CA2590569A1 - Heat exchanger - Google Patents
Heat exchanger Download PDFInfo
- Publication number
- CA2590569A1 CA2590569A1 CA002590569A CA2590569A CA2590569A1 CA 2590569 A1 CA2590569 A1 CA 2590569A1 CA 002590569 A CA002590569 A CA 002590569A CA 2590569 A CA2590569 A CA 2590569A CA 2590569 A1 CA2590569 A1 CA 2590569A1
- Authority
- CA
- Canada
- Prior art keywords
- heat exchanger
- inner tube
- outlet
- spiral line
- 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
- 239000002826 coolant Substances 0.000 claims abstract description 35
- 239000007789 gas Substances 0.000 claims description 32
- 238000001816 cooling Methods 0.000 claims description 20
- 238000002485 combustion reaction Methods 0.000 claims description 13
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 claims description 3
- 229910052802 copper Inorganic materials 0.000 claims description 3
- 239000010949 copper Substances 0.000 claims description 3
- 239000000463 material Substances 0.000 claims description 3
- 238000004804 winding Methods 0.000 abstract description 6
- 230000007704 transition Effects 0.000 abstract 1
- 238000010438 heat treatment Methods 0.000 description 8
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 7
- 239000007788 liquid Substances 0.000 description 4
- IJDNQMDRQITEOD-UHFFFAOYSA-N n-butane Chemical compound CCCC IJDNQMDRQITEOD-UHFFFAOYSA-N 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 230000003197 catalytic effect Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 238000000746 purification Methods 0.000 description 2
- 230000003584 silencer Effects 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 239000000470 constituent Substances 0.000 description 1
- 239000003344 environmental pollutant Substances 0.000 description 1
- 230000005012 migration Effects 0.000 description 1
- 238000013508 migration Methods 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 231100000719 pollutant Toxicity 0.000 description 1
- 230000008092 positive effect Effects 0.000 description 1
- 229910052709 silver Inorganic materials 0.000 description 1
- 239000004332 silver Substances 0.000 description 1
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
- F28D7/02—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 helically coiled
-
- 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
- F28D7/02—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 helically coiled
- F28D7/024—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 helically coiled the conduits of only one medium being helically coiled tubes, the coils having a cylindrical configuration
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Separation By Low-Temperature Treatments (AREA)
- Power Steering Mechanism (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The invention relates to a heat exchanger for transferring heat between two media, comprising: a jacket tube (8) that has an inlet (1) and an outlet (2) for a medium to be cooled; an inner tube (3), which is situated inside the jacket tube (8), is closed on the side facing the inlet (1), is joined to a coolant inlet (5) on the side facing the outlet (2), and has a coolant outlet.
This coolant outlet leads to the side facing the outlet (2) of the inner tube (3) and transitions into a spiral line (7) which, from the side facing the outlet, extends toward the inlet (1) while winding around the inner tube (3) and, in the end, leads into a coolant discharge (10).
This coolant outlet leads to the side facing the outlet (2) of the inner tube (3) and transitions into a spiral line (7) which, from the side facing the outlet, extends toward the inlet (1) while winding around the inner tube (3) and, in the end, leads into a coolant discharge (10).
Description
Heat exchanger The invention relates to a heat exchanger for transferring heat between two separate media.
Heat exchangers are often used in technology in order to provide a transfer of heat between two media. Media which are to be treated are either warmed or cooled using heat exchangers in this way.
One field of use for heat exchangers is cooling hot gases. For example, in the field of internal combustion engines, exhaust gases at temperatures of 1000 C and more are discharged from the combustion chambers. In some cases, it is desirable to cool said hot gases to temperatures of 50 C and less. Heat exchangers are typically used here. In certain situations in which space is restricted or else in which it is necessary for other reasons to provide the exchange of heat over as short a path as possible, heat exchangers of smaller or shorter design are desirable.
No heat exchangers are known from the prior art which are particularly suitable for generating a high temperature gradient over an extremely short distance (for example cooling hot gases from an inlet temperature of 1000 C and more to an outlet temperature of below 80 C, preferably below 50 C, over an installation length of approximately 30 cm).
It is therefore an object of the invention to specify a heat exchanger which, with a compact design, makes it possible to obtain a high heat transfer efficiency.
Said object is achieved with a heat exchanger having the features of claim 1. Further advantageous design embodiments of the heat exchanger are specified in claims 2 to 7. Claim 8 specifies a preferred use of the heat exchanger according to the invention, which however does not constitute the only possible use.
