CN100447518C - Heat exchanger - Google Patents
Heat exchanger Download PDFInfo
- Publication number
- CN100447518C CN100447518C CNB2004800381366A CN200480038136A CN100447518C CN 100447518 C CN100447518 C CN 100447518C CN B2004800381366 A CNB2004800381366 A CN B2004800381366A CN 200480038136 A CN200480038136 A CN 200480038136A CN 100447518 C CN100447518 C CN 100447518C
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- Prior art keywords
- heat exchanger
- tubes
- exchanger according
- housing
- structural
- Prior art date
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- 239000002826 coolant Substances 0.000 claims description 19
- 239000000110 cooling liquid Substances 0.000 claims description 12
- 239000007789 gas Substances 0.000 description 13
- 230000008646 thermal stress Effects 0.000 description 6
- 238000009826 distribution Methods 0.000 description 5
- 239000012530 fluid Substances 0.000 description 5
- 239000007788 liquid Substances 0.000 description 5
- 238000003466 welding Methods 0.000 description 5
- 238000009835 boiling Methods 0.000 description 4
- 238000001816 cooling Methods 0.000 description 4
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 3
- 238000005219 brazing Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 238000002485 combustion reaction Methods 0.000 description 1
- 230000005284 excitation Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 230000006698 induction Effects 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000013021 overheating Methods 0.000 description 1
- 238000007665 sagging Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 238000005728 strengthening Methods 0.000 description 1
- 230000035882 stress Effects 0.000 description 1
Images
Classifications
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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
- F28F1/14—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 and extending longitudinally
-
- 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
- F28D7/163—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 with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
- F28D7/1653—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 with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing the conduit assemblies having a square or rectangular shape
-
- 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
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
-
- 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
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
- F28F9/0268—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box in the form of multiple deflectors for channeling the heat exchange medium
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D21/0001—Recuperative heat exchangers
- F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- 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
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)
- Exhaust-Gas Circulating Devices (AREA)
Abstract
The invention relates to a heat exchanger (1), especially for motor vehicles, comprising a housing (2) and at least one pipe (3) disposed inside said housing (2). The heat exchanger is characterized in that structures (4) are provided in the area between the pipes (3) and the housing (2) and/or between the pipes (3).
Description
Technical Field
The invention relates to a heat exchanger for a motor vehicle.
Background
Nowadays, there are increasing demands on engines with regard to reducing emissions and fuel consumption, and in order to meet these demands, many measures are taken, such as increasing the boost and more precisely influencing the combustion conditions. For automotive heat exchangers, this makes the operating conditions higher, for example, gas and coolant pressures increase, temperatures increase and flow rates increase. At the same time, the requirements for contrast power (Leistungsdichten) and service life are also increasing. Therefore, it is necessary to locally adopt a new cooling concept. Thus, in charge air coolers, the air/air cooler conventionally used is at least partly replaced by an air/liquid cooler in order to achieve the power and specific power required for high charging of the engine. In exhaust gas heat exchangers, the exhaust gas recirculation rate is also increasing under increasing operating conditions, such as pressure, temperature and specific power. Thus, in modern heat exchangers, the mechanical loads, in particular the pressures and vibrations, are increasing.
The temperature difference between the first medium to be cooled (usually in the gaseous state) and the second medium acting as cooling (usually in the liquid state here) is so great that the temperature rise of the components on the first medium side and on the second medium side differs. In the exhaust gas heat exchanger, this temperature difference can be up to 700K above, in the charge air cooler up to 300K. In this way, strong thermal stresses are generated due to the difference in linear expansion between the first medium side and the second medium side. In the case of rapid changes in the operating state, an uneven temperature distribution (temperature jump) can also increase this thermal stress.
As the specific power of the heat exchanger becomes greater, the risk of boiling of the cooling liquid also increases, which leads to a considerable reduction in power and service life.
Finally, the processes and materials used are subject to considerable restrictions due to the presence of strongly corrosive media, such as condensate water from the exhaust gas in the exhaust gas heat exchanger, which leads to greater problems with increasing demands for power. Therefore, there is a need for a long term solution that combines sufficient internal and external compressive strength of the flow channel, boiling avoidance, and sufficient resistance to vibrational excitation and thermal stresses.
Disclosure of Invention
It is an object of the present invention to provide an improved heat exchanger.
This object is achieved by a heat exchanger having the following features. Preferred embodiments are also provided below.
