CA1090778A - Exhaust gas heat exchanger - Google Patents
Exhaust gas heat exchangerInfo
- Publication number
- CA1090778A CA1090778A CA284,385A CA284385A CA1090778A CA 1090778 A CA1090778 A CA 1090778A CA 284385 A CA284385 A CA 284385A CA 1090778 A CA1090778 A CA 1090778A
- Authority
- CA
- Canada
- Prior art keywords
- fluid
- heat exchanger
- dished
- outlet
- portions
- 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.)
- Expired
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/12—Elements constructed in the shape of a hollow panel, e.g. with channels
-
- 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
- F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
- F01N3/02—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust
- F01N3/04—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust using liquids
- F01N3/043—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust using liquids without contact between liquid and exhaust gases
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
- F02M26/29—Constructional details of the coolers, e.g. pipes, plates, ribs, insulation or materials
- F02M26/32—Liquid-cooled heat exchangers
-
- 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
- F28D7/10—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 one within the other, e.g. concentrically
- F28D7/106—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 one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
- F28D9/0037—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the conduits for the other heat-exchange medium also being formed by paired plates touching each other
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/08—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning
- F28F3/086—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning having one or more openings therein forming tubular heat-exchange passages
-
- 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
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Landscapes
- 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)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Exhaust-Gas Circulating Devices (AREA)
- Exhaust Gas After Treatment (AREA)
Abstract
ABSTRACT
A heat exchanger for utilization in an exhaust gas recirculation system of an automotive internal combustion engine to reduce the temperature level of the exhaust gas from the combustion cycle that is metered from the exhaust manifold and recycled through the combustion cycle. The heat exchanger includes a pair of generally conformably nesting shells providing a relatively narrow chamber or envelope for fluid movement generally encompassing a central chamber in the inner shell for the hot gases; the central chamber having a turbulizer or fin member to enhance move-ment of heat outwardly from the exhaust gas passing there-through to the fluid circulating through the outer envelope.
The inner chamber may have a central spreader acting to move the exhaust gas outwardly toward the outer wall of the inner shell.
A heat exchanger for utilization in an exhaust gas recirculation system of an automotive internal combustion engine to reduce the temperature level of the exhaust gas from the combustion cycle that is metered from the exhaust manifold and recycled through the combustion cycle. The heat exchanger includes a pair of generally conformably nesting shells providing a relatively narrow chamber or envelope for fluid movement generally encompassing a central chamber in the inner shell for the hot gases; the central chamber having a turbulizer or fin member to enhance move-ment of heat outwardly from the exhaust gas passing there-through to the fluid circulating through the outer envelope.
The inner chamber may have a central spreader acting to move the exhaust gas outwardly toward the outer wall of the inner shell.
Description
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The present invention relates to exhaust gaQ recir-culation in the automotive internal combustion engine and more particularly to a means for cooling the exhaust gas that is returned to the combustion cycle. Since approxi-mately 1971, automotive vehicle manufacturers have been required to add an ever-increasing number of components or systems to the vehicle or to the internal combustion engine therein to increase the safety of the vehicle or decrease the emissions inherent in the exhaust gases from the in-ternal combustion engine. Such components include positive crankcase ventilation, exhaust gas recirculation, an evap-oration control system and a catalytic converter in the exhaust line.
Of major concern is the emissions from the exhaust gas of an internal combustion cycle which have been blamed for conditions such as smog occurring in large cities where a large number of automobiles are present each day. The ;~
oxides of nitrogen are one such emission, and an exhaust gas recirculation cycle is used to reduce these oxides present in the engine exhaust. Formation of nitrogen oxides takes place at very high temperatures and consequently occurs during the peak temperature period of the combustion pro-cess. To reduce and control nitrogen oxides formation, only a slight reduction in peak temperature is required.
This temperature reduction can be accomplished by introducing small amounts of an inert gas into the com-bustion process and, as the ent products of combustion ~'~029-LC
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provide a continuous supply of relatively inert gases, it becomes a matter of utilizing those gases in the correct proportion. Thus, a recirculation passage is connected to the exhaust manifold and to a vacuum modulated shut-off and metering valve installed on the inlet manifold to control the flow of exhaust gases. The recirculation or additional exhaust gas passages are closely positioned to the engine or may be cast into the complex runner system of the inlet manifold.
However, the exhaust gases from the internal combustion engine cycle are still at a very high temperature level and it is desirable to substantially reduce that temperature level before the gases are reintroduced into the combustion cycle. The present invention accomplishes this desired temperature reduction.
The present invention comprehends the provision of a heat exchanger to be inserted in the exhaust gas recir-culation system of an automotive internal combustion engine to cool the recirculating exhaust gases before reintro-duction into the inlet manifold. The heat exchanger is of a compact design to fit within the relatively crowded space in the engine compartment of the vehicle and to be easily mounted on the engine without substantially increasing the flow path of the recirculating gases.
The present invention also comprehends the provision of an exhaust gas heat exchanger having an outer envelope of
The present invention relates to exhaust gaQ recir-culation in the automotive internal combustion engine and more particularly to a means for cooling the exhaust gas that is returned to the combustion cycle. Since approxi-mately 1971, automotive vehicle manufacturers have been required to add an ever-increasing number of components or systems to the vehicle or to the internal combustion engine therein to increase the safety of the vehicle or decrease the emissions inherent in the exhaust gases from the in-ternal combustion engine. Such components include positive crankcase ventilation, exhaust gas recirculation, an evap-oration control system and a catalytic converter in the exhaust line.
Of major concern is the emissions from the exhaust gas of an internal combustion cycle which have been blamed for conditions such as smog occurring in large cities where a large number of automobiles are present each day. The ;~
oxides of nitrogen are one such emission, and an exhaust gas recirculation cycle is used to reduce these oxides present in the engine exhaust. Formation of nitrogen oxides takes place at very high temperatures and consequently occurs during the peak temperature period of the combustion pro-cess. To reduce and control nitrogen oxides formation, only a slight reduction in peak temperature is required.
This temperature reduction can be accomplished by introducing small amounts of an inert gas into the com-bustion process and, as the ent products of combustion ~'~029-LC
~ 7~
provide a continuous supply of relatively inert gases, it becomes a matter of utilizing those gases in the correct proportion. Thus, a recirculation passage is connected to the exhaust manifold and to a vacuum modulated shut-off and metering valve installed on the inlet manifold to control the flow of exhaust gases. The recirculation or additional exhaust gas passages are closely positioned to the engine or may be cast into the complex runner system of the inlet manifold.
