CN101078598A - Multi-tube pass type heat exchanger - Google Patents
Multi-tube pass type heat exchanger Download PDFInfo
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- CN101078598A CN101078598A CN 200610081473 CN200610081473A CN101078598A CN 101078598 A CN101078598 A CN 101078598A CN 200610081473 CN200610081473 CN 200610081473 CN 200610081473 A CN200610081473 A CN 200610081473A CN 101078598 A CN101078598 A CN 101078598A
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Abstract
The invention relates to a heat exchanger with multiple tube side, especially applied in exhaust gas recirculation cooling device in automobile engine system. The invention comprises shell and heat exchanging pipe. Pipe plates are set at two ends of said shell. Pipe ports of said heat exchanging pipe are welt on the pipe plate and are fixed in the shell in parallel. Double tube side is constituted by said heat exchanging pipe groups and is divided into a first tube side and a second tube side. The quality of heat exchanging pipes in the first tube side is more than the one in the second tube side. The height of sections of said heat exchanging pipe is different from the width and it is flat shape. Grooves are set on said heat exchanging pipe on the outer surface. Said grooves are convex on the inner surface of heat exchanging pipe and the shape is corresponding to the groove. The invention can improve heat exchanging efficiency by 25-40%, decrease emission of NOx in automobile engine, and shorten length and cubage of heat exchanger. The invention is provided with simple and compact structure, low scaling and low manufacture and maintenance cost.
Description
Technical field
The present invention relates to a kind of heat exchanger, be particularly related to a kind of heat exchanger of multitube journey, this heat exchanger is applicable in the gas recirculation system of automobile engine, in order to reduce the cooler of oxynitrides (NOx) discharge capacity, be equally applicable to middle device for cooling, to improve the performance of engine as turbo charge system.
Background technology
The application of heat exchanger spreads all over each industrial department such as power, metallurgy, chemical industry, oil refining, building, machine-building, food, medicine and Aero-Space.Therefore the optimal design of heat exchanger is particularly important for industry-by-industry.Along with countries in the world to the more and more stricter requirement of discharge standard, the heat exchanger in the automobile exhaust gas recirculated cooling system is most important.
Waste gas recirculation cooling technology is in well-known vehicle engine exhaust gas recirculation system, the part waste gas that automobile engine is discharged carries out cool cycles by heat exchanger and utilizes, again pass back in the combustion chamber of engine through waste gas cooled, having introduced not active gases like this, mainly is carbon dioxide (CO
2) to the combustion chamber, both can reduce the nitrogen (N in the combustion chamber
2) content, can reduce the temperature of combustion chamber again, lower temperature and less nitrogen (N in the combustion chamber
2), can make full combustion of fuel can make nitrogen (N again
2) and oxygen (O
2) reaction condition lack, thereby reach generation and the discharging that suppresses oxynitrides (NOx).Therefore in gas recirculation system, having efficiently, waste gas recirculation heat-exchanger can make the discharge capacity of automobile reach higher standard.
At present, the heat exchanger used of vehicle engine exhaust gas recirculation system has two big classes.
The first kind is a plate-fin heat exchanger, is by the secondary surface composition between a lot of piece thin plates and plate, and two subsurfaces are both as the rib face, can play the tube sheet spacing again and strengthen the effect of rigidity, this type of heat converter structure complexity, manufacturing cost height.
Second class is a shell-and-tube exchanger, and shell-and-tube exchanger is that many parallel pipes (claiming these parallel pipes to be tube bank) are set in a cylindrical shell, and cold and hot two kinds of fluids flow through the exchange of carrying out heat from managing interior space (pipe side) and managing the external space (shell-side) respectively; Usually can the shell-side device longitudinal baffle parallel with tube bank or with restrain vertical deflection plate; To improve flow rate of fluid and to strengthen disturbance, improve heat exchange efficiency; This type of heat converter structure is simple, but heat exchange efficiency is lower.Because the automobile engine surrounding space is limited, under the precursor that does not reduce heat exchange efficiency,, need find the heat exchanger of a kind of heat exchange efficiency height and compact conformation for reducing unnecessary setting effectively.