The invention relates to a heat exchanger having a housing and at least one tube arranged in the housing, wherein structural elements (Strukturen) are provided between the tube and the housing and/or between the tubes. The first medium flows through the tube. The second medium then flows in the interspaces between the tubes and/or between the tubes and the housing, in which interspaces also structural elements are arranged. The structural member has improved strength by strengthening in terms of internal and external pressure loads of the tube. Furthermore, the thermal stresses between the first medium side and the second medium side are homogenized over the entire length of the cooler by the connection between the tube and the housing, so that the stresses at the tube ends are significantly reduced. Additionally, the structural members may form fluid lines within the heat exchanger and distribute the fluid. Here, the fin plate may improve heat transfer, thereby enabling thermal stress to be reduced through the improvement of heat transfer. By enlarging the heat transfer area, the tubes can be better cooled, thus avoiding boiling. In this way, the specific power of the heat exchanger is significantly increased overall compared to conventional heat exchangers without structural elements. Structural plates (blechtrekturen) in the form of individual tubes, fin plates, plates with knobs (nopenbleche) are preferably inserted into the heat exchanger as structural elements. This heat exchanger may be an exhaust gas heat exchanger or a charge air cooler, but may also be another heat exchanger, for example another gas-liquid heat exchanger, in which the gas is passed through a pipe through a heat exchanger for cooling (radiator), or a liquid-gas heat exchanger, in which the cold gas is passed through a pipe through a heat exchanger for heating (heater), or a liquid-liquid heat exchanger. The tubes and/or the housing may also be correspondingly structured instead of structured plates, i.e. the surface of the tubes may be provided with fins or knobs (noppenartis). The height of the structural member is preferably 1mm to 5mm, preferably 1mm to 3mm, and most preferably 1.5 mm. The span (teilung) L of the structural elements is preferably 0.1 to 6 times, preferably 0.5 to 4 times the height h of the structural elements. The transverse span (Querteiiung) Q is preferably 0.15 to 8 times, preferably 0.5 to 5 times, the height h of the structural element. In the structured area, the ratio of the height of the flow channels between the tubes to the height of the flow channels in the tubes is preferably 0.1 to 1, preferably 0.2 to 0.7. The hydraulic diameter between the tubes in the structured zone is preferably 0.5mm to 10mm, preferably 1mm to 5 mm.
The component is preferably fixedly connected, in particular soldered, to the housing and/or the tube. Here, the fixed connection is not interrupted, or is interrupted in order to improve the distribution of the cooling liquid, in particular over a large part of the length of the heat exchanger. By means of this fixed connection, the external compressive strength (overpressure on the second medium side) will be increased very effectively, since the structural parts act as tie bars, preventing the pipe from sagging. In addition, the structural members absorb the vibrations that occur in the tubes that are rather unstable in conventional heat exchangers and very effectively homogenize the thermal stresses. In addition, this fixed connection facilitates heat transfer from the tube to the structural member, thereby improving cooling of the tube. In addition, the number of tubes is reduced due to the improvement of heat transfer, so that the manufacturing cost can be reduced.
At least part of the tube is preferably formed by a flat tube. The flat tubes are here, from a thermodynamic point of view, significantly better in conductivity than round tubes, but have a lower compressive strength, so that measures for increasing the compressive strength, such as the support structure according to the invention on the outside of the tubes, have to be taken for the flat tubes. In particular, the flat tubes have a substantially rectangular cross section and the corners are rounded. The rectangular tube may furthermore be one piece. They have a longitudinal weld seam and can be formed by welding, such as laser welding, friction welding, induction welding, etc., or brazing. The rectangular tube may also be formed by welded or brazed half-shells. The tube may also be of any other shape, for example oval, and/or with welded or brazed projections. Additionally, the tubes may be slightly convex in order to compensate for tolerances in the housing and tubes and the structural members located therebetween. Turbulators (small fins) may also be provided in and/or on the tubes. The surface (inner and/or outer) of the tube may also be provided with structural elements in order to generate vortices.
The structural element preferably has an inhomogeneous structure at least in sections, so that the coolant can be supplied in targeted manner to critical areas in order to avoid overheating or boiling. The amount of coolant supplied can also be increased by eliminating some of the structural elements. By this measure the pressure loss of the heat exchanger and the lateral distribution of the cooling liquid in the heat exchanger can be optimized. The areas with inhomogeneous structure are preferably located in the inlet and/or outlet area of the fluid. They serve for the guidance of the fluid and keep the pressure loss as low as possible.
By making at least a part of the structural member serrated, it is possible to improve the structural stability and optimize the flow path of the coolant.
In order to simplify the construction of the heat exchanger, the housing is preferably formed in two or more parts, in particular a U-shaped half-shell with a cover plate, wherein a water tank can be integrated in the cover plate. In principle, an integrated construction is also possible, for example the water tank can be formed on the housing.