However, the exhaust gases from the internal combustion engine cycle are still at a very high temperature level and it is desirable to substantially reduce that temperature level before the gases are reintroduced into the combustion cycle. The present invention accomplishes this desired temperature reduction.
The present invention comprehends the provision of a heat exchanger to be inserted in the exhaust gas recir-culation system of an automotive internal combustion engine to cool the recirculating exhaust gases before reintro-duction into the inlet manifold. The heat exchanger is of a compact design to fit within the relatively crowded space in the engine compartment of the vehicle and to be easily mounted on the engine without substantially increasing the flow path of the recirculating gases.
The present invention also comprehends the provision of an exhaust gas heat exchanger having an outer envelope of
-2-7t~
cooling fluid around a generally central gas flow p~ssa~e to reduce as far as possible the escape of heat to adjacent areas around the heat exchanger. The heat exchanger may also provide a central gas flow passage having a dead or inner tube extending axially in the center of the passage to effectively force the hot gases outwardly into contact with extended fin surfaces to enhance the heat transfer to the outer cooling water envelope.
The present invention further comprehends the provision of an exhaust gas heat exchanger which provides for adequate gas flow therethrough with low resistance or pressure drop. Although primarily utilized for exhaust gas recirculation systems, the same heat exchanger could be used to extract heat from the other exhaust gas flow and for other purposes, such as a fast passenger compartment heat-up system or for a gas turbine heat exchange system. The heat exchanger is formed of suitable materials to resist corrosion and decay in the highly corrosive exhaust gas environment.
Various embodiments of heat exchangers incorporating the aforementioned concepts of the present invention are disclosed i herein. The embodiment claimed herein is defined as a two fluid heat exchanger comprising a generally flat heat exchanger formed of two pairs of metal plates, the inner pair of plates having oppositely disposed dished portions forming a chamber and joined by peripheral flanges, the chamber having an inlet and an outlet adapted to receive a first fluid, a heat transfer surface formed of at least one metal plate received in the chamber, and the outer pair of plates having oppositely disposed dished portions and peripheral flanges generally completely joined to the flanges of the inner plates, the outer dished portions cooperating with the inner dished portions to form a fluid envelope generally encompassing the chamber and having an inlet and an outlet to .~ .~ ., .
ob/t' - lV~ 7~
receive a second fluid therein~ at least an oppositely disposed pair of side walls of the outer dished p~rtions are spaced from side walls of the inner dished portions, the flanges of the inner plates extend between the inner and outer side walls to divide the envelope into upper and lower portions and have openings therein to provide communication between the upper and lower envelope portions, the second fluid inlet and outlet being located in one of the outer dished portions, and a central depression is formed in the same dished portion to extend across the dished portion and divide the upper envelope portion between the inlet and outlet into generally equal halves.
In the accompanying drawings:
Figure 1 is a perspective view, partially broken away, of one form of exhaust gas heat exchanger.
Figure 2 is a side elevational view, partially broken ,' away, of the left-hand end of the heat exchanger of Figure 1.
Figure 3 is a vertical cross sectional view of the heat exchanger taken on the line 3-3 of Figure 2.
Figure 4 is a perspective view of a second embodiment of heat exchanger.
- 3a -ob~
0- ~29-LC ~ V~ 7~
FIGURE 5 is a vertical cross sectional view taken on the line 5-5 of FIGURE 4.
FIGURE 6 is a partial vertical cross sectional view taken on the irregular line 6-6 of FIGURE 4.
FIGURE 7 is a top plan view of a third embodiment of heat exchanger.
FIGURE 8 is a vertical cross sectional view taken on the line 8-8 of FIGURE 7.
FIGU~E 9 is a partial vertical cross sectional view taken on the line 9-9 of FIGURE 7.
FIGURE 10 is a top plan view of a fourth embodiment of heat exchanger.
FIGURE 11 is a vertical cross sectional view taken on the line 11-11 of FIGURE 10.
FIGURE 12 is a partial vertical cross sectional view taken on the line 12-12 of FIGURE 10.
FIGURE 13 is a perspective view of a fifth embodiment of heat exchanger with the ends omitted.
FIGURE 14 is a top plan view of the heat exchanger of FIGURE 13 including the end pieces and with the front and rear portions broken away.
FIGURE 15 is a vertical cross sectional view taken on the line 15-15 of FIGURE 14.
FIGURE 16 is a vertical cross sectional view of a heat exchanger plate taken on the line 16-16 of FIGURE 15.
Referring to the drawings an exhaust gas heat exchanger 10 for use in the exhaust gas recirculation line of an automotive internal combustion engine is provided which includes an outer cylindrical tube 11 and an inner cylindrical ~ `~29-LC
tube 12 forming an annular envelope 13 therebetween for cooling fluid admitted through an inlet conduit 14 and exiting through an outlet conduit 15. The inner and outer tubes 12 and 11 are crimped and secured together at the opposite ends to seal the fluid envelope 13 (FIGURE 2). The housing 11 is closed at the opposite ends by end plates 16 and 17, with an exhaust gas inlet conduit 18 being secured in one plate and an exhaust gas outlet conduit 19 centrally secured in the opposite plate, so that the heat exchanger may provide concurrent or counter current flow heat transfer.
Within the inner tube 12, a dead tube 21 is centrally positioned by an extended fin surface 23; the dead tube comprising a hollow tube closed at each end 22 by a rounded surface to effectively force the hot gases outwardly into the extended fin surface 23. The fin surface is preferably formed of a single sheet of material having a high heat conductivity and formed into a generally corrugated member of a sinusoidal configuration around the dead tube 21 with the peaks 24 contacting and suitably joined to the inner wall 12 and the inner apices 25 contacting and suitably joined to the dead tube 21; joining being by brazing or soldering. The fin surface 23 may be imperforate or may i contain a plurality of slits or louvres to enhance the heat transfer and to act as a turbulizer for the gas flow in the i passages formed by the fin surface.
This heat exchanger 10 provides a compact cylindrical design which will easily fit within the limited space requirements found in an automobile engine compartment and ~ t'~7~
has a double-walled passage or envelope 13 for a cooling fluid 26 which not only provides an efficient heat transfer from the hot exhaust gases but also provides insulation of the exhaust gas temperatures from the engine compartment to reduce the escape of heat therefrom into the hot engine compartment. The heat exchanger will rapidly cool the exhaust gases from a temperature of approximately 1250F. to a level of approximately 550F. and provides for adequate gas flow with low resistance or pressure drop. The material selected for the heat exchanger should provide high re-sistance to corrosion and decay from the corrosive exhaust gas environment; with a preferred material being a stainless steel, such as type 304 stainless steel.