Summary of the invention
The objective of the invention is be to improve the heat exchange efficiency of heat exchanger and the heat exchanger technical scheme of a kind of multitube journey that compact conformation proposes, this heat exchanger is particularly useful for the exhaust gas recirculation cooling device in the automobile engine system or the middle device for cooling of engine turbine pressure charging system.
Technical scheme of the present invention is achieved in that this heat exchanger includes housing, heat exchanger tube; Described housing two ends are respectively equipped with tube sheet, and the described heat exchanger tube mouth of pipe is welded on the tube sheet respectively and is parallel to each other and is fixed in the housing; It is characterized in that, form two-tube-pass by described heat exchanger tube, press the sequencing that heat transferring medium flows in heat exchanger tube, be divided into first tube side and second tube side, the described first tube side heat transferring medium outlet and the second tube side heat transferring medium import, form " U " shape loop by the end socket that is fixed on the housing, the heat exchanger tube quantity of described first tube side is more than the second tube side heat exchanger tube quantity; Described heat exchanger tube depth of section and width are unequal, and it is flat-shaped that shape is; Described heat exchanger tube is provided with groove along outer surface, and described groove is projection at the heat exchanger tube inner surface, and its shape is corresponding with groove shapes.
Described heat exchanger tube cross section is oval, and the ratio of long axis of ellipse and minor axis was less than 4: 1.
Described heat exchanger tube cross section is flat, and two relative long limits are set to be the arc of projection from inside to outside, two relative minor faces for curved projection from inside to outside and with grow the limit and be connected for the circular arc transition.
Described heat exchanger tube cross sectional shape is made of two relative minor faces long limit relative with two, and wherein, described minor face is the camber line that protrudes from inside to outside, and described long limit is a straight line.
Described heat exchanger tube cross sectional shape is a rectangle, and connects for arc-shaped transition between the adjacent both sides.
Described heat exchanger tube is the stainless steel body.
Described groove is interrupted or continuously spiral setting along described heat exchange pipe external surface.
Described heat exchanger tube depth of groove is not less than 0.4mm.
Described groove is one or more its cross sectional shape to be set for " U " shape or " V " shape.
Described end socket is shaped as arc-shaped curved surface.
Be provided with deflection plate in the described heat exchanger shell.
The housing of heat exchanger can carry out the surface structure design of various ways according to the engine interior space.Heat exchanger tube then is arranged in the housing of heat exchanger with rational arrangement mode according to the different face shaping of housing.
The present invention is compared with the prior art advantage:
1. under equal conditions, promptly under the prerequisite that the volume of cooler and heat exchange medium flow are constant, use the present invention can improve 25～40% heat exchange efficiency.
2. in vehicle engine exhaust gas recirculation system, use the present invention, under equal conditions can reduce the discharge capacity of automobile engine oxynitrides (NOx), improve the discharge performance index of automobile engine.
3. compare with plate-fin heat exchanger, the present invention is simple in structure, has reduced manufacturing cost.
4. because the present invention has used multichannel tube side structure in heat exchanger, under equal conditions shortened heat exchanger length and volume, made engine structure compact more.
Since the present invention when the spiral salient shape structure that the heat exchanger tube inwall is provided with has strengthened heat exchange, strong turbulent motion makes dirt suffer fierce erosion in pipe, and is less scaling, is beneficial to cleaning, reduced the heat exchanger maintenance cost.
6, the present invention improves performance as starting point to save cost, for organically integrating, engine exhaust recirculation refrigeration system and dynamical system provide technology platform, saved between engine air greatly and volume, reduced unnecessary setting effectively, when improving engine performance, greatly save manufacturing cost for the producer.
Below by drawings and Examples, technical scheme of the present invention is elaborated.
Description of drawings
Fig. 1 is a structural representation of the present invention;
Fig. 2 is end plate front schematic view of the present invention;
Fig. 3 is the heat exchanger tube schematic diagram that has helical groove;
Fig. 4 is first kind of heat exchanger tube cross sectional shape schematic diagram;
Fig. 5 is second kind of heat exchanger tube cross sectional shape schematic diagram;
Fig. 6 is the third heat exchanger tube cross sectional shape schematic diagram;
Fig. 7 is the 4th a kind of heat exchanger tube cross sectional shape schematic diagram;
Fig. 8 has the structural representation of deflection plate for the present invention.