The structural elements may also be arranged in the tubes themselves, so that all the above-described structures, which may be arranged between the tubes, may also be integrated into the tubes. Such structural members are preferably formed by fin plates or plates with knobs, which are connected to the tube by welding, brazing or snapping. The height of the structural member is preferably 1mm to 5mm, preferably 1mm to 3mm, and most preferably 1.5 mm. The span L of the structural members is preferably 0.5 to 6 times the height h of the structural members. The transverse span Q is preferably 0.5 to 8 times the structural member height h. In the structured zone, the hydraulic diameter in the tubes is preferably 0.5mm to 10mm, preferably 1mm to 5 mm.
Drawings
The present invention will be described in detail below with reference to examples and the accompanying drawings. Wherein,
figure 1 is a cross-sectional view of an exhaust gas heat exchanger,
figure 2 is a perspective view of the heat exchanger shown in figure 1,
figure 3 is a schematic perspective view of a fin plate,
figure 4 is a schematic perspective view of a modified fin plate,
fig. 5a-d are different variants of the inlet area.
Detailed Description
The exhaust gas heat exchanger 1 has a two-part housing 2 and a plurality of tubes 3 arranged in the housing 2. Fin plates 4 are arranged between the tubes 3 and between the housing 2 and the tubes 3 as structural elements, wherein the fin plates 4 have a saw-tooth like structure according to the above described embodiment, as shown in fig. 3 and will be explained in detail later. Here, the tubes 3 are flat tubes.
The exhaust gases (gaseous first medium) from the engine to be cooled flow in the pipe 3, whereas in fig. 2 the flow direction is indicated by two solid drawn arrows. The housing 2 has a tube 3 arranged therein and is formed by a U-shaped first housing part 2 'and a housing cover 2 ", wherein the cover is placed on the first housing part 2' from the top. For the inflow and outflow of the cooling liquid (second liquid medium), two cooling liquid connections 5 are provided in the housing cover 2 ″, whereas in fig. 2 the flow direction of the cooling liquid in the forward flow mode is indicated by the arrows drawn with dashed lines. The flow through can likewise be effected in counterflow, so that the flow direction of the coolant is reversed. Since the coolant flows in the housing 2 and flows around the tubes 3, the fin plates 4 are arranged on the coolant side.
In fig. 3, the coolant easily passes through the fin plate 4 having the straight serration structure in the direction indicated by the arrow drawn by the solid line, whereas the coolant does not easily pass through the fin plate in the direction indicated by the arrow drawn by the broken line. The flow of the medium can be influenced by varying the longitudinal and transverse spans L, Q and the fin height h. Instead of straight serrations, slanted serrations may be used. In the corresponding configuration of the respective fin plate 4, the fin plate contributes to a targeted delivery of the cooling liquid to particularly critical locations, for which reason the fin plate 4 is at least partially inhomogeneous.
Fig. 4 shows a simple variant of a fin plate with linearly extending fins having a longitudinal span L of 2.4mm and a fin or structural member height h of 1.5 mm. The fin plate can also be formed by a perforated plate which is bent so that the corrugated side walls are penetrated by the medium due to the holes.
In an embodiment, not shown, a corresponding structural element is applied to the charge air cooler.
In fig. 5a-d are non-uniform areas of the structure formed by the fin plate 4. They allow better distribution of the fluid when it is introduced. According to a first variant, shown in fig. 5a, the transverse distribution ducts are formed by forming or stamping. According to a variant in fig. 5b and 5c, a portion of the fin plate 4 is cut away. The variant shown in fig. 5d has a special distributor structure formed on the fin plate 4. On the exit side, a non-uniform area can also be provided, as shown in fig. 5a to 5 d.
Claims (30)
1. Heat exchanger for a motor vehicle, with a housing (2) and at least one tube (3) arranged in the housing (2), characterized in that structural elements are provided between the tube (3) and the housing (2) and/or between the tubes (3), and that the inner and/or outer surfaces of the tubes (3) have means for creating turbulence.
2. Heat exchanger according to claim 1, characterized in that the structural members are formed by structural plates arranged between the tubes (3) and the shell (2) and/or between the tubes (3).
3. A heat exchanger according to claim 2, characterized in that the structured plates are fin plates (4), plates with spherical protrusions or separate tube structures.
4. Heat exchanger according to claim 1, characterized in that the structural members are formed directly on the shell (2) and/or the tubes (3).
5. The heat exchanger of claim 4, wherein the structural members are formed by pressing.
6. Heat exchanger according to one of the preceding claims, wherein the structural parts are fixedly connected to the housing (2) and/or the tubes (3) in a manner comprising a brazed joint.