FIGURES 4 through 6 disclose an alternate embodiment of heat exchanger 31 having a generally flat configuration which will easily and compactly fit alongside the vehicle engine in the limited space of the engine compartment. This heat exchanger is formed from four stamped pieces of sheet metal comprising a pair of symmetrical inner sheets 32,32a and a pair of generally identical outer pieces 47,47a; the inner pieces having flat flanges 33,33a around three sides of the unit and generally flat flanges 34,34a on the fourth side provided with two pairs of oppositely disposed emboss- -ments 35,35a; the embossments 35 extending above the plane of the flanges 34,34a and the other embossment 35a extending below the flange plane.
The pieces 32,32a have oppositely dished central portions 36,36a with generally vertical side walls 37,37a merging into the flanges 33 and converging away from the ~-~6029-LC
walls 38,38a merging into the flanges 34. The walls 37,37a converge toward walls 39,39a parallel to and opposite the wall 38. Generally conical embossments 40,40a are formed in the central portions 36,36a and merge into the embossments 35,35a to define openings for an inlet conduit 41 and an outlet conduit 42. The conical embossments 40,40a also merge into the sheets 32,32a as seen in Figure 5. Within a central chamber 43 formed by the dished portions 36,36a, is positioned a partially folded turbulizer 44 extending longi-tudinally in the chamber to divide the chamber into a plurality of parallel flow passages 45; the turbulizer terminating short of the ends of the chamber to form an entrance tank 46 and an exit tank (not shown) for the exhaust gas.
The outer pieces 47,47a also have flat flanges 48,48a ~, sandwiching the flanges 33,33a around three sides of the heat exchanger and generally flat flanges 49,49a sandwiching the flanges 34,34a on the fourth side. Conical embossments 50,50a are formed in central dished portions 52,52a defined ' by the flanges 48,48a, 49,49a with outer edges 51,51a en-gaging and secured to the embossments 35,35a. The dished portions 52,52a have side walls 53,53a converging from a rear wall 54,54a having the embossments therein and toward -forward walls 55,55a parallel to the walls 54,54a; the walls r~, being spaced outwardly of the walls of the inner dished portions 36,36a. A central indentation 56 in the dished portion 52 engages its respective inner dished portion 36 to 3i divide the upper portion of the fluid envelope 57 formed between the dished portions 36,36a, 52,52a to cause flow of the cooling fluid into the lower envelope portion.
The flanges 33 of the inner sheets 32,32a, as seen in FIGURES 5 and 6, act to divide the fluid envelope 57 into upper and lower portions; however, fluid ports or openings 58 are formed in the oppositely disposed flanges 33 at the opposite ends of the inner pieces to allow fluit communi-cation and flow between the upper and lower portions of the envelope. A cooling fluid inlet conduit 59 and a fluid outlet conduit 60 are secured in the upper piece 52 adjacent the indentation 56; the conduits communicating with the upper portion of the fluid envelope 57. As shown by the arrows in FIGURE 4, the hot exhaust gas enters the conduit 41 (arrow A) into the entrance tank 46, passes through the parallel passages 44 to the exit tank, and the cooled gas leaves through the conduit 42 (arrow B). The cooling water enters conduit 59 (arrow C) into the communicating half of the upper portion of the envelope 57 passes down through the openings 58 to the lower envelope portion, flows across the lower portion and up through the opposite set of openings 58 ~`
to the other half of the upper envelope portion and exits through the conduit 60 (arrow D) to cool the exhaust gas.
FIGURES 7, 8 and 9 disclose a third embodiment of heat exchanger 61 having a generally rectangular symmetrical con-figuration. This device includes a pair of inner metal sheets 62,62a having parallel side flanges 63 and curved end flanges 64; the sheets having oppositely dished portions 65,65a with dished end extensions 66,66a. The dished portions 65,65a form a central chamber 67 for the exhaust gases, with $029-LC llL~ 7 ~
the extensions 66,66a forming inlet and outlet chambers. An elongated opening 68 in the extension 66 forms an inlet port and an elongated opening 69 forms the outlet port in the opposite extension 66.
A pair of outer sheets 71,71a have flanges 72 engaging the flanges 63 (see FIGURE 8) and flanges 73 engaging the dished extensions 66,66a (FIGURE 9); the sheets having oppositely dished portions 74,74a cooperating with the dished portions 65,65a to provide a cooling fluid envelope around the chamber 67. As seen in FIGURE 8, the walls 75 of dished portions 65,65a are spaced inwardly of the walls 76 of dished portions 74,74a with the side flanges 63 dividing the fluid envelope into upper and lower portions 77 and 78, respectlvely, and provided with openings 79 formed therein to provide communication between these two portions. Emboss-ments 80 are preferably formed in the sheets 71,71a to extend into the cooling fluid envelope.
The sheet 71 has a fluid inlet conduit 81 formed in the dished portion 74 on one side of a central depression 82 and a fluid outlet conduit 83 adjacent the opposite side of the depression. The central transverse elongated depression 82 is formed across the dished portion 74 and extends inwardly to contact and be joined to the dished portion 65 of the upper sheet 62. This depression 82 effectively divides the upper envelope portion 77 in half to provide the desired flow pattern for the fluid.
In use, the hot exhaust gas enters the inlet port 68 in the inlet chamber and passes into the central chamber where a partially folded metal sheet 84 forms a plurality of flow _9_ 07L~29-LC l~t~ '7 7~
passages 85. The cooled gas flows into the outlet chamber and exits through the port 69. Also, the cooling fluid, such as water, enters the upper portion 77 of the envelope via the conduit 81, but is stopped from directly flowing to the outlet conduit 83 by the depression 82. Thus, fluid flows from the upper portion through the openings 79 at the end 86 to the lower envelope portion 78, across the portion 78 to the openings 79 at the end 87 and enters the upper envelope portion 77 again to exit through the outlet conduit 83. The ribs or embossments 8~ formed in the dished portions 71,71a (see FIGURE 8) act to interrupt straight flow of the fluid in the envelope and turbulize the fluid to enhance the heat transfer and reduce any channelling of the flow of the cooling fluid.
