US20140345839A1 - Heat Exchanger For Gas, Particularly For Engine Exhaust Gases - Google Patents
Heat Exchanger For Gas, Particularly For Engine Exhaust Gases Download PDFInfo
- Publication number
- US20140345839A1 US20140345839A1 US14/361,322 US201214361322A US2014345839A1 US 20140345839 A1 US20140345839 A1 US 20140345839A1 US 201214361322 A US201214361322 A US 201214361322A US 2014345839 A1 US2014345839 A1 US 2014345839A1
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- US
- United States
- Prior art keywords
- casing
- protuberances
- heat exchanger
- tubes
- tube
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
- 239000007789 gas Substances 0.000 title claims abstract description 32
- 230000006835 compression Effects 0.000 claims abstract description 6
- 238000007906 compression Methods 0.000 claims abstract description 6
- 238000005476 soldering Methods 0.000 claims description 10
- 239000012809 cooling fluid Substances 0.000 claims description 6
- 230000002787 reinforcement Effects 0.000 claims description 6
- 101100028082 Arabidopsis thaliana OPR3 gene Proteins 0.000 claims description 3
- 239000002826 coolant Substances 0.000 abstract 1
- 238000003466 welding Methods 0.000 description 10
- 239000000463 material Substances 0.000 description 7
- 239000012530 fluid Substances 0.000 description 5
- 230000035945 sensitivity Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 229910052751 metal Inorganic materials 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000003134 recirculating effect Effects 0.000 description 2
- 239000004411 aluminium Substances 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 238000004458 analytical method Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 239000000112 cooling gas Substances 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 229910003460 diamond Inorganic materials 0.000 description 1
- 239000010432 diamond Substances 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 229920003023 plastic Polymers 0.000 description 1
- 239000004033 plastic Substances 0.000 description 1
- 239000002994 raw material Substances 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
- 239000010935 stainless steel Substances 0.000 description 1
Images
Classifications
-
- 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
- F28D7/0041—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 for only one medium being tubes having parts touching each other or tubes assembled in panel form
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy
- F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using heat
-
- 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
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
- F28D7/1684—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/007—Auxiliary supports for elements
- F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/02—Tubular elements of cross-section which is non-circular
- F28F2001/027—Tubular elements of cross-section which is non-circular with dimples
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2240/00—Spacing means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2275/00—Fastening; Joining
- F28F2275/04—Fastening; Joining by brazing
Definitions
- the present invention relates to a heat exchanger for gas, in particular for the exhaust gases of an engine.
- the invention is used more specifically in heat exchangers for recirculating exhaust gases of an engine (EGRC).
- heat exchangers for cooling gas for example those used in systems for recirculating exhaust gases towards the input of a positive-ignition engine, the two media which exchange heat are separated by a wall.
- the basic principle in a heat exchanger is the exchange of heat between two fluids at different temperatures.
- the hot fluid and the cold fluid conventionally flow through independent circuits which are located as close as possible to each other.
- the efficiency of the exchange depends on the mass flow rate, the speed, the specific heat and the temperature of each fluid relative to the other.
- the design of each circuit, the design of the partition wall and the raw materials are also important.
- EGR exchangers present on the market corresponds to a metal heat exchanger which is generally made of stainless steel or aluminium.
- the heat exchanger itself may have different configurations: for example, it may consist of a casing inside which there are arranged a series of parallel conduits for the passage of gases, the cooling fluid flowing in the casing, outside the conduits; in another embodiment, the exchanger is composed of a series of parallel plates which form the heat exchange surfaces so that the exhaust gases and the cooling fluid flow between two plates, in alternate layers.
- the assembly between the conduits and the casing may be of different types.
- the conduits are fixed by means of the ends thereof between two support plates which are connected at each of the casing, the two support plates having a plurality of holes for positioning the respective conduits. These support plates are in turn fixed to means for connection to the recirculation conduit.
- connection means may consist of a V-shaped branch or a peripheral connection edge or flange, depending on the design of the recirculation conduit where the heat exchanger is assembled.
- the support plate is constructed in one piece with the connection means and forms a single connection flange.
- the connection means may also consist of a gas reservoir which is arranged at one or both ends of the casing.
- EGR exchanger In the two types of EGR exchanger, the majority of the components thereof are metal so that they are assembled using mechanical means and then welded in a furnace, or arc- or laser-welded, in order to ensure the appropriate sealing required by this application. In some cases, they may also comprise some components made of plastics material, which may have a single function or several functions integrated in a single component.
- the undulations or fins help to guide the fluid so that it can correctly fill the entire circuit, promote heat exchange and improve the mechanical strength when there is an increase of pressure in the circuit.
- Patent application ES 2331218 describes a tubular heat exchanger having a casing which comprises a series of protuberances which are stamped on its surface and directed towards the inside thereof so that the protuberances are arranged at a predetermined distance relative to the assembly of tubes, which thus ensures controlled expansion of the tubes in the event of a pressure increase.
- Patent DE19961054368 describes a heat exchanger which comprises a bundle of gas tubes having a rectangular cross-section arranged inside a casing.
- the tubes comprise protuberances which are directed towards the outside and which determine the distance between adjacent tubes and relative to the inner surface of the casing.
- Furnace soldering of the assembly formed by the tubes, the casing and the fins is carried out after complete assembly of the various components of the exchanger.
- the quality of the final furnace welding will be appropriate only on the condition that complete contact of the components is ensured during furnace soldering.