7. Heat exchanger according to claim 1, characterized in that at least a part of the tubes (3) are flat tubes.
8. Heat exchanger according to claim 7, characterized in that the tubes (3) are provided with supporting knobs on the outside of the tubes.
9. A heat exchanger according to claim 1 or 2 or 3 or 4 or 5, wherein at least a part of the structural members are of non-uniform configuration.
10. The heat exchanger of claim 8, wherein at least a portion of the structural members are of non-uniform configuration.
11. A heat exchanger according to claim 1 or 2 or 3 or 4 or 5, wherein at least a portion of the structural members are serrated.
12. Heat exchanger according to claim 1 or 2 or 3 or 4 or 5, characterized in that the housing (2) is made of two or three parts.
13. Heat exchanger according to claim 1 or 2 or 3 or 4 or 5, characterized in that the medium to be cooled flows in the tubes (3) and that the cooling liquid flows in the interspaces between the shell (2) and the tubes (3) and the structural elements.
14. A heat exchanger according to claim 9, characterized in that the medium to be cooled flows in the tubes (3) and that the cooling liquid flows in the interspaces between the shell (2) and the tubes (3) and the structural parts.
15. A heat exchanger according to claim 10, characterized in that the medium to be cooled flows in the tubes (3) and that the cooling liquid flows in the interspaces between the shell (2) and the tubes (3) and the structural parts.
16. A heat exchanger according to claim 11, characterized in that the medium to be cooled flows in the tubes (3) and that the cooling liquid flows in the interspaces between the shell (2) and the tubes (3) and the structural parts.
17. A heat exchanger according to claim 12, characterized in that the medium to be cooled flows in the tubes (3) and that the cooling liquid flows in the interspaces between the shell (2) and the tubes (3) and the structural parts.
18. A heat exchanger according to claim 1 or 2 or 3 or 4 or 5, characterised in that the structural parts in the housing (2) of the heat exchanger (1) are arranged on the coolant side.
19. Heat exchanger according to claim 9, characterized in that the structural parts in the housing (2) of the heat exchanger (1) are arranged on the coolant side.
20. Heat exchanger according to claim 10, characterized in that the structural parts in the housing (2) of the heat exchanger (1) are arranged on the coolant side.
21. Heat exchanger according to claim 11, characterized in that the structural parts in the housing (2) of the heat exchanger (1) are arranged on the coolant side.
22. Heat exchanger according to claim 12, characterized in that the structural parts in the housing (2) of the heat exchanger (1) are arranged on the coolant side.
23. Heat exchanger according to claim 13, characterized in that the structural parts in the housing (2) of the heat exchanger (1) are arranged on the coolant side.
24. Heat exchanger according to claim 14, characterized in that the structural parts in the housing (2) of the heat exchanger (1) are arranged on the coolant side.
25. Heat exchanger according to claim 15, characterized in that the structural parts in the housing (2) of the heat exchanger (1) are arranged on the coolant side.
26. Heat exchanger according to claim 16, characterized in that the structural parts in the housing (2) of the heat exchanger (1) are arranged on the coolant side.
27. Heat exchanger according to claim 17, characterized in that the structural parts in the housing (2) of the heat exchanger (1) are arranged on the coolant side.
28. A heat exchanger according to claim 1 or 2 or 3 or 4 or 5, wherein the structural member is arranged inside at least one tube.
29. A heat exchanger according to claim 1 or 2 or 3 or 4 or 5, wherein the structural members are at least one fin, and the fins are straight or corrugated and/or ribbed.