FIGURES 10 through 12 disclose another heat exchanger 91 similar to that shown in FIGURES 7 through 9 except for the positioning of the exhaust gas inlet and outlet. This heat exchanger 91 utilizes a pair of inner plates 92,92a having flanges 93 around the periphery and defining oppositely disposed dished portions 94,94a forming a central chamber 95. Outer metal sheets 96,96a have peripheral flanges 97 and oppositely dished portions 98,98a. As seen in FIGURE 11, the exhaust gas inlet 99 and the exhaust gas outlet 101 are formed through both sheets 92,96, with the sheets being crimped together to form the conduits. A partially folded metal plate 102 is positioned in the chamber 95 to divide the flow of hot gases and enhance heat transfer to the cooLing fluid in the surrounding envelope.
The spacing between the dished portions forms a fluid envelope having an upper portion 103 and a lower portion . -10-~ 1 V'~ 78 104. An elongated central depression or rib 105 is formed in the sheet 96 and engages the inner sheet 92 to divide the upper envelope portion 103 to two compartments; a fluid inlet conduit 106 in sheet 96 communicates with the compart-ment on one side of the rib 105 and the fluid outlet conduit 107 communicates with the opposite compartment. A plurality of openings 108 are formed in the flanges 93 between the spaced walls of the dished portions 92,92a and 98,98a adjacent the conduit 106 and a second set of openings 109 are formed in the flanges 93 adjacent the outlet conduit 107. The flow of hot exhaust gas and cooling water takes substantially the same paths as for the heat exchanger 61.
FIGURES 13 through 16 disclose a fifth embodiment of heat exchanger 111 which differs from those previously shown in utilizing a plurality of generally elliptical perforated disks or plates 112 which are stacked together to form the heat exchanger. Each plate 112 is stamped to form a peri-pheral flange 113, a gas inlet opening 114 defined by a flange 115, a gas outlet opening 116 defined by a flange 117 and several elongated narrow openings 118 defined by flanges 119. All of the flanges 113, 115, 117 and 119 project from one surface 121 of the plate 112, and all of the plates are similarly oriented so that the flanges of one plate abut the unflanged surface 122 of the next adjacent plate. Each respective set of openings and flanges are axially aligned to form a continuous passage through the plates.
Each plate 112 may be imperforate but preferably has a series of slits or louvres 123 formed therein between the openings 114 and 116 to enhance the heat transfer from the ~ 7~
hot exhaust gas to the cooling water. The front end plate 112a includes the gas inlet and outlet openings 114,116 and the narrow openings 118, but without the slits, and the rear end plate 112b is similar to the plate 112a except there are no flanges or gas inlet and outlet openings. Also each flange 115,117 has one or more openings 124,125, respectively, formed therein, to allow the exhaust gases to pass transversely across and between the plates. A domed end cap 126 is secured to the front end plate 112a and has an inlet conduit 127 defined by a flange 128 and an outlet conduit 129 defined by a flange 131; the flanges 128,131 being aligned with ~he openings 114 and 116, respectively, and secured to the plate 112a. A cooling fluid inlet conduit 132 is also formed in --the end cap 126 and communicates with a chamber 133 therein to distribute fluid to the openings 118. A second domed end cap 134 is secured to the end plate 112b and defines a chamber 135 collecting fluid from the openings 118 for egress through a fluid outlet conduit 136.
To assemble, the plates 112j112a,112b and the end caps 126 and 134 are stacked in a suitable jig with the flanges of one plate abutting the surface 122 of the next ad;acent plate and the plates and end caps are suitably joined together, such as by brazing or soldering. The peripheral flanges 113 on the plates provide an outer shell for the heat exchanger so that it is self-contained. In use, the cooling water enters the conduit 132 and passes through the chamber to the passages 118 (arrow L) formed by the flanges ;
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lU~ ' 7~3 119 at one end of the heat exchanger and exits from the opposite end into the chamber 135 and through the conduit 136. The hot exhaust gas, however, enters the inlet conduit 127 and into the passage formed by the flanges 115 (arrow M) and fills the passage. The gas passes through the openings 124 in the flanges 115 to flow between the plates 112 and passes through the openings 125 of flanges 117 to exit from the passage (arrow N) formed by the flanges 117 and from the heat exchanger through the conduit 129. The gas gives up heat to the plates 112, with the slits or lou~res 123 enhancing heat transfer; ~he heat being transferred to the cooling water within the passages formed by flanges 119.
Obviously, in the embodiments of Figures 4-6, 7-9 and 10-12, the water connections would be positioned in the outer envelope to provide the most effective distribution and circulation of the cooling fluid; and the folded metal sheet in the inner chamber acts to break up the hot gas flow into smaller streams to effectively maximize the heat trans-fer from the exhaust gas to the cooling fluid in the envelope.
Also, the flow of cooling fluid can be either concurrent or counter current to the gas flow, with the cooling fluid jacket shielding a very localized but high temperature zone.
Although several embodiments and flow patterns have been shown and described by way of illustration, it is not our intent or desire to unnecessarily restrict the improvement by virtue of this limited showing.
cooling fluid around a generally central gas flow p~ssa~e to reduce as far as possible the escape of heat to adjacent areas around the heat exchanger. The heat exchanger may also provide a central gas flow passage having a dead or inner tube extending axially in the center of the passage to effectively force the hot gases outwardly into contact with extended fin surfaces to enhance the heat transfer to the outer cooling water envelope.
The present invention further comprehends the provision of an exhaust gas heat exchanger which provides for adequate gas flow therethrough with low resistance or pressure drop. Although primarily utilized for exhaust gas recirculation systems, the same heat exchanger could be used to extract heat from the other exhaust gas flow and for other purposes, such as a fast passenger compartment heat-up system or for a gas turbine heat exchange system. The heat exchanger is formed of suitable materials to resist corrosion and decay in the highly corrosive exhaust gas environment.