The heat exchanger according to the invention is characterized by an inner tube which is situated within a casing tube and which is closed off at one side. The closed-off end of the inner tube is situated at the inlet side of the casing tube, into which flow for example hot gases or other hot media to be cooled. A coolant is initially guided into the inner tube and cools the medium to be cooled, which is flowing past, both on the closed-off end side and on the tube wall. From the inner tube, the cooling medium then passes into a spiral line which is wound around the inner tube, and also leads there to a further cooling action before leaving the heat exchanger.
This firstly results in a considerably increased contact surface in relation to conventional heat exchangers at which contact takes place, separated by means of the walls of the inner tube or of the spiral line, between the cooling medium and the medium to be cooled. In addition, this design embodiment, in which the medium to be cooled initially flows against the single-sidedly closed-off end of the inner tube and then flows laterally past the inner tube along the wound spiral lines, causes turbulence of the medium to be cooled, with said medium also partially running counter to the actual main flow in vortices. This results in a particularly long residence time or a long migration path of the medium to be cooled in the heat exchanger, such that, over a short installation extent of the heat exchanger, intimate contact is generated between the medium to be cooled and the elements, the inner tube and the spiral line, which are to be traversed by the medium. This fact finally has the result that considerable cooling can be obtained over a short longitudinal extent of the heat exchanger.
The heat exchanger according to the invention is of course however also conversely suitable for heating a cool medium, which flows into the casing tube, by means of a heating medium flowing into the "coolant" inflow. In this respect, the terms "coolant inlet", "coolant outlet" and "coolant outflow" are not to be interpreted to be restricted to a coolant, but can likewise be used for a medium which is used for heating a medium flowing through the casing tube, consequently a "heating medium".
An outlet tube which, according to claim 2, is to be provided in the interior of the inner tube has the advantage that the coolant flowing into the inner tube must be distributed in the entire inner tube before it can pass into the spiral line through the outlet tube. The cooling action obtained at the wall of the inner tube is intensified in this way, which leads to an overall better cooling capacity or heat transfer capacity of the heat exchanger. Similar considerations of course apply to operation of the heat exchanger for heating a medium.
The formation of the closed-off side of the inner tube as an impact plate leads to a first generation of turbulence of the inflowing medium taking place already at said geometry, which turbulence contributes overall to the long residence time of the inflowing medium in the heat exchanger and to the thereby obtained high heat exchanger efficiency of the heat exchanger.
The refinement as per claim 4, that the spiral line is guided at least along the entire length of the inner tube so as to surround the latter, likewise contributes to a high heat exchanger efficiency. The individual windings of the spiral line are preferably wound tightly but without coming into contact. A spacing must remain between the individual windings of the spiral line in order that there can also be contact there between the medium to be cooled or to be heated and the surface of the spiral line which is traversed by the coolant or heating medium.
A design as specified in claim 5, wherein the spiral line is arranged with a radial spacing to the wall of the inner tube and to the wall of the casing tube, assists the desired turbulence of the medium flowing through the casing tube, and the associated increased heat transfer efficiency.
It has been proven here that a radial spacing of the spiral line to the wall of the inner tube which is approximately identical to the radial spacing of the spiral line to the wall of the casing tube provides particularly good results (claim 6).
According to claim 7, it is finally advantageous if at least the spiral line of the heat exchanger is composed of a material with good heat conducting properties. Here, copper is preferably used, though other materials with good heat conducting properties are also conceivable, such as for example silver.
The heat exchanger according to the invention is preferably used to cool combustion exhaust gases from internal combustion engines, in particular combustion exhaust gases from motor vehicle engines. Specifically in motor vehicle engines or in the exhaust system of motor vehicle engines, a heat exchanger of said type must on the one hand provide a high cooling capacity in order to cool the hot exhaust gases, which exit the combustion chamber at approximately 1000 C and more, to a temperature of 80 C and less, preferably below 50 C. The heat exchanger must however also be of compact design since the space in the exhaust system of the motor vehicle is restricted. The heat exchanger according to the invention is particularly suitable here.
Further advantages and features of the heat exchanger according to the invention can be gathered from the following description on the basis of the appended figure, in which:
Fig. 1 schematically shows a cross section through a heat exchanger according to the invention.
The figure schematically illustrates a heat exchanger 12 according to the invention in cross section. The heat exchanger 12 according to the invention has a casing tube 8 which opens out via radial narrowed portions into an inlet 1 (illustrated at the top in the drawing) and an outlet 2 (illustrated at the bottom in the drawing) . This exemplary embodiment of the heat exchanger 12 is preferably designed for cooling hot gases. The heat exchanger according to the invention can however be used in all possible variants, for example also for cooling liquids, for heating gases or liquids or other heat transfers.