30. Heat exchanger according to one of claims 1 to 5, characterized in that it is used as an exhaust gas heat exchanger or charge air cooler for a motor vehicle.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE10349259.3 | 2003-10-20 | ||
| DE10349259 | 2003-10-20 | ||
| EP04024691.0 | 2004-10-15 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1898519A CN1898519A (en) | 2007-01-17 |
| CN100447518C true CN100447518C (en) | 2008-12-31 |
Family
ID=34399543
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2004800381366A Active CN100447518C (en) | 2003-10-20 | 2004-10-20 | Heat exchanger |
Country Status (3)
| Country | Link |
|---|---|
| EP (1) | EP1528348B1 (en) |
| CN (1) | CN100447518C (en) |
| DE (1) | DE102004050567A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110959097A (en) * | 2017-08-04 | 2020-04-03 | 希塔科技有限公司 | Heat exchanger |
Families Citing this family (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102005042315A1 (en) * | 2005-09-06 | 2007-03-08 | Behr Gmbh & Co. Kg | Coolant cooler, in particular for a motor vehicle |
| EP1929231B1 (en) | 2005-09-16 | 2018-08-01 | MAHLE Behr GmbH & Co. KG | Heat exchanger, in particular exhaust gas heat exchanger for motor vehicles |
| US8915292B2 (en) | 2006-02-07 | 2014-12-23 | Modine Manufacturing Company | Exhaust gas heat exchanger and method of operating the same |
| DE102006005362A1 (en) * | 2006-02-07 | 2007-08-09 | Modine Manufacturing Co., Racine | Exhaust gas heat exchanger in an exhaust gas recirculation arrangement |
| WO2008113540A2 (en) | 2007-03-16 | 2008-09-25 | Behr Gmbh & Co. Kg | Flow channel, heat exchanger, exhaust gas recycling system, charge air supply system, use of a heat exchanger |
| DE102007024379A1 (en) * | 2007-05-23 | 2008-11-27 | Mingatec Gmbh | Plate apparatus for heat transfer operations |
| DE102009012027A1 (en) * | 2009-03-10 | 2010-09-16 | Behr Gmbh & Co. Kg | Apparatus for supplying combustion air to an internal combustion engine |
| DE102009035723B3 (en) * | 2009-07-31 | 2011-02-03 | Pierburg Gmbh | Cooling device for an internal combustion engine |
| ES2401626B1 (en) * | 2011-10-05 | 2014-09-02 | Valeo Térmico, S. A. | HEAT EXCHANGER FOR GASES, ESPECIALLY OF EXHAUST GASES OF AN ENGINE |
| DE102012217872A1 (en) * | 2012-09-28 | 2014-04-03 | Behr Gmbh & Co. Kg | Heat exchanger |
| CN105486150A (en) * | 2016-01-11 | 2016-04-13 | 芜湖美的厨卫电器制造有限公司 | Heat exchange part and heat exchanger |
| CN110274227B (en) * | 2017-05-22 | 2021-03-16 | 中国北方车辆研究所 | Combustion air supply circular plate and combustor system thereof |
| CN110513677B (en) * | 2017-05-22 | 2021-06-04 | 中国北方车辆研究所 | Vehicle heater system |
| CN107246346B (en) * | 2017-05-22 | 2018-11-27 | 中国北方车辆研究所 | A kind of burner mounting seat and the buner system including pedestal |
| CN110274225B (en) * | 2017-05-22 | 2020-10-30 | 中国北方车辆研究所 | Mounting bracket and combustor system thereof |
| CN108626037B (en) * | 2018-06-11 | 2024-06-18 | 山东宇洋汽车尾气净化装置有限公司 | Compact EGR cooler |
| CN109612311A (en) * | 2019-01-17 | 2019-04-12 | 广东环葆嘉节能科技有限公司 | A kind of heat-exchanging component and heat exchanger |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001174169A (en) * | 1999-12-20 | 2001-06-29 | Denso Corp | Heat exchanger |
| JP2001330394A (en) * | 2000-05-22 | 2001-11-30 | Denso Corp | Exhaust gas heat exchanger |
| JP2003090693A (en) * | 2001-07-10 | 2003-03-28 | Denso Corp | Exhaust gas heat exchanger |
| JP2003106794A (en) * | 2000-12-19 | 2003-04-09 | Denso Corp | Exhaust heat exchanger |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7077190B2 (en) * | 2001-07-10 | 2006-07-18 | Denso Corporation | Exhaust gas heat exchanger |
-
2004
- 2004-10-15 EP EP04024691.0A patent/EP1528348B1/en active Active
- 2004-10-15 DE DE102004050567A patent/DE102004050567A1/en not_active Withdrawn
- 2004-10-20 CN CNB2004800381366A patent/CN100447518C/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001174169A (en) * | 1999-12-20 | 2001-06-29 | Denso Corp | Heat exchanger |
| JP2001330394A (en) * | 2000-05-22 | 2001-11-30 | Denso Corp | Exhaust gas heat exchanger |
| JP2003106794A (en) * | 2000-12-19 | 2003-04-09 | Denso Corp | Exhaust heat exchanger |
| JP2003090693A (en) * | 2001-07-10 | 2003-03-28 | Denso Corp | Exhaust gas heat exchanger |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110959097A (en) * | 2017-08-04 | 2020-04-03 | 希塔科技有限公司 | Heat exchanger |
| CN110959097B (en) * | 2017-08-04 | 2021-10-01 | 希塔科技有限公司 | Heat exchanger |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102004050567A1 (en) | 2005-06-09 |
| CN1898519A (en) | 2007-01-17 |
| EP1528348B1 (en) | 2014-03-05 |
| EP1528348A1 (en) | 2005-05-04 |
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