Various embodiments of heat exchangers incorporating the aforementioned concepts of the present invention are disclosed i herein. The embodiment claimed herein is defined as a two fluid heat exchanger comprising a generally flat heat exchanger formed of two pairs of metal plates, the inner pair of plates having oppositely disposed dished portions forming a chamber and joined by peripheral flanges, the chamber having an inlet and an outlet adapted to receive a first fluid, a heat transfer surface formed of at least one metal plate received in the chamber, and the outer pair of plates having oppositely disposed dished portions and peripheral flanges generally completely joined to the flanges of the inner plates, the outer dished portions cooperating with the inner dished portions to form a fluid envelope generally encompassing the chamber and having an inlet and an outlet to .~ .~ ., .
ob/t' - lV~ 7~
receive a second fluid therein~ at least an oppositely disposed pair of side walls of the outer dished p~rtions are spaced from side walls of the inner dished portions, the flanges of the inner plates extend between the inner and outer side walls to divide the envelope into upper and lower portions and have openings therein to provide communication between the upper and lower envelope portions, the second fluid inlet and outlet being located in one of the outer dished portions, and a central depression is formed in the same dished portion to extend across the dished portion and divide the upper envelope portion between the inlet and outlet into generally equal halves.
In the accompanying drawings:
Figure 1 is a perspective view, partially broken away, of one form of exhaust gas heat exchanger.
Figure 2 is a side elevational view, partially broken ,' away, of the left-hand end of the heat exchanger of Figure 1.
Figure 3 is a vertical cross sectional view of the heat exchanger taken on the line 3-3 of Figure 2.
Figure 4 is a perspective view of a second embodiment of heat exchanger.
- 3a -ob~
0- ~29-LC ~ V~ 7~
FIGURE 5 is a vertical cross sectional view taken on the line 5-5 of FIGURE 4.
FIGURE 6 is a partial vertical cross sectional view taken on the irregular line 6-6 of FIGURE 4.
FIGURE 7 is a top plan view of a third embodiment of heat exchanger.
FIGURE 8 is a vertical cross sectional view taken on the line 8-8 of FIGURE 7.
FIGU~E 9 is a partial vertical cross sectional view taken on the line 9-9 of FIGURE 7.
FIGURE 10 is a top plan view of a fourth embodiment of heat exchanger.
FIGURE 11 is a vertical cross sectional view taken on the line 11-11 of FIGURE 10.
FIGURE 12 is a partial vertical cross sectional view taken on the line 12-12 of FIGURE 10.
FIGURE 13 is a perspective view of a fifth embodiment of heat exchanger with the ends omitted.
FIGURE 14 is a top plan view of the heat exchanger of FIGURE 13 including the end pieces and with the front and rear portions broken away.
FIGURE 15 is a vertical cross sectional view taken on the line 15-15 of FIGURE 14.
FIGURE 16 is a vertical cross sectional view of a heat exchanger plate taken on the line 16-16 of FIGURE 15.
Referring to the drawings an exhaust gas heat exchanger 10 for use in the exhaust gas recirculation line of an automotive internal combustion engine is provided which includes an outer cylindrical tube 11 and an inner cylindrical ~ `~29-LC
tube 12 forming an annular envelope 13 therebetween for cooling fluid admitted through an inlet conduit 14 and exiting through an outlet conduit 15. The inner and outer tubes 12 and 11 are crimped and secured together at the opposite ends to seal the fluid envelope 13 (FIGURE 2). The housing 11 is closed at the opposite ends by end plates 16 and 17, with an exhaust gas inlet conduit 18 being secured in one plate and an exhaust gas outlet conduit 19 centrally secured in the opposite plate, so that the heat exchanger may provide concurrent or counter current flow heat transfer.
Within the inner tube 12, a dead tube 21 is centrally positioned by an extended fin surface 23; the dead tube comprising a hollow tube closed at each end 22 by a rounded surface to effectively force the hot gases outwardly into the extended fin surface 23. The fin surface is preferably formed of a single sheet of material having a high heat conductivity and formed into a generally corrugated member of a sinusoidal configuration around the dead tube 21 with the peaks 24 contacting and suitably joined to the inner wall 12 and the inner apices 25 contacting and suitably joined to the dead tube 21; joining being by brazing or soldering. The fin surface 23 may be imperforate or may i contain a plurality of slits or louvres to enhance the heat transfer and to act as a turbulizer for the gas flow in the i passages formed by the fin surface.
This heat exchanger 10 provides a compact cylindrical design which will easily fit within the limited space requirements found in an automobile engine compartment and ~ t'~7~
has a double-walled passage or envelope 13 for a cooling fluid 26 which not only provides an efficient heat transfer from the hot exhaust gases but also provides insulation of the exhaust gas temperatures from the engine compartment to reduce the escape of heat therefrom into the hot engine compartment. The heat exchanger will rapidly cool the exhaust gases from a temperature of approximately 1250F. to a level of approximately 550F. and provides for adequate gas flow with low resistance or pressure drop. The material selected for the heat exchanger should provide high re-sistance to corrosion and decay from the corrosive exhaust gas environment; with a preferred material being a stainless steel, such as type 304 stainless steel.
FIGURES 4 through 6 disclose an alternate embodiment of heat exchanger 31 having a generally flat configuration which will easily and compactly fit alongside the vehicle engine in the limited space of the engine compartment. This heat exchanger is formed from four stamped pieces of sheet metal comprising a pair of symmetrical inner sheets 32,32a and a pair of generally identical outer pieces 47,47a; the inner pieces having flat flanges 33,33a around three sides of the unit and generally flat flanges 34,34a on the fourth side provided with two pairs of oppositely disposed emboss- -ments 35,35a; the embossments 35 extending above the plane of the flanges 34,34a and the other embossment 35a extending below the flange plane.
The pieces 32,32a have oppositely dished central portions 36,36a with generally vertical side walls 37,37a merging into the flanges 33 and converging away from the ~-~6029-LC
walls 38,38a merging into the flanges 34. The walls 37,37a converge toward walls 39,39a parallel to and opposite the wall 38. Generally conical embossments 40,40a are formed in the central portions 36,36a and merge into the embossments 35,35a to define openings for an inlet conduit 41 and an outlet conduit 42. The conical embossments 40,40a also merge into the sheets 32,32a as seen in Figure 5. Within a central chamber 43 formed by the dished portions 36,36a, is positioned a partially folded turbulizer 44 extending longi-tudinally in the chamber to divide the chamber into a plurality of parallel flow passages 45; the turbulizer terminating short of the ends of the chamber to form an entrance tank 46 and an exit tank (not shown) for the exhaust gas.