Arranged in the interior of the casing tube 8 and concentrically with respect thereto is an inner tube 3 which is closed off at its end side (illustrated at the top in the drawing) facing toward the inlet 1. The closed-off end side of the inner tube 3 forms an impact plate 11 for a medium, in particular gas, flowing into the heat exchanger 12 via the inlet 1. On that side of the inner tube 3 which faces toward the outlet 2, said inner tube 3 has a coolant inlet 5 which extends through the casing tube 8 and is connected to a coolant inflow 9. Situated in the interior of the inner tube 3 is an outlet tube 6 which extends up to just in front of the impact plate 11 and has an opening there. Said opening is situated approximately centrally on the central axis of the inner tube 3. The outlet tube 6 leads out of the inner tube 3 and merges into a spiral line 7 which is guided, with narrow windings but while maintaining a spacing between the windings, at least along the entire length of the inner tube 3 so as to surround the latter. At the end of the spiral line, the latter merges into a coolant outflow 10 which extends through the casing tube 8.
In a preferred mode of operation for cooling hot exhaust gases of internal combustion engines, the hot exhaust gases pass via the inlet 1 into the casing tube 8. There, said exhaust gases impinge on the impact plate 11, with the flow being separated and first turbulence being generated.
This is illustrated schematically in the figure by means of corresponding arrows. A first direct contact with the cooling medium flowing in the inner tube 3 takes place there at the impact plate 11, such that an initial cooling action is already brought about. After the inflowing hot medium, preferably the gas, is deflected by the impact plate 11, said medium passes into the annular space formed between the casing tube 8 and the inner tube 3. Situated in said annular space is the spiral line which, in this exemplary embodiment, is arranged in the radial direction approximately centrally between the wall of the inner tube 3 and the wall of the outer tube 8. As a result of the flow resistance formed by the spiral line 7 on the one hand and also as a result of the convection occurring between the comparatively cold wall of the inner tube 3, on account of the fresh inflowing coolant, and the warmer walls of the spiral line 7 which has already been traversed by heated coolant, the medium, preferably the gas, flowing into the casing tube 8 is forced to become turbulent. This is indicated in the figure at the top right at the upper two windings of the spiral line 7 by corresponding arrows. As a result of said turbulence, the inflowing medium, preferably gas, runs over a considerably longer path within the casing tube 8 and comes into intensive contact with the surfaces of the elements, inner tube 3 and spiral line 7, which are traversed by the cooling medium.
After passing through the entire length of the casing tube 8 or of the spiral line 7, and after undergoing intense turbulence in doing so, the cooled medium, preferably gas, passes out through the outlet 2.
The flow of the coolant from the coolant inflow 9 through the inner tube 3 and the spiral line 7 to the coolant outflow 10 is likewise indicated by arrows.
In the exemplary embodiment shown for a heat exchanger according to the invention, the inner tube 3 has a diameter d of 60 mm, the diameter of the spiral line ds, measured from outer wall to outer wall, is 110 mm, the diameter D of the casing tube is 150 mm, the length L of the casing tube is 200 to 300 mm, and the diameter of the inlet 1 and of the outlet 2 (not denoted in the figures) is approximately 50 to 60 mm. A copper line with a circular cross section and a diameter of 15 mm is used as the spiral line 7.
This heat exchanger is used to cool exhaust gases, which exit an internal combustion engine at approximately 1000 C, to temperatures of approximately 50 C. For this purpose, n-butane at room temperature (approximately 25 C) is fed into the coolant inlet; the n-butane then left the coolant outlet at a temperature of approximately 120 C. A 30 bar pump was used to feed the coolant n-butane. Instead of n-butane, water or another liquid or liquid mixture can alternatively also be used as coolant.
On account of its dimensions, the heat exchanger according to the invention could be integrated into the exhaust system of a motor vehicle, for example as a replacement for a catalytic converter or silencer.
A positive effect of the drastic cooling of the exhaust gases was found to be that pollutants contained in the exhaust gas, which must otherwise be extracted from the exhaust gas flow by means of complex catalytic converter technology, were precipitated in the heat exchanger. This can be explained in that water is formed as a result of the fast cooling of the exhaust gases from the temperatures at which they exit the internal combustion engine to the dew point of water. Said water almost completely elutriates the further harmful constituents contained in the exhaust gas flow. As a result of the water generated during the cooling of the exhaust gases to the dew point of water, an additional cooling effect is generated, since water can also dissipate a proportion of heat.
In addition, since all gases expand by 1/126 when heated by 1 C and contract in the event of a reduction in temperature, the gas will assume a smaller volume in the case of a temperature difference of several hundred degrees Celsius. This has the result that the use of the heat exchanger according to the invention for cooling the exhaust gases generated in an internal combustion engine of a motor vehicle the noise emissions can be almost completely dissipated and conventional silencers can be dispensed with with the exception of a final silencer.