- the objective of the heat exchanger for gas, in particular the exhaust gases of an engine, according to the present invention is to overcome the disadvantages of the exchangers known in the art by providing excellent distribution of the compression between the assembled components and good furnace soldering of the exchanger.
- the heat exchanger for gas in particular for the exhaust gases of an engine, to which the present invention relates is of the type which comprises a plurality of parallel tubes which are arranged inside a casing and via which the gases to be cooled by means of heat exchange with a cooling fluid circulate, and fins which disrupt the flow of gas and which are arranged inside each tube, and is characterised in that the tubes and the casing comprise each a plurality of protuberances whose distribution pattern and dimensions are defined in accordance with the dimensions of the tubes and the casing, and which are capable of ensuring good distribution of the compression between the casing, the tubes and the fins with respect to one another during the furnace welding of the exchanger.
- the invention is consequently based on a pattern and specific dimensions of the protuberances which are arranged on the surface of the casing and the tubes.
- the protuberances are produced by means of stamping, each protuberance comprising a protruding contact surface which is substantially planar and circular and a frustoconical side defined by a stamping angle and connection radii relative to said contact surface and to the surface of the tube or the casing where the protuberance is stamped.
- the dimensions of the protuberances of both the tubes and the casing are defined by their diameter and height, the stamping angle and the connection radii at the frustoconical side.
- the distribution pattern of the protuberances on the tubes is defined in accordance with the thickness, the width and the length of the tube itself, the tubes having a substantially rectangular cross-section and being provided with two opposing flat sides which are wider than they are high.
- the protuberances are arranged on the two opposing flat sides of the tubes, orientated towards the outside of the tube and distributed in one or more longitudinal rows in accordance with the width of the tube.
- the protuberances of the same row on the tubes are spaced apart by a predetermined distance defined by the length of the tube, and the first protuberance of the corresponding row is arranged relative to an of the tube at a predetermined distance which is also defined by the length of the tube.
- the protuberances on the tubes are distributed over two mutually parallel, longitudinal rows which are equidistant relative to a longitudinal axis of symmetry and which are spaced apart by a predetermined distance which is defined in accordance with the width of the tube.
- each reinforcement protuberance which are each located relative to an of the tube at a predetermined distance defined by the length of the tube.
- the distribution pattern of the protuberances on the casing is defined in accordance with the width of the tube and the thickness, the width and the length of the casing, the casing having a substantially rectangular cross-section.
- the protuberances are arranged on at least one side of the casing, directed towards the inside of the casing and distributed in one or more groups of two longitudinal rows in accordance with the width of the casing.
- the protuberances of the same row on the casing are spaced apart by a predetermined distance which is defined by the length of the casing, and the first protuberance of the corresponding row is arranged relative to one of the casing at a predetermined distance which is also defined by the length of the casing.
- the protuberances on the casing are distributed in two groups of two mutually parallel, longitudinal rows which are spaced apart by a predetermined distance defined in accordance with the width of the casing, and the two groups of two rows are equidistant relative to a longitudinal axis of symmetry.
- each group there are two reinforcement protuberances which are each located relative to an of the casing at a predetermined distance which is defined by the length of the casing.
- the protuberances may have different shapes such as, inter alia, circular, cross-like, diamond-like or linear.
- FIG. 1 is a perspective view of a known heat exchanger provided with protuberances on the casing;
- FIG. 2 is a perspective view of the heat exchanger of FIG. 1 , without the gas reservoirs and along a longitudinal section of the casing in order to show the assembly of parallel tubes accommodated therein;
- FIG. 3 is a view along a cross-section of a tube showing the fins which are accommodated inside it and the protuberances according to the invention
- FIG. 4 is a perspective view of a tube with a single row of protuberances according to a first embodiment of the invention
- FIG. 5 is a front view of the tube of FIG. 4 ;
- FIG. 6 is a plan view of the tube of FIG. 4 ;
- FIG. 7 is a detailed cross-section of a protuberance of the tube along the line VII-VII of FIG. 6 ;
- FIG. 8 is a plan view of the casing with a group of two rows of protuberances, according to the first embodiment of the invention.
- FIG. 9 is a detailed cross-section of a protuberance of the casing along the line IX-IX of FIG. 8 ;
- FIG. 10 is a perspective view of a tube with two rows of protuberances according to a second embodiment of the invention.
- FIG. 11 is a front view of the tube of FIG. 10 ;
- FIG. 12 is a plan view of the tube of FIG. 10 ;
- FIG. 13 is a detailed cross-section of a protuberance of the tube along the line XIII-XIII of FIG. 12 ;
- FIG. 14 is a plan view of the casing with two groups of two rows of protuberances, according to the second embodiment of the invention.
- FIG. 15 is a detailed cross-section of a protuberance of the casing along the line XV-XV of FIG. 14 ;
- FIGS. 16 a to 16 e are plan views of five protuberances which have different shapes and orientations;
- FIG. 17 is a diagram relating to the sensitivity of the position of the protuberances.
- FIG. 18 is a diagram relating to the sensitivity of the thickness of the soldering material.
- the heat exchanger 1 for gas in particular for the exhaust gases of an engine, comprises an assembly of parallel tubes 2 which, in this example, are flat, have a rectangular cross-section and are intended for the circulation of the gases with exchange of heat with a cooling fluid.
- Said assembly of parallel conduits 2 is accommodated inside a casing 3 which, in this instance, also has a rectangular cross-section.
- FIG. 2 shows the casing 3 in longitudinal section, in order to show the assembly of parallel tubes 2 therein.