The outer pieces 47,47a also have flat flanges 48,48a ~, sandwiching the flanges 33,33a around three sides of the heat exchanger and generally flat flanges 49,49a sandwiching the flanges 34,34a on the fourth side. Conical embossments 50,50a are formed in central dished portions 52,52a defined ' by the flanges 48,48a, 49,49a with outer edges 51,51a en-gaging and secured to the embossments 35,35a. The dished portions 52,52a have side walls 53,53a converging from a rear wall 54,54a having the embossments therein and toward -forward walls 55,55a parallel to the walls 54,54a; the walls r~, being spaced outwardly of the walls of the inner dished portions 36,36a. A central indentation 56 in the dished portion 52 engages its respective inner dished portion 36 to 3i divide the upper portion of the fluid envelope 57 formed between the dished portions 36,36a, 52,52a to cause flow of the cooling fluid into the lower envelope portion.
The flanges 33 of the inner sheets 32,32a, as seen in FIGURES 5 and 6, act to divide the fluid envelope 57 into upper and lower portions; however, fluid ports or openings 58 are formed in the oppositely disposed flanges 33 at the opposite ends of the inner pieces to allow fluit communi-cation and flow between the upper and lower portions of the envelope. A cooling fluid inlet conduit 59 and a fluid outlet conduit 60 are secured in the upper piece 52 adjacent the indentation 56; the conduits communicating with the upper portion of the fluid envelope 57. As shown by the arrows in FIGURE 4, the hot exhaust gas enters the conduit 41 (arrow A) into the entrance tank 46, passes through the parallel passages 44 to the exit tank, and the cooled gas leaves through the conduit 42 (arrow B). The cooling water enters conduit 59 (arrow C) into the communicating half of the upper portion of the envelope 57 passes down through the openings 58 to the lower envelope portion, flows across the lower portion and up through the opposite set of openings 58 ~`
to the other half of the upper envelope portion and exits through the conduit 60 (arrow D) to cool the exhaust gas.
FIGURES 7, 8 and 9 disclose a third embodiment of heat exchanger 61 having a generally rectangular symmetrical con-figuration. This device includes a pair of inner metal sheets 62,62a having parallel side flanges 63 and curved end flanges 64; the sheets having oppositely dished portions 65,65a with dished end extensions 66,66a. The dished portions 65,65a form a central chamber 67 for the exhaust gases, with $029-LC llL~ 7 ~
the extensions 66,66a forming inlet and outlet chambers. An elongated opening 68 in the extension 66 forms an inlet port and an elongated opening 69 forms the outlet port in the opposite extension 66.
A pair of outer sheets 71,71a have flanges 72 engaging the flanges 63 (see FIGURE 8) and flanges 73 engaging the dished extensions 66,66a (FIGURE 9); the sheets having oppositely dished portions 74,74a cooperating with the dished portions 65,65a to provide a cooling fluid envelope around the chamber 67. As seen in FIGURE 8, the walls 75 of dished portions 65,65a are spaced inwardly of the walls 76 of dished portions 74,74a with the side flanges 63 dividing the fluid envelope into upper and lower portions 77 and 78, respectlvely, and provided with openings 79 formed therein to provide communication between these two portions. Emboss-ments 80 are preferably formed in the sheets 71,71a to extend into the cooling fluid envelope.
The sheet 71 has a fluid inlet conduit 81 formed in the dished portion 74 on one side of a central depression 82 and a fluid outlet conduit 83 adjacent the opposite side of the depression. The central transverse elongated depression 82 is formed across the dished portion 74 and extends inwardly to contact and be joined to the dished portion 65 of the upper sheet 62. This depression 82 effectively divides the upper envelope portion 77 in half to provide the desired flow pattern for the fluid.
In use, the hot exhaust gas enters the inlet port 68 in the inlet chamber and passes into the central chamber where a partially folded metal sheet 84 forms a plurality of flow _9_ 07L~29-LC l~t~ '7 7~
passages 85. The cooled gas flows into the outlet chamber and exits through the port 69. Also, the cooling fluid, such as water, enters the upper portion 77 of the envelope via the conduit 81, but is stopped from directly flowing to the outlet conduit 83 by the depression 82. Thus, fluid flows from the upper portion through the openings 79 at the end 86 to the lower envelope portion 78, across the portion 78 to the openings 79 at the end 87 and enters the upper envelope portion 77 again to exit through the outlet conduit 83. The ribs or embossments 8~ formed in the dished portions 71,71a (see FIGURE 8) act to interrupt straight flow of the fluid in the envelope and turbulize the fluid to enhance the heat transfer and reduce any channelling of the flow of the cooling fluid.
FIGURES 10 through 12 disclose another heat exchanger 91 similar to that shown in FIGURES 7 through 9 except for the positioning of the exhaust gas inlet and outlet. This heat exchanger 91 utilizes a pair of inner plates 92,92a having flanges 93 around the periphery and defining oppositely disposed dished portions 94,94a forming a central chamber 95. Outer metal sheets 96,96a have peripheral flanges 97 and oppositely dished portions 98,98a. As seen in FIGURE 11, the exhaust gas inlet 99 and the exhaust gas outlet 101 are formed through both sheets 92,96, with the sheets being crimped together to form the conduits. A partially folded metal plate 102 is positioned in the chamber 95 to divide the flow of hot gases and enhance heat transfer to the cooLing fluid in the surrounding envelope.
The spacing between the dished portions forms a fluid envelope having an upper portion 103 and a lower portion . -10-~ 1 V'~ 78 104. An elongated central depression or rib 105 is formed in the sheet 96 and engages the inner sheet 92 to divide the upper envelope portion 103 to two compartments; a fluid inlet conduit 106 in sheet 96 communicates with the compart-ment on one side of the rib 105 and the fluid outlet conduit 107 communicates with the opposite compartment. A plurality of openings 108 are formed in the flanges 93 between the spaced walls of the dished portions 92,92a and 98,98a adjacent the conduit 106 and a second set of openings 109 are formed in the flanges 93 adjacent the outlet conduit 107. The flow of hot exhaust gas and cooling water takes substantially the same paths as for the heat exchanger 61.
FIGURES 13 through 16 disclose a fifth embodiment of heat exchanger 111 which differs from those previously shown in utilizing a plurality of generally elliptical perforated disks or plates 112 which are stacked together to form the heat exchanger. Each plate 112 is stamped to form a peri-pheral flange 113, a gas inlet opening 114 defined by a flange 115, a gas outlet opening 116 defined by a flange 117 and several elongated narrow openings 118 defined by flanges 119. All of the flanges 113, 115, 117 and 119 project from one surface 121 of the plate 112, and all of the plates are similarly oriented so that the flanges of one plate abut the unflanged surface 122 of the next adjacent plate. Each respective set of openings and flanges are axially aligned to form a continuous passage through the plates.