The specific embodiment
Referring to Fig. 1 and Fig. 2, be the embodiment that heat exchanger tube is divided into the two-way tube side, wherein, be provided with fixed tube sheet 3 at the two ends of housing 1, have the fixed via of heat exchanger tube 2 on the tube sheet 3, the nose end portion of heat exchanger tube 2 is welded on respectively on the tube sheet 3 in the corresponding with it hole, and is parallel to each other and is fixed in the housing 1.
The direction of arrow among Fig. 1 is the flow direction of heat exchange medium, and the quantity of first tube side, 4 heat exchanger tubes 2 is greater than the quantity of second tube side, 5 heat exchanger tubes 2.
On housing 1, be provided with cooling medium inlet 7, be provided with cooling medium outlet 12 near the exhaust gas inlet end place of the second road tube side 5 at the opposite face of housing 1 upper inlet 7 near the exhaust gas inlet end place of first via tube side 4.
Suppose that fluid density ρ is a definite value, the volume flow Q of fluid
VBe constant, roughly the same in order to guarantee average flow velocity v and the drag losses situation of fluid in different tube sides, according to hydrodynamics formula Q
V=Av=con tan t as can be known, the circulation area A of different tube sides is identical, the number of just different tube side heat exchanger tubes is roughly the same.
In embodiment 1, the waste gas that engine comes out flows through the heat exchanger tube 2 of first tube side 4 earlier, then flows through the heat exchanger tube 2 of second tube side 5, and fluid is in the loop of " U " shape of mobile being of tube side.Waste gas is behind subcooler, and the temperature before and after the cooling can differ several Baidu, and the density p of gas has a certain distance when high temperature and low temperature, therefore the variable density of gas is considered that in the design of heat exchanger, then fluid is at the mass flow Q of different tube sides
MUnder the prerequisite that remains unchanged, the temperature height when the temperature ratio of waste gas by first tube side 4 time passes through second tube side 5, the density p of waste gas when first tube side so
1Than the density p when second tube side 5
2Low, i.e. ρ
1≤ ρ
2, according to formula Q
M=ρ
1A
1v
1=ρ
2A
2v
2=con tan t as can be known, roughly the same in order to guarantee average flow velocity v and the drag losses situation of fluid in different tube sides, then the circulation area of first tube side 4 is greater than the circulation area of second tube side 5, i.e. A
1〉=A
2So the quantity of the heat exchanger tube 2 of first tube side 4 is more than the quantity of the heat exchanger tube 2 of second tube side 5.So promptly guaranteed under identical mass flow, the pipe quantity of first tube side 4 increases to some extent, resistance descends to some extent, the pipe number of second tube side 5 reduces to some extent, speed increases, and then heat exchange effect strengthens to some extent, finally makes heat exchanger reach higher heat exchange efficiency, also reduce simultaneously the quantity that heat exchanger tube uses, saved material.
Referring to Fig. 3, the heat exchanger tube 2 in embodiment 1 is the stainless steel body, and there is an inwardly protruded spiral rotation groove 21 on the surface; This helical groove 21 is one, also can be many; This helical groove 21 is provided with continuously along the surface of heat exchanger tube 2, also can be interrupted setting; The cross sectional shape of helical groove 21 is " U " shape, also can be set to " V " shape, is beneficial to the processing of small size shape face; The lead angle 24 of groove 21 is 25 degree, can be arranged between 20～75 degree; The degree of depth of groove 21 is 1mm, and its degree of depth setting should be not less than the ratio of warp in 0.4mm and heat exchanger tube external diameter and the set groove bottom land of heat exchanger tube less than 1.4.
The heat exchanger tube of band helical groove is set in heat exchanger, when fluid passes through this heat exchanger tube, run into the inhibition of pipe inside spin boss, flow direction changes, and produces complicated secondary stream vortex flow, has also formed vortex in the back of spiral salient simultaneously, increased the turbulivity of waste gas, especially increased disturbance to the near wall region boundary layer, destroy or attenuate the boundary layer of fluid, thereby strengthened heat exchange; Simultaneously, the enhancing of flow disturbance makes critical Reynolds number reduce, and promptly takes place ahead of time from the transformation of laminar flow to turbulent flow, and strong turbulent motion makes dirt suffer fierce erosion in pipe, and is less scaling, is beneficial to cleaning.
