diameter of equivalent circle de/ (S/Swa) is 0.8～6.2mm.
12. interstage cooler as claimed in claim 9 is characterized in that, the thickness of slab of aforementioned interior radiating fin is below the 0.15mm.
13. interstage cooler as claimed in claim 9 is characterized in that:
Aforementioned pipeline and aforementioned interior radiating fin are made of copper or Cuprum alloy.
14. interstage cooler as claimed in claim 13 is characterized in that, revising diameter of equivalent circle de/ (S/Swa) is 0.6～7.2mm.
15. interstage cooler as claimed in claim 13 is characterized in that, revising diameter of equivalent circle de/ (S/Swa) is 0.8～6.2mm.
16. interstage cooler as claimed in claim 13 is characterized in that, the thickness of slab of aforementioned interior radiating fin is lower than 0.15mm.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004246827 | 2004-08-26 | ||
| JP2004246827 | 2004-08-26 | ||
| JP2005219021 | 2005-07-28 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1740545A CN1740545A (en) | 2006-03-01 |
| CN100395444C true CN100395444C (en) | 2008-06-18 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005100926241A Expired - Fee Related CN100395444C (en) | 2004-08-26 | 2005-08-19 | Intercooler |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN100395444C (en) |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4702079A (en) * | 1984-10-11 | 1987-10-27 | Toyota Kidosha Kabushiki Kaisha | Air-cooled type intercooler for a supercharged internal combustion engine |
| US5894649A (en) * | 1997-08-28 | 1999-04-20 | Transpro, Inc. | Heat exchanger assembly utilizing grommets and integral cast tanks |
| US6189607B1 (en) * | 1998-07-31 | 2001-02-20 | Kazuki Hosoya | Heat exchanger |
| US6394176B1 (en) * | 1998-11-20 | 2002-05-28 | Valeo Thermique Moteur | Combined heat exchanger, particularly for a motor vehicle |
| JP2003021432A (en) * | 2001-07-09 | 2003-01-24 | Zexel Valeo Climate Control Corp | Condenser |
-
2005
- 2005-08-19 CN CNB2005100926241A patent/CN100395444C/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4702079A (en) * | 1984-10-11 | 1987-10-27 | Toyota Kidosha Kabushiki Kaisha | Air-cooled type intercooler for a supercharged internal combustion engine |
| US5894649A (en) * | 1997-08-28 | 1999-04-20 | Transpro, Inc. | Heat exchanger assembly utilizing grommets and integral cast tanks |
| US6189607B1 (en) * | 1998-07-31 | 2001-02-20 | Kazuki Hosoya | Heat exchanger |
| US6394176B1 (en) * | 1998-11-20 | 2002-05-28 | Valeo Thermique Moteur | Combined heat exchanger, particularly for a motor vehicle |
| JP2003021432A (en) * | 2001-07-09 | 2003-01-24 | Zexel Valeo Climate Control Corp | Condenser |
Non-Patent Citations (2)
| Title |
|---|
| 板翅式换热器. 王松汉等，第34页表1-11和表1-3、图1-3和图1-12，化学工业出版社. 1984 |
| 板翅式换热器. 王松汉等，第34页表1-11和表1-3、图1-3和图1-12，化学工业出版社. 1984 * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1740545A (en) | 2006-03-01 |
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Granted publication date: 20080618 Termination date: 20120819 |