Each plate 112 may be imperforate but preferably has a series of slits or louvres 123 formed therein between the openings 114 and 116 to enhance the heat transfer from the ~ 7~
hot exhaust gas to the cooling water. The front end plate 112a includes the gas inlet and outlet openings 114,116 and the narrow openings 118, but without the slits, and the rear end plate 112b is similar to the plate 112a except there are no flanges or gas inlet and outlet openings. Also each flange 115,117 has one or more openings 124,125, respectively, formed therein, to allow the exhaust gases to pass transversely across and between the plates. A domed end cap 126 is secured to the front end plate 112a and has an inlet conduit 127 defined by a flange 128 and an outlet conduit 129 defined by a flange 131; the flanges 128,131 being aligned with ~he openings 114 and 116, respectively, and secured to the plate 112a. A cooling fluid inlet conduit 132 is also formed in --the end cap 126 and communicates with a chamber 133 therein to distribute fluid to the openings 118. A second domed end cap 134 is secured to the end plate 112b and defines a chamber 135 collecting fluid from the openings 118 for egress through a fluid outlet conduit 136.
To assemble, the plates 112j112a,112b and the end caps 126 and 134 are stacked in a suitable jig with the flanges of one plate abutting the surface 122 of the next ad;acent plate and the plates and end caps are suitably joined together, such as by brazing or soldering. The peripheral flanges 113 on the plates provide an outer shell for the heat exchanger so that it is self-contained. In use, the cooling water enters the conduit 132 and passes through the chamber to the passages 118 (arrow L) formed by the flanges ;
07602~-LC
lU~ ' 7~3 119 at one end of the heat exchanger and exits from the opposite end into the chamber 135 and through the conduit 136. The hot exhaust gas, however, enters the inlet conduit 127 and into the passage formed by the flanges 115 (arrow M) and fills the passage. The gas passes through the openings 124 in the flanges 115 to flow between the plates 112 and passes through the openings 125 of flanges 117 to exit from the passage (arrow N) formed by the flanges 117 and from the heat exchanger through the conduit 129. The gas gives up heat to the plates 112, with the slits or lou~res 123 enhancing heat transfer; ~he heat being transferred to the cooling water within the passages formed by flanges 119.
Obviously, in the embodiments of Figures 4-6, 7-9 and 10-12, the water connections would be positioned in the outer envelope to provide the most effective distribution and circulation of the cooling fluid; and the folded metal sheet in the inner chamber acts to break up the hot gas flow into smaller streams to effectively maximize the heat trans-fer from the exhaust gas to the cooling fluid in the envelope.
Also, the flow of cooling fluid can be either concurrent or counter current to the gas flow, with the cooling fluid jacket shielding a very localized but high temperature zone.
Although several embodiments and flow patterns have been shown and described by way of illustration, it is not our intent or desire to unnecessarily restrict the improvement by virtue of this limited showing.
Claims (9)
1. A two fluid heat exchanger comprising a generally flat heat exchanger formed of two pairs of metal plates, the inner pair of plates having oppositely disposed dished portions forming a chamber and joined by peripheral flanges, the chamber having an inlet and an outlet adapted to receive a first fluid, a heat transfer surface formed of at least one metal plate received in said chamber, and the outer pair of plates having oppositely disposed dished portions and peripheral flanges generally completely joined to the flanges of said inner plates, said outer dished portions cooperating with said inner dished portions to form a fluid envelope generally encompassing the chamber and having an inlet and an outlet to receive a second fluid therein, at least an oppositely disposed pair of side walls of said outer dished portions are spaced from side walls of said inner dished portions, said flanges of the inner plates extend between said inner and outer side walls to divide said envelope into upper and lower portions and have openings therein to provide communication between said upper and lower envelope portions, said second fluid inlet and outlet being located in one of the outer dished portions, and a central depression is formed in the same dished portion to extend across the dished portion and divide said upper envelope portion between the inlet and outlet into generally equal halves.
2. A two fluid heat exchanger as set forth in Claim 1, in which the flow of the second fluid enters the inlet and corresponding upper envelope portion half, passes through the openings in the inner flanges adjacent the inlet, passes through the lower envelope portion to the openings in the inner flanges at the opposite side of the heat exchanger, enters the opposite upper envelope portion half and exits through the outlet.
3. A two fluid heat exchanger as set forth in Claim 1, in which said first fluid inlet and outlet are positioned in one pair of aligned side walls of the inner and outer dished portions adjacent the opposite ends of the heat exchanger, said inner and outer flanges on the side of the heat exchanger receiving said first fluid inlet and outlet are embossed around the inlet and the outlet, and said chamber has an inlet portion and an outlet portion aligned with said first fluid inlet and outlet, and said partially folded metal sheet extends longitudinally between said inlet and outlet chamber portions.
4. A two fluid heat exchanger as set forth in Claim 3, wherein said embossments in said inner and outer flanges merge into said inner and outer dished portions, respectively.
5. A two fluid heat exchanger as set forth in Claim 1, wherein said inner dished portions are provided with oppositely disposed dished extensions projecting beyond the outer flanges, and said first fluid inlet and outlet are located in said extensions.
6. A two fluid heat exchanger as set forth in Claim 5, wherein said inner dished extensions are located on two parallel sides, and the two outer dished portions extend beyond the inner dished portions on the opposite two parallel sides.
7. A two fluid heat exchanger as set forth in Claim 6, in which said first fluid flow in said central chamber is generally transverse to the flow of said second fluid in said outer envelope.
8. A two fluid heat exchanger as set forth in Claim 7, including a plurality of flow diverting ribs formed on said outer dished portions and extending into said fluid envelope portions.