- the two ends of the assembly of parallel conduits 2 are each fixed to a support plate 4 which has a plurality of holes for positioning the respective conduits 2 .
- Each support plate 4 is assembled at the corresponding of the casing 3 .
- the casing 3 comprises at each of the two ends thereof a gas reservoir 5 which is assembled on the gas recirculation conduit, although it would also be possible to use a connection flange and a gas reservoir.
- the casing 3 also comprises an inlet conduit 6 and an output conduit 7 of the cooling circuit.
- fins 9 which are arranged inside the tubes 2 , as can be seen in FIG. 3 .
- Furnace soldering of the assembly formed by the tubes 2 , the casing 3 and the fins 9 is carried out after complete assembly of the various components of the exchanger 1 .
- the quality of the final furnace welding will be appropriate only on the condition that complete contact of the components is ensured during the furnace-soldering process.
- the tubes 2 and the casing 3 comprise a plurality of protuberances 10 and 11 , respectively, whose distribution pattern and dimensions are defined in accordance with the dimensions of the tubes 2 and the casing 3 and which are capable of ensuring appropriate distribution of the compression between the casing 3 , the tubes 2 and the fins 9 relative to one another during assembly and furnace soldering of the exchanger 1 .
- protuberances 10 , 11 are produced by means of stamping and have a circular configuration.
- Each protuberance 10 , 11 comprises a substantially planar and circular protruding contact surface 12 and a frustoconical side which is defined by a stamping angle A and connection radii RR relative to said contact surface 12 and to the surface of the tube 2 or casing 3 where the protuberance 10 , 11 is stamped.
- the dimensions of the protuberances 10 , 11 of the tubes 2 and the casing 3 , respectively, are defined by their diameter D and height H, the stamping angle A and the connection radii RR at the frustoconical side.
- a tube 2 has been illustrated with a single row of protuberances 10 .
- the definition of the protuberance pattern 10 is determined by the following geometric relationships:
- a casing 3 has been illustrated with a single group of two rows of protuberances 11 .
- the definition of the protuberance pattern 11 is determined by the following geometric relationships:
- a tube 2 has been illustrated with two rows of protuberances 10 which are mutually parallel.
- the definition of the protuberance pattern 10 is determined by the following geometric relationships:
- a casing 3 has been illustrated with two groups of two rows of protuberances 11 which are mutually parallel.
- the definition of the protuberance pattern 11 is determined by the following geometric relationships:
- protuberances 10 , 11 have been illustrated with a circular configuration, they may also have other shapes, such as an elongate shape with different orientations (see FIGS. 16 a to 16 c ), or be in the form of a cross ( FIG. 16 d ) or of a diamond ( FIG. 16 e ), inter alia.
- the maximum permissible gap in this technology is 0.15 mm, which corresponds to a distance between protuberances of 40 mm. The greater the dimension of the gap, the more significant the furnace soldering defects and the more the mechanical strength is reduced.
- the maximum permissible gap in this technology is 0.15 mm, which corresponds to a thickness of the welding material of 50 micrometres.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
A heat exchanger uses engine exhaust gases. The heat exchanger comprises a plurality of parallel tubes arranged inside a header and through which the gases to be cooled by exchange of heat with a coolant flow, and fins that disturb the flow of the gas and that are arranged inside each tube. The tubes and the header comprise a plurality of protrusions and respectively, the distribution pattern and dimensions of which are defined according to the dimensions of the tubes and of the header and which are able to guarantee suitable distribution of the compression between the header, the tubes and the fins relative to one another while the heat exchanger is being assembled and brazed in the furnace.
Description
- The present invention relates to a heat exchanger for gas, in particular for the exhaust gases of an engine.
- The invention is used more specifically in heat exchangers for recirculating exhaust gases of an engine (EGRC).
- In some heat exchangers for cooling gas, for example those used in systems for recirculating exhaust gases towards the input of a positive-ignition engine, the two media which exchange heat are separated by a wall.
- The basic principle in a heat exchanger is the exchange of heat between two fluids at different temperatures. The hot fluid and the cold fluid conventionally flow through independent circuits which are located as close as possible to each other. The efficiency of the exchange depends on the mass flow rate, the speed, the specific heat and the temperature of each fluid relative to the other. The design of each circuit, the design of the partition wall and the raw materials are also important.
- The current configuration of EGR exchangers present on the market corresponds to a metal heat exchanger which is generally made of stainless steel or aluminium.
- The heat exchanger itself may have different configurations: for example, it may consist of a casing inside which there are arranged a series of parallel conduits for the passage of gases, the cooling fluid flowing in the casing, outside the conduits; in another embodiment, the exchanger is composed of a series of parallel plates which form the heat exchange surfaces so that the exhaust gases and the cooling fluid flow between two plates, in alternate layers.
- In the case of heat exchangers having a bundle of conduits, the assembly between the conduits and the casing may be of different types. Generally, the conduits are fixed by means of the ends thereof between two support plates which are connected at each of the casing, the two support plates having a plurality of holes for positioning the respective conduits. These support plates are in turn fixed to means for connection to the recirculation conduit.
- These connection means may consist of a V-shaped branch or a peripheral connection edge or flange, depending on the design of the recirculation conduit where the heat exchanger is assembled. In some cases, the support plate is constructed in one piece with the connection means and forms a single connection flange. The connection means may also consist of a gas reservoir which is arranged at one or both ends of the casing.