The heat exchanger according to the invention is not restricted to the use described in this exemplary embodiment, but can be used for cooling or heating various media. It is for example conceivable to use a corresponding heat exchanger, which is of larger dimensions but similar proportions, for cooling exhaust gases from power plants or industrial plants, with it also being possible here for a purification effect to be obtained as a result of the abrupt cooling of the gases.
The heat exchanger can however also be used only for heat transfer without a purification effect.
In this respect, with regard to the importance and scope of the invention, reference is made to the following claims, which alone restrict the scope of the invention.
List of reference symbols 1 Inlet 2 Outlet 3 Inner tube 4 Lower tube end Coolant inlet 6 Outlet tube 7 Spiral line 8 Casing tube 9 Coolant inflow Coolant outflow 11 Impact plate 12 Heat exchanger D Diameter d Diameter ds Diameter L Length
Heat exchangers are often used in technology in order to provide a transfer of heat between two media. Media which are to be treated are either warmed or cooled using heat exchangers in this way.
One field of use for heat exchangers is cooling hot gases. For example, in the field of internal combustion engines, exhaust gases at temperatures of 1000 C and more are discharged from the combustion chambers. In some cases, it is desirable to cool said hot gases to temperatures of 50 C and less. Heat exchangers are typically used here. In certain situations in which space is restricted or else in which it is necessary for other reasons to provide the exchange of heat over as short a path as possible, heat exchangers of smaller or shorter design are desirable.
No heat exchangers are known from the prior art which are particularly suitable for generating a high temperature gradient over an extremely short distance (for example cooling hot gases from an inlet temperature of 1000 C and more to an outlet temperature of below 80 C, preferably below 50 C, over an installation length of approximately 30 cm).
It is therefore an object of the invention to specify a heat exchanger which, with a compact design, makes it possible to obtain a high heat transfer efficiency.
Said object is achieved with a heat exchanger having the features of claim 1. Further advantageous design embodiments of the heat exchanger are specified in claims 2 to 7. Claim 8 specifies a preferred use of the heat exchanger according to the invention, which however does not constitute the only possible use.
The heat exchanger according to the invention is characterized by an inner tube which is situated within a casing tube and which is closed off at one side. The closed-off end of the inner tube is situated at the inlet side of the casing tube, into which flow for example hot gases or other hot media to be cooled. A coolant is initially guided into the inner tube and cools the medium to be cooled, which is flowing past, both on the closed-off end side and on the tube wall. From the inner tube, the cooling medium then passes into a spiral line which is wound around the inner tube, and also leads there to a further cooling action before leaving the heat exchanger.
This firstly results in a considerably increased contact surface in relation to conventional heat exchangers at which contact takes place, separated by means of the walls of the inner tube or of the spiral line, between the cooling medium and the medium to be cooled. In addition, this design embodiment, in which the medium to be cooled initially flows against the single-sidedly closed-off end of the inner tube and then flows laterally past the inner tube along the wound spiral lines, causes turbulence of the medium to be cooled, with said medium also partially running counter to the actual main flow in vortices. This results in a particularly long residence time or a long migration path of the medium to be cooled in the heat exchanger, such that, over a short installation extent of the heat exchanger, intimate contact is generated between the medium to be cooled and the elements, the inner tube and the spiral line, which are to be traversed by the medium. This fact finally has the result that considerable cooling can be obtained over a short longitudinal extent of the heat exchanger.
The heat exchanger according to the invention is of course however also conversely suitable for heating a cool medium, which flows into the casing tube, by means of a heating medium flowing into the "coolant" inflow. In this respect, the terms "coolant inlet", "coolant outlet" and "coolant outflow" are not to be interpreted to be restricted to a coolant, but can likewise be used for a medium which is used for heating a medium flowing through the casing tube, consequently a "heating medium".
An outlet tube which, according to claim 2, is to be provided in the interior of the inner tube has the advantage that the coolant flowing into the inner tube must be distributed in the entire inner tube before it can pass into the spiral line through the outlet tube. The cooling action obtained at the wall of the inner tube is intensified in this way, which leads to an overall better cooling capacity or heat transfer capacity of the heat exchanger. Similar considerations of course apply to operation of the heat exchanger for heating a medium.
The formation of the closed-off side of the inner tube as an impact plate leads to a first generation of turbulence of the inflowing medium taking place already at said geometry, which turbulence contributes overall to the long residence time of the inflowing medium in the heat exchanger and to the thereby obtained high heat exchanger efficiency of the heat exchanger.