Referring to Fig. 4 to Fig. 8, the vertical cross-section of fixing heat exchanger tube 2 can have multiple shape in housing 1;
Arrange in the housing 1 that cross sectional shape is that flat-shaped band helical groove heat exchange tube is compared for circular band helical groove heat exchange tube with arranging cross sectional shape: at first, under the prerequisite that the heat exchanger tube area of section is constant and the heat exchange medium flow is constant, the perimeter of section of flat pipe is greater than the perimeter of section of pipe, so the heat exchange area of flat pipe is greater than the heat exchange area of pipe, and then improved the heat exchange area of whole heat exchanger, guaranteeing to make heat exchanger reach higher heat exchange effect under the constant prerequisite of heat exchanger volume; In addition, the heat exchanger tube of the flat-shaped band helical groove of being arranged in the waste gas recirculation heat-exchanger not only increases to some extent than the heat exchange area of pipe, and flat pipe contrast pipe, because flat pipe is not centrosymmetric shape with respect to pipe, the geometric center of flat-shaped band helical groove pipe is littler than the distance of round screw thread groove tube and tube wall with the distance of tube wall, most of fluid in the pipe can participate in heat exchange, and the shape of flat pipe makes the disturbance of fluid strengthen, the disturbance of fluid in pipe is more strong, also just strengthened the heat exchange effect, it is fast that thereby the temperature of tube fluid descends, and the temperature difference of import and export increases, and has improved heat exchange efficiency.
Referring to Fig. 1 and Fig. 4, the fixing heat exchanger tube of first kind of cross sectional shape showing for Fig. 4 of heat exchanger tube 2 in the housing 1, heat exchanger tube 2 cross sections are flat, two long relatively limits 23 are straight line, two relative minor faces 22 be from inside to outside curved projection and be connected for the circular arc transition with long limit 23, such setting makes full use of the surface of heat exchanger tube and realizes the heat exchange of maximal efficiency, and is easy to production and processing.
Embodiment 3
Referring to Fig. 1 and Fig. 5, the heat exchanger tube of second kind of cross sectional shape that fixing heat exchanger tube 2 shows for Fig. 5 in the housing 1, heat exchanger tube 2 cross sectional shapes are approximate rectangular, and circular arc transition connection is set between the adjacent both sides; Production and processing is convenient in such setting, also can improve the heat exchange efficiency of heat exchanger tube.
Embodiment 4
Referring to Fig. 1 and Fig. 6, the heat exchanger tube of the third cross sectional shape that fixing heat exchanger tube 2 shows for Fig. 6 in the housing 1, heat exchanger tube 2 cross sectional shapes are on the basis of first kind of cross sectional shape as shown in Figure 4, two relative long limits 23 of stainless steel tube are set to be the arc of projection from inside to outside, and the arc surface of curved projection from inside to outside all is arranged on four surfaces that are about to stainless steel tube; And the arc radius on long limit 23 is far longer than the radius of minor face 22, the phenomenon that the surface " subsides " can not occur on long limit 25 like this, is beneficial to processing and fabricating.
Referring to Fig. 1 and Fig. 7, fixing heat exchanger tube 2 be the heat exchanger tube of the 4th kind of cross sectional shape shown in Figure 7 in the housing 1, and heat exchanger tube 2 cross sectional shapes are an ellipse, and the ratio of long axis of ellipse and minor axis is 3: 1, and to be not more than 4: 1 be good; Cross sectional shape is oval-shaped heat exchanger tube, processes easily and has a good heat exchange effect.
Referring to Fig. 8, in housing 1, be provided with deflection plate 13; Suitably when housing 1 is longer deflection plate 13 is set plays the effect of supporting heat exchanger tube 2, can increase the disturbance of the outer cooling agent of pipe again, make the heat exchange effect of the interior outer fluid of pipe be enhanced.