- In the two types of EGR exchanger, the majority of the components thereof are metal so that they are assembled using mechanical means and then welded in a furnace, or arc- or laser-welded, in order to ensure the appropriate sealing required by this application. In some cases, they may also comprise some components made of plastics material, which may have a single function or several functions integrated in a single component.
- In tubular exchangers, it is known to use fins or undulations inside the heat exchange circuits since they contribute to improving the heat exchange and the mechanical strength of the heat exchanger.
- The undulations or fins help to guide the fluid so that it can correctly fill the entire circuit, promote heat exchange and improve the mechanical strength when there is an increase of pressure in the circuit.
- Patent application ES 2331218, from the same patentee as the present application, describes a tubular heat exchanger having a casing which comprises a series of protuberances which are stamped on its surface and directed towards the inside thereof so that the protuberances are arranged at a predetermined distance relative to the assembly of tubes, which thus ensures controlled expansion of the tubes in the event of a pressure increase.
- Patent JP20010130114 describes a heat exchanger which comprises a bundle of gas tubes having a rectangular cross-section, inside which tubes it comprises fins having a notched cross-section and whose smooth portions (which form the peak and the trough) are in contact with the inner surface of the tube, and a plurality of protuberances arranged in the walls of the tube opposite the smooth portions of the fins. This arrangement of the protuberances allows the correct positioning of the fin inside the tube and prevents it from becoming disengaged.
- Patent DE19961054368 describes a heat exchanger which comprises a bundle of gas tubes having a rectangular cross-section arranged inside a casing. The tubes comprise protuberances which are directed towards the outside and which determine the distance between adjacent tubes and relative to the inner surface of the casing.
- It is known that, during assembly, successful integration of the fins inside the tubes is achieved only if the fins may be completely soldered to the tubes. If this is not the case, the mechanical strength and the increase of the thermal yields cannot be ensured.
- Furnace soldering of the assembly formed by the tubes, the casing and the fins is carried out after complete assembly of the various components of the exchanger. However, the quality of the final furnace welding will be appropriate only on the condition that complete contact of the components is ensured during furnace soldering.
- The objective of the heat exchanger for gas, in particular the exhaust gases of an engine, according to the present invention is to overcome the disadvantages of the exchangers known in the art by providing excellent distribution of the compression between the assembled components and good furnace soldering of the exchanger.
- The heat exchanger for gas, in particular for the exhaust gases of an engine, to which the present invention relates is of the type which comprises a plurality of parallel tubes which are arranged inside a casing and via which the gases to be cooled by means of heat exchange with a cooling fluid circulate, and fins which disrupt the flow of gas and which are arranged inside each tube, and is characterised in that the tubes and the casing comprise each a plurality of protuberances whose distribution pattern and dimensions are defined in accordance with the dimensions of the tubes and the casing, and which are capable of ensuring good distribution of the compression between the casing, the tubes and the fins with respect to one another during the furnace welding of the exchanger.
- The invention is consequently based on a pattern and specific dimensions of the protuberances which are arranged on the surface of the casing and the tubes.
- In this manner, optimum configuration of the tubes is achieved in order to obtain good furnace soldering of the fins used. At the same time, the configuration improves the durability of the mechanical strength for the service-life of the exchanger.
- The advantages achieved owing to the configuration of the protuberances according to the invention are described below:
-
- The casing of the exchanger allows the tubes and the fins to be compressed at the same time.
- The tubes, after assembly, allow the fins to be compressed in order to ensure good contact with the tubes.
- The contact of the casing and the tubes is ensured by the contact of the protuberances. These protuberances at the same time allow distribution of cooling fluid and contact between the components.
- The casing and the tubes have the same protuberance pattern so that the components are compressed at the same time.
- The pattern and the dimensions of the protuberances allow excellent distribution of the compression to be obtained, and ultimately good furnace welding of the exchanger.
- Preferably, the protuberances are produced by means of stamping, each protuberance comprising a protruding contact surface which is substantially planar and circular and a frustoconical side defined by a stamping angle and connection radii relative to said contact surface and to the surface of the tube or the casing where the protuberance is stamped.
- Advantageously, the dimensions of the protuberances of both the tubes and the casing are defined by their diameter and height, the stamping angle and the connection radii at the frustoconical side.
- Also in an advantageous manner, the distribution pattern of the protuberances on the tubes is defined in accordance with the thickness, the width and the length of the tube itself, the tubes having a substantially rectangular cross-section and being provided with two opposing flat sides which are wider than they are high.
- Preferably, the protuberances are arranged on the two opposing flat sides of the tubes, orientated towards the outside of the tube and distributed in one or more longitudinal rows in accordance with the width of the tube.
- In accordance with a first embodiment for the tubes, the protuberances of the same row on the tubes are spaced apart by a predetermined distance defined by the length of the tube, and the first protuberance of the corresponding row is arranged relative to an of the tube at a predetermined distance which is also defined by the length of the tube.
- In accordance with a second embodiment for the tubes, the protuberances on the tubes are distributed over two mutually parallel, longitudinal rows which are equidistant relative to a longitudinal axis of symmetry and which are spaced apart by a predetermined distance which is defined in accordance with the width of the tube.
- Preferably, between the two rows of protuberances on the tubes there are two reinforcement protuberances which are each located relative to an of the tube at a predetermined distance defined by the length of the tube.
- Advantageously, the distribution pattern of the protuberances on the casing is defined in accordance with the width of the tube and the thickness, the width and the length of the casing, the casing having a substantially rectangular cross-section.