The refinement as per claim 4, that the spiral line is guided at least along the entire length of the inner tube so as to surround the latter, likewise contributes to a high heat exchanger efficiency. The individual windings of the spiral line are preferably wound tightly but without coming into contact. A spacing must remain between the individual windings of the spiral line in order that there can also be contact there between the medium to be cooled or to be heated and the surface of the spiral line which is traversed by the coolant or heating medium.
A design as specified in claim 5, wherein the spiral line is arranged with a radial spacing to the wall of the inner tube and to the wall of the casing tube, assists the desired turbulence of the medium flowing through the casing tube, and the associated increased heat transfer efficiency.
It has been proven here that a radial spacing of the spiral line to the wall of the inner tube which is approximately identical to the radial spacing of the spiral line to the wall of the casing tube provides particularly good results (claim 6).
According to claim 7, it is finally advantageous if at least the spiral line of the heat exchanger is composed of a material with good heat conducting properties. Here, copper is preferably used, though other materials with good heat conducting properties are also conceivable, such as for example silver.
The heat exchanger according to the invention is preferably used to cool combustion exhaust gases from internal combustion engines, in particular combustion exhaust gases from motor vehicle engines. Specifically in motor vehicle engines or in the exhaust system of motor vehicle engines, a heat exchanger of said type must on the one hand provide a high cooling capacity in order to cool the hot exhaust gases, which exit the combustion chamber at approximately 1000 C and more, to a temperature of 80 C and less, preferably below 50 C. The heat exchanger must however also be of compact design since the space in the exhaust system of the motor vehicle is restricted. The heat exchanger according to the invention is particularly suitable here.
Further advantages and features of the heat exchanger according to the invention can be gathered from the following description on the basis of the appended figure, in which:
Fig. 1 schematically shows a cross section through a heat exchanger according to the invention.
The figure schematically illustrates a heat exchanger 12 according to the invention in cross section. The heat exchanger 12 according to the invention has a casing tube 8 which opens out via radial narrowed portions into an inlet 1 (illustrated at the top in the drawing) and an outlet 2 (illustrated at the bottom in the drawing) . This exemplary embodiment of the heat exchanger 12 is preferably designed for cooling hot gases. The heat exchanger according to the invention can however be used in all possible variants, for example also for cooling liquids, for heating gases or liquids or other heat transfers.
Arranged in the interior of the casing tube 8 and concentrically with respect thereto is an inner tube 3 which is closed off at its end side (illustrated at the top in the drawing) facing toward the inlet 1. The closed-off end side of the inner tube 3 forms an impact plate 11 for a medium, in particular gas, flowing into the heat exchanger 12 via the inlet 1. On that side of the inner tube 3 which faces toward the outlet 2, said inner tube 3 has a coolant inlet 5 which extends through the casing tube 8 and is connected to a coolant inflow 9. Situated in the interior of the inner tube 3 is an outlet tube 6 which extends up to just in front of the impact plate 11 and has an opening there. Said opening is situated approximately centrally on the central axis of the inner tube 3. The outlet tube 6 leads out of the inner tube 3 and merges into a spiral line 7 which is guided, with narrow windings but while maintaining a spacing between the windings, at least along the entire length of the inner tube 3 so as to surround the latter. At the end of the spiral line, the latter merges into a coolant outflow 10 which extends through the casing tube 8.
In a preferred mode of operation for cooling hot exhaust gases of internal combustion engines, the hot exhaust gases pass via the inlet 1 into the casing tube 8. There, said exhaust gases impinge on the impact plate 11, with the flow being separated and first turbulence being generated.
This is illustrated schematically in the figure by means of corresponding arrows. A first direct contact with the cooling medium flowing in the inner tube 3 takes place there at the impact plate 11, such that an initial cooling action is already brought about. After the inflowing hot medium, preferably the gas, is deflected by the impact plate 11, said medium passes into the annular space formed between the casing tube 8 and the inner tube 3. Situated in said annular space is the spiral line which, in this exemplary embodiment, is arranged in the radial direction approximately centrally between the wall of the inner tube 3 and the wall of the outer tube 8. As a result of the flow resistance formed by the spiral line 7 on the one hand and also as a result of the convection occurring between the comparatively cold wall of the inner tube 3, on account of the fresh inflowing coolant, and the warmer walls of the spiral line 7 which has already been traversed by heated coolant, the medium, preferably the gas, flowing into the casing tube 8 is forced to become turbulent. This is indicated in the figure at the top right at the upper two windings of the spiral line 7 by corresponding arrows. As a result of said turbulence, the inflowing medium, preferably gas, runs over a considerably longer path within the casing tube 8 and comes into intensive contact with the surfaces of the elements, inner tube 3 and spiral line 7, which are traversed by the cooling medium.