It should be noted last that, below only unrestricted in order to technical scheme of the present invention to be described, although the present invention is had been described in detail with reference to the preferred arrangement scheme, those of ordinary skill in the art is to be understood that, can make amendment or be equal to replacement technical scheme of the present invention, and not break away from the spirit and scope of technical solution of the present invention.
Claims (11)
1. the heat exchanger of a multitube journey includes housing, heat exchanger tube; Described housing two ends are respectively equipped with tube sheet, and the described heat exchanger tube mouth of pipe is welded on the tube sheet respectively and is parallel to each other and is fixed in the housing; It is characterized in that, form two-tube-pass by described heat exchanger tube, press the sequencing that heat transferring medium flows in heat exchanger tube, be divided into first tube side and second tube side, the described first tube side heat transferring medium outlet and the second tube side heat transferring medium import, form " U " shape loop by the end socket that is fixed on the housing, the heat exchanger tube quantity of described first tube side is more than the second tube side heat exchanger tube quantity; Described heat exchanger tube depth of section and width are unequal, and it is flat-shaped that shape is; Described heat exchanger tube is provided with groove along outer surface, and described groove is projection at the heat exchanger tube inner surface, and its shape is corresponding with groove shapes.
2. the heat exchanger of a kind of multitube journey according to claim 1 is characterized in that, described heat exchanger tube cross section is oval, and the ratio of long axis of ellipse and minor axis was less than 4: 1.
3. the heat exchanger of a kind of multitube journey according to claim 1, it is characterized in that, described heat exchanger tube cross section is flat, and two relative long limits are set to be the arc of projection from inside to outside, two relative minor faces for curved projection from inside to outside and with grow the limit and be connected for the circular arc transition.
4. the heat exchanger of a kind of multitube journey according to claim 1 is characterized in that, described heat exchanger tube cross sectional shape is made of two relative minor faces long limit relative with two, and wherein, described minor face is the camber line that protrudes from inside to outside, and described long limit is a straight line.
5. the heat exchanger of a kind of multitube journey according to claim 1 is characterized in that, described heat exchanger tube cross sectional shape is a rectangle, and connects for arc-shaped transition between the adjacent both sides.
6. the heat exchanger of a kind of multitube journey according to claim 1 is characterized in that, described heat exchanger tube is the stainless steel body.
7. the heat exchanger of a kind of multitube journey according to claim 1 is characterized in that, described groove is interrupted or continuously spiral setting along described heat exchange pipe external surface.
8. the heat exchanger of a kind of multitube journey according to claim 1 is characterized in that, described heat exchanger tube depth of groove is not less than 0.4mm.
9. the heat exchanger of a kind of multitube journey according to claim 1 is characterized in that, described groove is one or more its cross sectional shape to be set for " U " shape or " V " shape.
10, the heat exchanger of a kind of multitube journey according to claim 1 is characterized in that, described end socket is shaped as arc-shaped curved surface.
11. the heat exchanger of a kind of multitube journey according to claim 1 is characterized in that, is provided with deflection plate in the described heat exchanger shell.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2006100814734A CN100460796C (en) | 2006-05-22 | 2006-05-22 | Multi-tube pass type heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2006100814734A CN100460796C (en) | 2006-05-22 | 2006-05-22 | Multi-tube pass type heat exchanger |