- Preferably, the protuberances are arranged on at least one side of the casing, directed towards the inside of the casing and distributed in one or more groups of two longitudinal rows in accordance with the width of the casing.
- In accordance with a first embodiment for the casing, the protuberances of the same row on the casing are spaced apart by a predetermined distance which is defined by the length of the casing, and the first protuberance of the corresponding row is arranged relative to one of the casing at a predetermined distance which is also defined by the length of the casing.
- In accordance with a second embodiment for the casing, the protuberances on the casing are distributed in two groups of two mutually parallel, longitudinal rows which are spaced apart by a predetermined distance defined in accordance with the width of the casing, and the two groups of two rows are equidistant relative to a longitudinal axis of symmetry.
- Preferably, between the two rows of protuberances of each group there are two reinforcement protuberances which are each located relative to an of the casing at a predetermined distance which is defined by the length of the casing.
- Advantageously, the protuberances may have different shapes such as, inter alia, circular, cross-like, diamond-like or linear.
- In order to facilitate the description of what is set out above, drawings are appended in which there are illustrated schematically and only by way of non-limiting example various practical cases of an embodiment of the heat exchanger for gas, in particular for the exhaust gases of an engine, according to the invention, in which:
-
FIG. 1 is a perspective view of a known heat exchanger provided with protuberances on the casing; -
FIG. 2 is a perspective view of the heat exchanger ofFIG. 1 , without the gas reservoirs and along a longitudinal section of the casing in order to show the assembly of parallel tubes accommodated therein; -
FIG. 3 is a view along a cross-section of a tube showing the fins which are accommodated inside it and the protuberances according to the invention; -
FIG. 4 is a perspective view of a tube with a single row of protuberances according to a first embodiment of the invention; -
FIG. 5 is a front view of the tube ofFIG. 4 ; -
FIG. 6 is a plan view of the tube ofFIG. 4 ; -
FIG. 7 is a detailed cross-section of a protuberance of the tube along the line VII-VII ofFIG. 6 ; -
FIG. 8 is a plan view of the casing with a group of two rows of protuberances, according to the first embodiment of the invention; -
FIG. 9 is a detailed cross-section of a protuberance of the casing along the line IX-IX ofFIG. 8 ; -
FIG. 10 is a perspective view of a tube with two rows of protuberances according to a second embodiment of the invention; -
FIG. 11 is a front view of the tube ofFIG. 10 ; -
FIG. 12 is a plan view of the tube ofFIG. 10 ; -
FIG. 13 is a detailed cross-section of a protuberance of the tube along the line XIII-XIII ofFIG. 12 ; -
FIG. 14 is a plan view of the casing with two groups of two rows of protuberances, according to the second embodiment of the invention; -
FIG. 15 is a detailed cross-section of a protuberance of the casing along the line XV-XV ofFIG. 14 ; -
FIGS. 16 a to 16 e are plan views of five protuberances which have different shapes and orientations; -
FIG. 17 is a diagram relating to the sensitivity of the position of the protuberances; and -
FIG. 18 is a diagram relating to the sensitivity of the thickness of the soldering material. - With reference to
FIGS. 1 to 3 , the heat exchanger 1 for gas, in particular for the exhaust gases of an engine, comprises an assembly ofparallel tubes 2 which, in this example, are flat, have a rectangular cross-section and are intended for the circulation of the gases with exchange of heat with a cooling fluid. Said assembly ofparallel conduits 2 is accommodated inside acasing 3 which, in this instance, also has a rectangular cross-section. -
FIG. 2 shows thecasing 3 in longitudinal section, in order to show the assembly ofparallel tubes 2 therein. The two ends of the assembly ofparallel conduits 2 are each fixed to asupport plate 4 which has a plurality of holes for positioning therespective conduits 2. Eachsupport plate 4 is assembled at the corresponding of thecasing 3. - In this embodiment, the
casing 3 comprises at each of the two ends thereof a gas reservoir 5 which is assembled on the gas recirculation conduit, although it would also be possible to use a connection flange and a gas reservoir. Thecasing 3 also comprises an inlet conduit 6 and anoutput conduit 7 of the cooling circuit. - In order to improve the heat exchange and the mechanical strength of the exchanger 1, there are used fins 9 which are arranged inside the
tubes 2, as can be seen inFIG. 3 . - Furnace soldering of the assembly formed by the
tubes 2, thecasing 3 and the fins 9 is carried out after complete assembly of the various components of the exchanger 1. The quality of the final furnace welding will be appropriate only on the condition that complete contact of the components is ensured during the furnace-soldering process. - In the same manner, the
tubes 2 and thecasing 3 comprise a plurality ofprotuberances tubes 2 and thecasing 3 and which are capable of ensuring appropriate distribution of the compression between thecasing 3, thetubes 2 and the fins 9 relative to one another during assembly and furnace soldering of the exchanger 1. - Two embodiments of protuberance patterns on the
tubes 2 and thecasing 3 are described below, respectively. In these instances, theprotuberances protuberance contact surface 12 and a frustoconical side which is defined by a stamping angle A and connection radii RR relative to saidcontact surface 12 and to the surface of thetube 2 orcasing 3 where theprotuberance - The dimensions of the
protuberances tubes 2 and thecasing 3, respectively, are defined by their diameter D and height H, the stamping angle A and the connection radii RR at the frustoconical side. - According to a first embodiment for the
tube 2 illustrated inFIGS. 4 to 7 , atube 2 has been illustrated with a single row ofprotuberances 10. - The definition of the
protuberance pattern 10 is determined by the following geometric relationships: -
- H=(1 to 4)×T1
- D=(0.1 to 0.5)×W1 and/or D=(0.06 to 0.4)×DD
- RR=(0.5 to 2)×T1 and/or RR=(0.1 to 0.6)×H
- 45°≦A≦75°
- DD=(0.05 to 0.6)×L1
- DDE=(0.05 to 0.6)×L1
- Position of a row of
protuberances 10 carried by the longitudinal line of symmetry of the tube±10 mm. - Protuberances distributed over a row if: 10≦W1≦30 mm
- Protuberances distributed over two rows if: 26≦W1≦45 mm
- where:
- H: Height of the
protuberance 10 - D: Diameter of the
contact surface 12 of theprotuberance 10 - RR: Connection radius relative to the
contact surface 12 and to the surface of thetube 2 - A: Stamping angle of the
protuberance 10 - T1: Thickness of the
tube 2 - W1: Width of the
tube 2 - L1: Length of the
tube 2 - DD: Distance between
protuberances 10 of the same row - DDE: Distance between the centre of the
first protuberance 10 of a row and an of thetube 2.