After passing through the entire length of the casing tube 8 or of the spiral line 7, and after undergoing intense turbulence in doing so, the cooled medium, preferably gas, passes out through the outlet 2.
The flow of the coolant from the coolant inflow 9 through the inner tube 3 and the spiral line 7 to the coolant outflow 10 is likewise indicated by arrows.
In the exemplary embodiment shown for a heat exchanger according to the invention, the inner tube 3 has a diameter d of 60 mm, the diameter of the spiral line ds, measured from outer wall to outer wall, is 110 mm, the diameter D of the casing tube is 150 mm, the length L of the casing tube is 200 to 300 mm, and the diameter of the inlet 1 and of the outlet 2 (not denoted in the figures) is approximately 50 to 60 mm. A copper line with a circular cross section and a diameter of 15 mm is used as the spiral line 7.
This heat exchanger is used to cool exhaust gases, which exit an internal combustion engine at approximately 1000 C, to temperatures of approximately 50 C. For this purpose, n-butane at room temperature (approximately 25 C) is fed into the coolant inlet; the n-butane then left the coolant outlet at a temperature of approximately 120 C. A 30 bar pump was used to feed the coolant n-butane. Instead of n-butane, water or another liquid or liquid mixture can alternatively also be used as coolant.
On account of its dimensions, the heat exchanger according to the invention could be integrated into the exhaust system of a motor vehicle, for example as a replacement for a catalytic converter or silencer.
A positive effect of the drastic cooling of the exhaust gases was found to be that pollutants contained in the exhaust gas, which must otherwise be extracted from the exhaust gas flow by means of complex catalytic converter technology, were precipitated in the heat exchanger. This can be explained in that water is formed as a result of the fast cooling of the exhaust gases from the temperatures at which they exit the internal combustion engine to the dew point of water. Said water almost completely elutriates the further harmful constituents contained in the exhaust gas flow. As a result of the water generated during the cooling of the exhaust gases to the dew point of water, an additional cooling effect is generated, since water can also dissipate a proportion of heat.
In addition, since all gases expand by 1/126 when heated by 1 C and contract in the event of a reduction in temperature, the gas will assume a smaller volume in the case of a temperature difference of several hundred degrees Celsius. This has the result that the use of the heat exchanger according to the invention for cooling the exhaust gases generated in an internal combustion engine of a motor vehicle the noise emissions can be almost completely dissipated and conventional silencers can be dispensed with with the exception of a final silencer.
The heat exchanger according to the invention is not restricted to the use described in this exemplary embodiment, but can be used for cooling or heating various media. It is for example conceivable to use a corresponding heat exchanger, which is of larger dimensions but similar proportions, for cooling exhaust gases from power plants or industrial plants, with it also being possible here for a purification effect to be obtained as a result of the abrupt cooling of the gases.
The heat exchanger can however also be used only for heat transfer without a purification effect.
In this respect, with regard to the importance and scope of the invention, reference is made to the following claims, which alone restrict the scope of the invention.
List of reference symbols 1 Inlet 2 Outlet 3 Inner tube 4 Lower tube end Coolant inlet 6 Outlet tube 7 Spiral line 8 Casing tube 9 Coolant inflow Coolant outflow 11 Impact plate 12 Heat exchanger D Diameter d Diameter ds Diameter L Length
Claims (8)
1. A heat exchanger for transferring heat between two media, having a casing tube (8) which has an inlet (1) and an outlet (2) for a medium to be cooled, having an inner tube (3) which is arranged within the casing tube (8) and is closed off at the side facing toward the inlet (1), is connected at the side facing toward the outlet (2) to a coolant inlet (5), and has a coolant outlet which leads to that side of the inner tube (3) which faces toward the outlet (2), and merges into a spiral line (7) which winds from there in the direction of the inlet (1) around the inner tube (3), which spiral line (7) finally opens out into a coolant outflow (10).
2. The heat exchanger as claimed in claim 1, wherein the coolant outlet (7) of the inner tube (3) is connected to an outlet tube (6) which is guided in the interior of the inner tube (3) up to that side of the inner tube which faces toward the inlet (1).
3. The heat exchanger as claimed in one of claims 1 or 2, wherein the closed-off side of the inner tube forms an impact plate (11) for medium to be cooled which flows into the casing tube (8) via the inlet (1).
4. The heat exchanger as claimed in one of the preceding claims, wherein the spiral line (7) is guided at least along the entire length of the inner tube (3) so as to surround the latter.