9. A two fluid heat exchanger as set forth in Claim 1, in which said second fluid inlet and outlet are centrally located in one outer dished portion adjacent the central depression, and said first fluid inlet and outlet are centrally located in said same outer dished portion and extending through said inner dished portion at the opposite ends of the central depression, said gas inlet and outlet each being defined by flared portions of said adjacent inner and outer dished portions which are crimped together.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA341,705A CA1104555A (en) | 1976-08-23 | 1979-12-12 | Exhaust gas heat exchanger |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US71662876A | 1976-08-23 | 1976-08-23 | |
| US716,628 | 1976-08-23 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1090778A true CA1090778A (en) | 1980-12-02 |
Family
ID=24878784
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA284,385A Expired CA1090778A (en) | 1976-08-23 | 1977-08-09 | Exhaust gas heat exchanger |
Country Status (7)
| Country | Link |
|---|---|
| JP (2) | JPS5325717A (en) |
| AU (1) | AU518454B2 (en) |
| CA (1) | CA1090778A (en) |
| DE (2) | DE2759785C2 (en) |
| FR (1) | FR2363073A1 (en) |
| GB (2) | GB1579275A (en) |
| SE (2) | SE429675B (en) |
Families Citing this family (19)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4258687A (en) * | 1979-10-09 | 1981-03-31 | Ford Motor Company | Engine with integral mounted EGR cooler |
| US4267812A (en) * | 1979-10-09 | 1981-05-19 | Ford Motor Company | Engine EGR cooler |
| JPS5763123U (en) * | 1980-09-30 | 1982-04-15 | ||
| JPS59199598A (en) * | 1983-04-26 | 1984-11-12 | Kyushu Denshi Kinzoku Kk | Apparatus for crystal growth |
| EP0563951B1 (en) * | 1992-04-02 | 1999-02-17 | Denso Corporation | A heat exchanger |
| JP2558019Y2 (en) * | 1992-09-24 | 1997-12-17 | カルソニック株式会社 | Oil cooler |
| IT1263611B (en) * | 1993-02-19 | 1996-08-27 | Giannoni Srl | PLATE HEAT EXCHANGER |
| JPH07174474A (en) * | 1993-07-26 | 1995-07-14 | Kimura Kohki Co Ltd | Sensible heat exchanger and heat transfer plate thereof |
| EP0840081B1 (en) * | 1996-10-29 | 2003-04-16 | Denso Corporation | Heat exchanger and method for manufacturing the same |
| AT411546B (en) * | 1998-01-15 | 2004-02-25 | Man Steyr Ag | LIQUID-COOLED INTERNAL COMBUSTION ENGINE WITH EXHAUST GAS RECIRCULATING DEVICE AND DEVICE FOR COOLING RECYCLED EXHAUST |
| DE19809859A1 (en) * | 1998-03-07 | 1999-09-09 | Mann & Hummel Filter | Device for cooling gases |
| FR2778947B1 (en) * | 1998-05-20 | 2000-09-22 | Valeo Thermique Moteur Sa | HEAT EXCHANGER FOR RECYCLED EXHAUST GASES FROM INTERNAL COMBUSTION ENGINES |
| JP2002054511A (en) * | 2000-08-14 | 2002-02-20 | Hino Motors Ltd | Egr cooler |
| US8241140B2 (en) | 2001-07-05 | 2012-08-14 | Bridgestone Sports Co., Ltd. | Golf club head |
| DE102005058204B4 (en) * | 2005-12-02 | 2008-07-24 | Pierburg Gmbh | Cooling device for an internal combustion engine |
| ES2331218B1 (en) | 2007-07-27 | 2010-09-29 | Valeo Termico, S.A. | HEAT EXCHANGER FOR GASES, ESPECIALLY OF EXHAUST GASES OF AN ENGINE. |
| AT507422B1 (en) * | 2008-10-20 | 2010-05-15 | Ebner Ind Ofenbau | HEAT EXCHANGER FOR A HEAT EXCHANGER FOR HEAT EXCHANGE BETWEEN TWO FLUIDS |
| JP6798762B2 (en) * | 2017-06-06 | 2020-12-09 | 株式会社前川製作所 | Refrigerant heat exchanger |
| JP6796906B2 (en) * | 2017-06-06 | 2020-12-09 | 株式会社前川製作所 | Refrigerant heat exchanger and secondary refrigerant refrigeration system equipped with this |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DD55046A (en) * | ||||
| US1342869A (en) * | 1919-11-11 | 1920-06-08 | Ricardo Harry Ralph | Means for heating the charges in internal-combustion engines |
| DE839806C (en) * | 1949-08-02 | 1952-05-26 | Otto H Dr-Ing E H Hartmann | Star-shaped folded tube as an insert tube for heat exchangers |
| US2952445A (en) * | 1958-06-25 | 1960-09-13 | United Aircraft Prod | Damage resistant plate type heat exchanger |
| FR95666E (en) * | 1966-01-22 | 1971-04-16 | Snecma | Improvements to plate heat exchangers. |
| JPS5138462B2 (en) * | 1972-06-20 | 1976-10-21 | ||
| PL84062B1 (en) * | 1972-07-13 | 1976-02-28 | Przedsiebiorstwo Doswiadczalnepo |
-
1977
- 1977-06-22 GB GB26182/77A patent/GB1579275A/en not_active Expired
- 1977-06-22 GB GB13656/79A patent/GB1579276A/en not_active Expired
- 1977-06-29 AU AU26556/77A patent/AU518454B2/en not_active Expired
- 1977-07-22 DE DE2759785A patent/DE2759785C2/en not_active Expired
- 1977-07-22 DE DE2733215A patent/DE2733215C3/en not_active Expired
- 1977-07-28 SE SE7708696A patent/SE429675B/en unknown
- 1977-08-09 CA CA284,385A patent/CA1090778A/en not_active Expired
- 1977-08-11 JP JP9655377A patent/JPS5325717A/en active Granted
- 1977-08-18 FR FR7725292A patent/FR2363073A1/en active Granted
-
1983
- 1983-06-13 SE SE8303353A patent/SE8303353D0/en not_active Application Discontinuation
-
1985
- 1985-08-09 JP JP60175638A patent/JPS6183881A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| GB1579276A (en) | 1980-11-19 |
| DE2759785C2 (en) | 1985-04-04 |
| DE2733215B2 (en) | 1980-10-23 |
| DE2733215A1 (en) | 1978-03-09 |
| AU518454B2 (en) | 1981-10-01 |
| FR2363073A1 (en) | 1978-03-24 |
| JPS6133972B2 (en) | 1986-08-05 |
| FR2363073B1 (en) | 1982-06-11 |
| SE7708696L (en) | 1978-02-24 |
| SE429675B (en) | 1983-09-19 |
| JPS6183881A (en) | 1986-04-28 |
| JPS5325717A (en) | 1978-03-09 |
| AU2655677A (en) | 1979-01-04 |
| DE2733215C3 (en) | 1981-06-25 |
| SE8303353L (en) | 1983-06-13 |
| GB1579275A (en) | 1980-11-19 |
| SE8303353D0 (en) | 1983-06-13 |
| JPS6223236B2 (en) | 1987-05-21 |
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Legal Events
| Date | Code | Title | Description |
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| MKEX | Expiry |