- According to a first embodiment for the
casing 3 illustrated inFIGS. 8 and 9 , acasing 3 has been illustrated with a single group of two rows ofprotuberances 11. - The definition of the
protuberance pattern 11 is determined by the following geometric relationships: -
- P=(1 to 4)×T2
- D=(0.1 to 0.5)×W1
- RR=(0.5 to 2)×T2 and/or RR=(0.1 to 0.6)×H
- DD=(0.05 to 0.6)×L2
- DDE=(0.05 to 0.6)×L2
- Position of a row of
protuberances 11 centred on the longitudinal axis of symmetry of the casing±10 mm. - where:
- P: Depth of the
protuberance 11 - H: Height of the
protuberance 11 - D: Diameter of the
contact surface 12 of theprotuberance 11 - RR: Connection radius relative to the
contact surface 12 - T2: Thickness of the
casing 3 - W1: Width of the
tube 2 - L2: Length of the
casing 3 - DD: Distance between
protuberances 11 of the same row - DDE: Distance between the centre of the
first protuberance 11 of a row and an of thecasing 3.
- According to a second embodiment for the
tube 2 illustrated inFIGS. 10 to 13 , atube 2 has been illustrated with two rows ofprotuberances 10 which are mutually parallel. - Likewise, between the two rows of
protuberances 10 on thetubes 2 are tworeinforcement protuberances 10 a which have a rectangular configuration with two semi-circles at the smallest opposing ends. - The definition of the
protuberance pattern 10 is determined by the following geometric relationships: -
- H=(1 to 4)×T1
- D=(0.1 to 0.5)×W1 and/or D=(0.06 to 0.4)×DD
- RR=(0.5 to 2)×T1 and/or RR=(0.1 to 0.6)×H
- 45°≦A≦75°
- Protuberances distributed over a row if: 10≦W1≦30 mm
- Protuberances distributed over two rows if: 26≦W1≦45 mm
- Number of protuberances: at least 1 protuberance over 100 to 600 mm2
- DDH=(0.05 to 0.6)×L1
- DDV:=(0.2 to 0.8)×W1
- DDE=(0.05 to 0.6)×L1
- DDE1A=(0.05 to 0.6)×L1
- DDE1B=(0.05 to 0.6)×L1
- where:
- H: Height of the
protuberance 10 - D: Diameter of the
contact surface 12 of theprotuberance 10 - RR: Connection radius relative to the
contact surface 12 and to thetube surface 2 - A: Stamping angle of the
protuberance 10 - T1: Thickness of the
tube 2 - W1: Width of the
tube 2 - L1: Length of the
tube 2 - DDH: Distance between
protuberances 10 of the same row - DDV: Distance between rows
- DDE: Distance between the
first protuberance 10 of a row and an of thetube 2. - DDE1A: Distance between a first centre of an
protuberance 10 a and an of the tube - DDE1B: Distance between a second centre of an
protuberance 10 a and an of thetube 2
- According to a second embodiment for the
casing 3 illustrated inFIGS. 14 and 15 , acasing 3 has been illustrated with two groups of two rows ofprotuberances 11 which are mutually parallel. - Likewise, between the two rows of
protuberances 11 of each group are tworeinforcement protuberances 11 a, which are circular in this instance. - The definition of the
protuberance pattern 11 is determined by the following geometric relationships: -
- P=(1 to 4)×T2
- D=(0.1 to 0.5)×W1
- RR=(0.5 to 2)×T2 and/or RR=(0.1 to 0.6)×H
- DDH=(0.05 to 0.6)×L2
- DDV=(0.2 to 0.8)×W2
- DDE=(0.05 to 0.6)×L1
- DdE1=(0.05 to 0.6)×L1
- where
- P: Depth of the
protuberance 11 - H: Height of the
protuberance 11 - D: Diameter of the
contact surface 12 of theprotuberance 11 - RR: Connection radius relative to the
contact surface 12 - T2: Thickness of the
casing 3 - W1: Width of the
tube 2 - W2: Width of the
casing 3 - L2: Length of the
casing 3 - DDH: Distance between
protuberances 11 of the same row - DDV: Distance between rows of the same group
- DDE: Distance between the centre of the
first protuberance 11 of a row and an of thecasing 3 - DDE1: Distance between the centre of an
protuberance 11 a and an of thecasing 3.