5. The heat exchanger as claimed in one of the preceding claims, wherein the spiral line (7) is arranged with a radial spacing to the wall of the inner tube (3) and to the wall of the casing tube (8).
6. The heat exchanger as claimed in claim 5, wherein the radial spacing of the spiral line (7) to the wall of the inner tube (3) is approximately identical to the radial spacing of the spiral line (7) to the wall of the casing tube (8).
7. The heat exchanger as claimed in one of the preceding claims, wherein at least the spiral line (7) is composed of a material with good heat conducting properties, preferably of copper.
8. The use of a heat exchanger as claimed in one of claims 1 to 7 for cooling combustion exhaust gases from internal combustion engines, in particular combustion exhaust gases from motor vehicle engines.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP04030073A EP1672304B1 (en) | 2004-12-18 | 2004-12-18 | Heat exchanger |
| EP04030073.3 | 2004-12-18 | ||
| PCT/EP2005/013548 WO2006063840A1 (en) | 2004-12-18 | 2005-12-16 | Heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2590569A1 true CA2590569A1 (en) | 2006-06-22 |
Family
ID=34927844
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002590569A Abandoned CA2590569A1 (en) | 2004-12-18 | 2005-12-16 | Heat exchanger |
Country Status (20)
| Country | Link |
|---|---|
| US (1) | US20070295493A1 (en) |
| EP (1) | EP1672304B1 (en) |
| JP (1) | JP2008524543A (en) |
| KR (1) | KR20070094792A (en) |
| CN (1) | CN101080605A (en) |
| AT (1) | ATE365900T1 (en) |
| AU (1) | AU2005315782A1 (en) |
| BR (1) | BRPI0519525A2 (en) |
| CA (1) | CA2590569A1 (en) |
| DE (1) | DE502004004210D1 (en) |
| ES (1) | ES2289419T3 (en) |
| IL (1) | IL183988A0 (en) |
| MA (1) | MA29102B1 (en) |
| MX (1) | MX2007007366A (en) |
| PL (1) | PL1672304T3 (en) |
| PT (1) | PT1672304E (en) |
| RU (1) | RU2007127415A (en) |
| TN (1) | TNSN07230A1 (en) |
| WO (1) | WO2006063840A1 (en) |
| ZA (1) | ZA200705222B (en) |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100943688B1 (en) * | 2008-03-05 | 2010-02-22 | 주식회사 한국피이엠 | Coiled Plastic Pipe for Geothermal Collecting and Manufacturing Method thereof |
| CN100578119C (en) * | 2008-05-17 | 2010-01-06 | 苏权兴 | Heat converter |
| DE202010012438U1 (en) | 2010-09-10 | 2010-11-18 | Hansen, Marret | heat exchangers |
| US9038579B2 (en) * | 2011-05-11 | 2015-05-26 | Korea Institute Of Machinery & Materials | Fuel cell-engine hybrid system |
| KR101384758B1 (en) | 2012-07-11 | 2014-04-14 | 엘지전자 주식회사 | Heat exchanger |
| KR101363545B1 (en) | 2012-07-11 | 2014-02-14 | 엘지전자 주식회사 | Heat exchanger |
| ES2574429T3 (en) | 2013-02-01 | 2016-06-17 | Lg Electronics, Inc. | Air conditioning and heat exchanger for this one |
| ITPD20130321A1 (en) * | 2013-11-26 | 2015-05-27 | I R C A S P A Ind Resiste Nze Corazzate | THERMOBLOCK FOR HEATING LIQUIDS |
| CN107192278A (en) * | 2017-03-27 | 2017-09-22 | 黄云生 | High temperature resistant shoe last tube core heat exchanger |
| CN111043880A (en) * | 2019-12-17 | 2020-04-21 | 山东九泽换热系统有限公司 | Spiral winding tubular heat exchanger |
Family Cites Families (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US757846A (en) * | 1903-05-08 | 1904-04-19 | Sydney Westhorpe Simpson | Feed-water heater. |
| US921811A (en) * | 1906-06-14 | 1909-05-18 | Henry E Deckebach | Liquid purifier and separator. |
| US1391989A (en) * | 1919-12-13 | 1921-09-27 | Zoppel Ferdinand Joseph | Condenser |
| US1992173A (en) * | 1933-08-16 | 1935-02-26 | Owen L Appleby | Water treating apparatus |
| GB571558A (en) * | 1943-08-26 | 1945-08-29 | Townson & Mercer Ltd | Improvements in or relating to the production of distilled water |