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| Publication Number | Publication Date |
|---|---|
| CN101078598A true CN101078598A (en) | 2007-11-28 |
| CN100460796C CN100460796C (en) | 2009-02-11 |
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ID=38906199
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2006100814734A Active CN100460796C (en) | 2006-05-22 | 2006-05-22 | Multi-tube pass type heat exchanger |
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102032817A (en) * | 2010-12-17 | 2011-04-27 | 张家港市华菱化工机械有限公司 | Novel heat exchange tube of heat exchanger |
| JP2012002495A (en) * | 2010-05-18 | 2012-01-05 | Yjs:Kk | Heat exchanger |
| CN102313478A (en) * | 2011-06-08 | 2012-01-11 | 上海科米钢管有限公司 | Heat exchange equipment utilizing flat type spiral heat exchange tubes |
| CN102331201A (en) * | 2011-07-11 | 2012-01-25 | 上海科米钢管有限公司 | Heat exchanger provided with elliptic flat spiral heat exchange tubes |
| CN105466256A (en) * | 2015-12-25 | 2016-04-06 | 无锡方盛换热器股份有限公司 | Twin type oil-water cooler |
| CN106323045A (en) * | 2016-08-23 | 2017-01-11 | 太仓圣广仁自动化设备有限公司 | Efficient heat exchanger |
| CN107606974A (en) * | 2017-09-14 | 2018-01-19 | 上海铠韧气体工程股份有限公司 | Integrated combination heat exchanger |
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| CN2076224U (en) * | 1990-11-01 | 1991-05-01 | 刘霖沛 | Shell-and-tube heat exchanger with turbulent helical |
| JPH0777397A (en) * | 1993-09-07 | 1995-03-20 | Kawaju Reinetsu Kogyo Kk | Heat transfer tube |
| CN2180961Y (en) * | 1993-12-14 | 1994-10-26 | 胡明辅 | Transverse rod heat-exchanger |
| CN2181667Y (en) * | 1993-12-24 | 1994-11-02 | 卢秉刚 | Spiral double circle-arc flat tube heat-exchanger |
| CN2335113Y (en) * | 1997-07-18 | 1999-08-25 | 孟继安 | Spiral twisted elliptic section heat-exchanging pipe |
| JP2001027157A (en) * | 1999-07-13 | 2001-01-30 | Mitsubishi Motors Corp | Strut for egr cooler |
| JP4536237B2 (en) * | 2000-09-29 | 2010-09-01 | 株式会社ティラド | Heat exchanger |
| DE10218521A1 (en) * | 2002-04-25 | 2003-11-06 | Behr Gmbh & Co | Exhaust gas heat exchanger, especially for motor vehicles |
| CN2682365Y (en) * | 2004-01-05 | 2005-03-02 | 齐世泽 | Pipe shell type stainless steel node pipe heat exchanger |
| CN100347419C (en) * | 2004-07-16 | 2007-11-07 | 北京美联桥科技发展有限公司 | Screw groove heat radiation tube for diesel engine waste gas recirculation cooler |
| CN2901226Y (en) * | 2006-05-22 | 2007-05-16 | 北京美联桥科技发展有限公司 | Heat exchanger of multitube distance |
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2012002495A (en) * | 2010-05-18 | 2012-01-05 | Yjs:Kk | Heat exchanger |
| CN102032817A (en) * | 2010-12-17 | 2011-04-27 | 张家港市华菱化工机械有限公司 | Novel heat exchange tube of heat exchanger |
| CN102313478A (en) * | 2011-06-08 | 2012-01-11 | 上海科米钢管有限公司 | Heat exchange equipment utilizing flat type spiral heat exchange tubes |
| CN102331201A (en) * | 2011-07-11 | 2012-01-25 | 上海科米钢管有限公司 | Heat exchanger provided with elliptic flat spiral heat exchange tubes |
| CN105466256A (en) * | 2015-12-25 | 2016-04-06 | 无锡方盛换热器股份有限公司 | Twin type oil-water cooler |
| CN106323045A (en) * | 2016-08-23 | 2017-01-11 | 太仓圣广仁自动化设备有限公司 | Efficient heat exchanger |
| CN107606974A (en) * | 2017-09-14 | 2018-01-19 | 上海铠韧气体工程股份有限公司 | Integrated combination heat exchanger |
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| CN100460796C (en) | 2009-02-11 |
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Address after: 100124 Chen Jialin, 9 hospital, eight Li Zhuang village, Gaobeidian Township, Chaoyang District, Beijing, 7 floor 705, 706 rooms, building 1, Co-patentee after: Jinzhou Meilianqiao Automobile Parts Co., Ltd. Patentee after: Beijing United Bridge Technology Group Co., Ltd. Address before: 100022 room 2503, block A, North office building, Jian Wai SOHO, 39 East Third Ring Road, Chaoyang District, Beijing. Co-patentee before: Jinzhou Meilianqiao Automobile Parts Co., Ltd. Patentee before: Meilianqioa Sci. & Tech. Development Co., Ltd., Beijing |
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