- It should be emphasised that, although
protuberances FIGS. 16 a to 16 c), or be in the form of a cross (FIG. 16 d) or of a diamond (FIG. 16 e), inter alia. - In the same manner, tests have been carried out with prototypes in order to analyse the relationship between the thickness of the welding material and the distance of the protuberances with respect to the gap which exists in the assembly joint with furnace welding.
- It is possible to see the results of a first test in the graph of
FIG. 17 , which shows the sensitivity of the position of theprotuberances tube 2. - The results indicate that, if the distance between protuberances is reduced, deformations are prevented during the assembly process (deformation of the tube 2) by means of which a smaller size of the gap between the
tubes 2 and the fins 9 is obtained. The maximum permissible gap in this technology is 0.15 mm, which corresponds to a distance between protuberances of 40 mm. The greater the dimension of the gap, the more significant the furnace soldering defects and the more the mechanical strength is reduced. - It is possible to see the results of a second text in the graph of
FIG. 18 , which shows the sensitivity of the thickness of the welding material, by establishing a ratio between the thickness of the welding material and the gap existing in the assembly joint when the fin 9 is introduced into thetube 2. - The results indicate that the larger the dimensions of the gap, the greater the thickness of the required welding material and, consequently, the more expensive the product. The maximum permissible gap in this technology is 0.15 mm, which corresponds to a thickness of the welding material of 50 micrometres.
Claims (15)
1. A heat exchanger (1) for exhaust gases of an engine, the heat exchanger (1) comprising a plurality of parallel tubes (2) which are arranged inside a casing (3) and via which the gases to be cooled by means of heat exchange with a cooling fluid circulate, and fins (9) which disrupt the flow of gas and which are arranged inside each tube (2), wherein the tubes (2) and the casing (3) comprise a plurality of protuberances (10) and (11), respectively, whose distribution pattern and dimensions are defined in accordance with dimensions of the tubes (2) and the casing (3), and which are capable of ensuring appropriate distribution of the compression between the casing (3), the tubes (2) and the fins (9) with respect to one another during furnace soldering of the heat exchanger (1).
2. The heat exchanger (1) according to claim 1 , wherein the protuberances (10, 11) are produced by means of stamping, each protuberance (10, 11) comprising a protruding contact surface (12) which is substantially planar and circular and a frustoconical side defined by a stamping angle (A) and connection radii (RR) relative to said contact surface (12) and to the surface of the tube (2) or the casing (3) where the protuberance (10, 11) is stamped.
3. The heat exchanger (1) according to claim 2 , wherein the dimensions of the protuberances (10, 11) of the tubes (2) and the casing (3), respectively, are defined by their diameter (D) and their height (H) and the stamping angle (A) and the connection radii (RR) at the frustoconical side.
4. The heat exchanger (1) according to claim 1 , wherein the distribution pattern of the protuberances (10) on the tubes (2) is defined in accordance with the thickness (T1), the width (W1) and the length (L1) of the tube (2) itself, the tubes (2) having a substantially rectangular cross-section and being provided with two opposing flat sides (W1) which are wider than they are high.
5. The heat exchanger (1) according to claim 4 , wherein the protuberances (10) are arranged on the two opposing flat sides of the tubes (2), directed towards the outside of the tube (2) and distributed over one or more longitudinal rows in accordance with the width (W1) of the tube (2).
6. The heat exchanger (1) according to claim 5 , wherein the protuberances (10) of the same row on the tubes (2) are spaced apart by a predetermined distance (DD, DDH) defined by the length (L1) of the tube (2), and the first protuberance (10) of the corresponding row is arranged relative to an of the tube (2) at a predetermined distance (DDE) which is also defined by the length (L1) of the tube (2).
7. The heat exchanger (1) according to claim 5 , wherein the protuberances (10) on the tubes (2) are distributed over two parallel, longitudinal rows which are equidistant relative to a longitudinal axis of symmetry and spaced apart by a predetermined distance (DDV) which is defined in accordance with the width (W1) of the tube (2).
8. The heat exchanger (1) according to claim 7 , wherein between the two rows of protuberances (10) on the tubes (2) there are two reinforcement protuberances (10 a) which are each located relative to the opposing ends of the tube (2) at a predetermined distance (DDE1, DDE2) defined by the length (L1) of the tube (2).
9. The heat exchanger (1) according to claim 1 , wherein the distribution pattern of the protuberances (11) on the casing (3) is defined in accordance with a width (W1) and thickness (T2) of the tube (2), a width (W2) and length (L2) of the casing (3), with the casing (3) having a substantially rectangular cross-section.
10. The heat exchanger (1) according to claim 9 , wherein the protuberances (11) are arranged on at least one side of the casing (3), directed towards the inside of the casing (3) and distributed in one or more groups of two longitudinal rows in accordance with the width (W2) of the casing (3).
11. The heat exchanger (1) according to claim 10 , wherein the protuberances (11) of the same row are spaced apart by a predetermined distance (DD, DDH) which is defined by the length (L2) of the casing (3) and the first protuberance (11) of the corresponding row is arranged relative to one of the casing (3) at a predetermined distance (DDE) which is also defined by the length (L2) of the casing (3).
12. The heat exchanger (1) according to claim 10 , wherein the protuberances (11) are distributed in two groups of two parallel, longitudinal rows which are spaced apart by a predetermined distance (DDV) defined in accordance with the width (W2) of the casing (3), and the two groups of two rows are arranged so as to be equidistant relative to the longitudinal axis of symmetry.