| DE2938324A1 (en) * | 1979-09-21 | 1981-04-09 | Willi Ing.(grad.) 3000 Hannover Strohmeyer | House heating system heat exchanger - has even number of pipe coils connected to single inlet and outlet |
| AU7807487A (en) * | 1986-08-21 | 1988-03-08 | Emil Bader | Countercurrent heat-exchanger with helical bank of tubes |
| US4749030A (en) * | 1987-09-28 | 1988-06-07 | Knox Jr Arthur C | Device for condensing organic solvents |
| US5309987A (en) * | 1992-07-21 | 1994-05-10 | Astec | Method and apparatus for heating and cooling food products during processing |
| US5487423A (en) * | 1993-02-16 | 1996-01-30 | Piscine Service Anjou Sa | Heat exchanger |
| NL1009669C2 (en) * | 1998-07-16 | 2000-01-18 | Fasto Nefit Bv | Device for heating sanitary water. |
| DE29815951U1 (en) * | 1998-09-08 | 1998-12-24 | Witzenmann GmbH Metallschlauch-Fabrik Pforzheim, 75175 Pforzheim | Fuel cooler |
| US6293335B1 (en) * | 1999-06-24 | 2001-09-25 | Aquacal, Inc. | Method and apparatus for optimizing heat transfer in a tube and shell heat exchanger |
| CN2404087Y (en) * | 2000-01-26 | 2000-11-01 | 淮阴辉煌太阳能有限公司 | Assembled spiral sleeve heat exchanger |
| US20050133202A1 (en) * | 2001-11-09 | 2005-06-23 | Aalborg Industries A/S | Heat exchanger, combination with heat exchanger and method of manufacturing the heat exchanger |
-
2004
- 2004-12-18 PL PL04030073T patent/PL1672304T3/en unknown
- 2004-12-18 ES ES04030073T patent/ES2289419T3/en active Active
- 2004-12-18 DE DE502004004210T patent/DE502004004210D1/en active Active
- 2004-12-18 PT PT04030073T patent/PT1672304E/en unknown
- 2004-12-18 EP EP04030073A patent/EP1672304B1/en active Active
- 2004-12-18 AT AT04030073T patent/ATE365900T1/en active
-
2005
- 2005-12-16 MX MX2007007366A patent/MX2007007366A/en not_active Application Discontinuation
- 2005-12-16 CA CA002590569A patent/CA2590569A1/en not_active Abandoned
- 2005-12-16 RU RU2007127415/06A patent/RU2007127415A/en not_active Application Discontinuation
- 2005-12-16 KR KR1020077016434A patent/KR20070094792A/en not_active Application Discontinuation
- 2005-12-16 CN CNA2005800434832A patent/CN101080605A/en active Pending
- 2005-12-16 WO PCT/EP2005/013548 patent/WO2006063840A1/en not_active Application Discontinuation
- 2005-12-16 BR BRPI0519525-0A patent/BRPI0519525A2/en not_active Application Discontinuation
- 2005-12-16 US US11/792,513 patent/US20070295493A1/en not_active Abandoned
- 2005-12-16 AU AU2005315782A patent/AU2005315782A1/en not_active Abandoned
- 2005-12-16 JP JP2007545957A patent/JP2008524543A/en active Pending
-
2007
- 2007-06-15 TN TNP2007000230A patent/TNSN07230A1/en unknown
- 2007-06-17 IL IL183988A patent/IL183988A0/en unknown
- 2007-06-18 MA MA30005A patent/MA29102B1/en unknown
- 2007-07-02 ZA ZA200705222A patent/ZA200705222B/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| PT1672304E (en) | 2007-09-27 |
| MX2007007366A (en) | 2007-08-20 |
| IL183988A0 (en) | 2007-10-31 |
| ES2289419T3 (en) | 2008-02-01 |
| KR20070094792A (en) | 2007-09-21 |
| US20070295493A1 (en) | 2007-12-27 |
| EP1672304A1 (en) | 2006-06-21 |
| WO2006063840A1 (en) | 2006-06-22 |
| MA29102B1 (en) | 2007-12-03 |
| CN101080605A (en) | 2007-11-28 |
| TNSN07230A1 (en) | 2008-11-21 |
| EP1672304B1 (en) | 2007-06-27 |
| JP2008524543A (en) | 2008-07-10 |
| WO2006063840A8 (en) | 2007-10-18 |
| DE502004004210D1 (en) | 2007-08-09 |
| ATE365900T1 (en) | 2007-07-15 |
| ZA200705222B (en) | 2008-05-28 |
| BRPI0519525A2 (en) | 2009-02-10 |
| AU2005315782A1 (en) | 2006-06-22 |
| RU2007127415A (en) | 2009-01-27 |
| PL1672304T3 (en) | 2007-11-30 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| FZDE | Discontinued |