13. The heat exchanger (1) according to claim 12 , wherein between the two rows of protuberances (11) of each group there are two reinforcement protuberances (11 a) which are each located relative to the opposite ends of the casing (3) at a predetermined distance (DDE1) which is defined by the length (L2) of the casing (3).
14. The heat exchanger (1) according to claim 1 , wherein the protuberances (10, 11) may have different shapes such as, circular, cross-like, diamond-like or linear.
15. The heat exchanger (1) according to claim 2 , wherein the distribution pattern of the protuberances (10) on the tubes (2) is defined in accordance with the thickness (T1), the width (W1) and the length (L1) of the tube (2) itself, the tubes (2) having a substantially rectangular cross-section and being provided with two opposing flat sides (W1) which are wider than they are high.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
ES201131952A ES2406184B1 (en) | 2011-12-01 | 2011-12-01 | HEAT EXCHANGER FOR GASES, ESPECIALLY OF EXHAUST GASES OF AN ENGINE |
ESP201131952 | 2011-12-01 | ||
PCT/EP2012/074079 WO2013079656A1 (en) | 2011-12-01 | 2012-11-30 | Heat exchanger for gas, particularly for engine exhaust gases |
Publications (1)
Publication Number | Publication Date |
---|---|
US20140345839A1 true US20140345839A1 (en) | 2014-11-27 |
Family
ID=47263376
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/361,322 Abandoned US20140345839A1 (en) | 2011-12-01 | 2012-11-30 | Heat Exchanger For Gas, Particularly For Engine Exhaust Gases |
Country Status (5)
Country | Link |
---|---|
US (1) | US20140345839A1 (en) |
EP (1) | EP2786084A1 (en) |
KR (1) | KR20140106610A (en) |
ES (1) | ES2406184B1 (en) |
WO (1) | WO2013079656A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20170367217A1 (en) * | 2015-11-12 | 2017-12-21 | Apaltek Co., Ltd. | Liquid Cooling Radiation System and Liquid Radiator Thereof |
US20190186431A1 (en) * | 2017-12-14 | 2019-06-20 | Hanon Systems | Tube, in particular a flat tube for an exhaust gas cooler and exhaust gas cooler |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR3099240B1 (en) * | 2019-07-25 | 2021-08-06 | Valeo Systemes Thermiques | Heat exchanger in particular for a motor vehicle and method of manufacturing such a heat exchanger |
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DE19833338A1 (en) * | 1998-07-24 | 2000-01-27 | Modine Mfg Co | Heat exchangers, in particular exhaust gas heat exchangers |
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JP5250924B2 (en) * | 2001-07-16 | 2013-07-31 | 株式会社デンソー | Exhaust heat exchanger |
JP3879614B2 (en) * | 2002-07-25 | 2007-02-14 | 株式会社デンソー | Heat exchanger |
JP5107604B2 (en) * | 2007-04-27 | 2012-12-26 | 株式会社ティラド | Heat exchanger manufacturing method and heat exchanger |
ES2331218B1 (en) * | 2007-07-27 | 2010-09-29 | Valeo Termico, S.A. | HEAT EXCHANGER FOR GASES, ESPECIALLY OF EXHAUST GASES OF AN ENGINE. |
JP5486239B2 (en) * | 2009-08-18 | 2014-05-07 | 株式会社ティラド | Header plateless heat exchanger |
-
2011
- 2011-12-01 ES ES201131952A patent/ES2406184B1/en not_active Expired - Fee Related
-
2012
- 2012-11-30 EP EP12794337.1A patent/EP2786084A1/en not_active Withdrawn
- 2012-11-30 US US14/361,322 patent/US20140345839A1/en not_active Abandoned
- 2012-11-30 WO PCT/EP2012/074079 patent/WO2013079656A1/en active Application Filing
- 2012-11-30 KR KR1020147017539A patent/KR20140106610A/en not_active Application Discontinuation
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US3757855A (en) * | 1971-10-15 | 1973-09-11 | Union Carbide Corp | Primary surface heat exchanger |
US3810509A (en) * | 1971-10-15 | 1974-05-14 | Union Carbide Corp | Cross flow heat exchanger |
US6378203B1 (en) * | 2000-03-07 | 2002-04-30 | Thermal Dynamics Corporation | Method of making fluid heat exchanger |
US20030010479A1 (en) * | 2001-07-10 | 2003-01-16 | Takayuki Hayashi | Exhaust gas heat exchanger |
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US20170367217A1 (en) * | 2015-11-12 | 2017-12-21 | Apaltek Co., Ltd. | Liquid Cooling Radiation System and Liquid Radiator Thereof |
US10609841B2 (en) * | 2015-11-12 | 2020-03-31 | Shenzhen APALTEK Co., Ltd. | Liquid cooling radiation system and liquid radiator thereof |
US20190186431A1 (en) * | 2017-12-14 | 2019-06-20 | Hanon Systems | Tube, in particular a flat tube for an exhaust gas cooler and exhaust gas cooler |
Also Published As
Publication number | Publication date |
---|---|
ES2406184B1 (en) | 2014-04-29 |
ES2406184A2 (en) | 2013-06-05 |
ES2406184R1 (en) | 2013-07-02 |
KR20140106610A (en) | 2014-09-03 |
EP2786084A1 (en) | 2014-10-08 |
WO2013079656A1 (en) | 2013-06-06 |
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Legal Events
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Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |