WO2016012514A2

WO2016012514A2 - Heat exchanger and modular system for producing a heat exchanger

Info

Publication number: WO2016012514A2
Application number: PCT/EP2015/066794
Authority: WO
Inventors: Peter Neidenberger; Xaver HANSLMEIER; Max Bauer; Volodymyr Ilchenko
Original assignee: Webasto SE
Priority date: 2014-07-23
Filing date: 2015-07-22
Publication date: 2016-01-28
Also published as: WO2016012514A3; DE102014010891A1

Abstract

The invention relates to a heat exchanger comprising a flow channel which is adapted to produce turbulence. The invention also relates to a heat exchanger comprising a deflection body which comprises a deflection area, the contour thereof promoting the production of turbulence in a subsequent channel section of a flow channel. The invention also relates to a heat exchanger comprising a heat exchanger body which is divided into sections which are arranged such that they can rotate with respect to each other about an axis. The invention further relates to a modular system for producing a heat exchanger.

Description

Heat exchanger and modular system for the production of a heat exchanger

The invention relates to heat exchangers for exhaust gas heat recovery and a modular system for producing a heat exchanger.

Heat exchangers for the use of exhaust heat usually have a flow channel through which the exhaust gas is passed. The heat exchanger comprises a heat exchanger body. The primary function of the heat exchanger body is the efficient heat transfer of the heat of the exhaust gas to the fluid flowing on the side of the heat exchanger body facing away from the exhaust gas. It can be provided that a deflecting body is connected at least at one end of the heat exchanger body in order to deflect an exhaust gas or a fluid to be heated, in particular in order to direct it after its exit from an exhaust pipe into the flow channel.

In the present description, a distinction is made between a turbulence of a flow or a turbulent flow and a vortex of a flow or a turbulent flow. Turbulence or turbulent flow are flows that have undefined cross flows to the general flow direction while a vortex or vortex flow is a defined circular flow. The term circular flow is not to be understood as a circular flow with a constant radius, but rather as a substantially continuous flow. A vortex may take various forms, such as a cone shape, a cylinder shape, or any intermediate shape between these two extremes. In addition, vortices can occur whose diameter initially increases starting from the point of origin or the surface of origin and later decreases, or whose diameter initially decreases and later increases. Such vertebrae may be in the form of a hyperboloid or a paraboloid. The term circular flow also includes vortices whose cross-sectional area is elliptical or otherwise continuous have curved circumferential line. If flows have mixed forms of vortexes and turbulent flows, ie the flows have a definable vortex component, then these flows fall under the terms vortex or vortex flow. The vortex forms mentioned above are examples of single vertebrae.

If the vortex has a shape that is inherent to a central axis, for example a circular or elliptical shape, then the center axis can run parallel, perpendicular or angled to the general flow direction in the flow channel. If the vortex has a shape that does not have a central axis, then the center line is the connecting line of the centroids of the cross sections of the vortex in the direction of flow, that is, a line tangent to the general streamline. It can happen that two or more vertebrae overlap. In the following, the term vortex therefore includes flows with one or more individual vertebrae. It is an object of the invention to provide a heat exchanger and a modular system for a heat exchanger, which ensures increased heat transfer.

This object is achieved by a heat exchanger or a modular system according to the independent claims. Advantageous embodiments are given in the dependent claims.

A first aspect of the invention relates to a heat exchanger for exhaust heat utilization, comprising a heat exchanger body, a deflecting body for deflecting an exhaust gas in a common flow channel of the heat exchanger body and the deflecting, wherein the flow channel in the deflecting body has a contour which is formed for vortex formation in a subsequent channel section , The contour for vortex formation can be realized for example by a correspondingly formed side or bottom wall, which gives the flow a twist. However, channel contours may also be provided which are defined by metal plates, protrusions, pins, nails or other vertebral bodies arranged and projecting in the flow channel. Preferably, the contour has a tangent or tangential plane that points through a central region of a flow channel section in the heat exchanger body, in particular a tangent or a tangential plane that runs perpendicular to a longitudinal axis of the flow channel section in the heat exchanger body. In particular, the contour may have a tangential plane parallel to a longitudinal axis, in particular special center axis, the flow channel section extends in the heat exchanger body. The flow channel may be divided in the diverting body into a plurality of subchannels, so that the exhaust gas flows away via partial streams from the exhaust pipe. Furthermore, deflecting regions may be arranged on the outside of the deflecting body, which connect two or more subchannels of the plurality of subchannels, so that the fluid to be heated is located in a sub-channel in a direct current to the flow direction of the exhaust gas and in a further sub-channel in a counter-current is located to the flow direction of the exhaust gas. In particular, the deflection regions can be formed in ribs which are formed in the deflecting body. Suitably, the ribs may have a cross-sectional profile at a connecting surface to the heat transfer body, which corresponds to the cross-sectional profile of the heat exchanger. Furthermore, such features may be included as are described for the third aspect of the invention. The deflection body described here can also be combined with the heat exchanger body described below. That is, for example, a heat exchanger can be formed, which has a flow channel extending in the heat exchanger body and the deflecting body, wherein the flow channel has a cross-sectional profile which is adapted to a peripheral shape of the vortex to be formed and wherein the flow channel in the Deflection body has a contour which is formed for vortex formation in a subsequent channel section. The contour may also include sheets, protrusions, pins, needles, ribs or fin fins that protrude into the channel. Furthermore, the contour may have a knocking bottom or a curved bottom, wherein this may have a curvature about a longitudinal axis and / or transverse axis of the flow channel in the deflection body, so that a twist is imposed on the flow. Like the flow channel according to the third aspect of the invention, the deflecting body can likewise have a cross-sectional profile which promotes or facilitates vortex formation. In particular, the cross-sectional profile can be arranged in the region of a rib.

In an expedient development of the heat exchanger, it is provided that the contour is designed as a wave contour, the contour in particular having a meander shape or a pendulum length. In this way more than one vortex can be superimposed, whereby the vortexes can also flow through different regions of the further flow channel. The flow channel is adapted in the case of multiple vortices to the outlines of all vertebrae. A second aspect of the invention relates to a heat exchanger for exhaust heat utilization, comprising a heat exchanger body, wherein the heat exchanger body is divided into a plurality of heat exchanger body sections, which can form a flow channel in a corresponding relative position in a reference state, wherein the heat transformer body sections in a working state relative to the reference state a common axis are arranged rotated to each other, so that there is a deviating from the reference state configuration of the heat exchanger body. For example, inner walls of the heat exchanger body sections in the reference state may be partially aligned with one another to have inner walls offset from one another in the working state, wherein the end faces of one heat exchanger body section may protrude into the flow channel section of another heat exchanger body section. In particular, these may be end faces of staggered ribs of the heat exchanger bodies. The angle through which two adjacent heat exchanger body sections are rotated relative to one another is defined as their torsional angle. The heat exchanger body is preferably formed as an extruded profile, which is subdivided into the heat exchanger body sections after production. The heat exchanger body sections can be reworked in a post-processing step to produce a desired flow channel formation. For example, the edges of the end faces can be rounded or chamfered. For extrusions are particularly suitable steel and aluminum or alloys of these metals. The heat exchanger body sections can also be made of a different metal. Starting from a heat exchanger body section arranged at one end of the heat exchanger body, the heat exchanger body sections can each be rotated relative to one another by the same angle of rotation. The heat exchanger body sections in particular have an identical cross-sectional profile. A cross-sectional profile of a heat exchanger body portion may be a cross-sectional profile as described in the third aspect of the invention. The cross-sectional profile may be an 8-ter shape, a loop shape, a cone shape, or the like. It can also be a form consisting of straight lines and / or elliptical and / or circular arches, for example an egg shape. Two adjacent heat exchanger body sections can also have different cross-sectional profiles. The heat exchanger body sections can also be arranged rotated relative to one another so that the flow channel branches. A heat exchanger body section may be provided at a transition to an adjacent heat exchanger body section or at a transition to a diverter body in the flow chamber. mungskanal have curves, curvatures or chamfers, which prevent turbulence, but favor or allow vortex generation or a directed cross-flow in the flow channel. The axis is preferably a respective longitudinal axis of the heat exchanger body sections, in particular if the heat exchanger body sections are extruded sections or if the heat exchanger body section is a body having a longitudinal axis. For example, this may be a cylinder-like or cone-like body formed as an extrusion body. In particular, the axis may be a common center axis.

An advantageous development is configured such that due to the rotation of the plurality of heat exchanger body sections, flow obstacles are formed in the flow channel. In particular, the flow obstacles in the flow channel may be curves, bends or bevels that prevent turbulence but promote or permit vortex generation or directed cross flow in the flow channel.

It can be provided in particular that the flow obstacles are formed as a vortex generating means. As a result, one or more defined vortices can be generated in the flow channel of the heat exchanger body in a simple manner, without having to provide additional vertebral bodies or special contours of the channel walls.

The heat exchanger can be developed so that the flow channel is formed by the rotation in a spiral shape. As a result, a flow through the middle layers of the flow in the flow channel can be achieved in a simple manner. In particular, in the flow through a deflection in a deflecting an additional swirl can be generated, which reduces a pressure drop, even if the deflecting has no vortex-promoting design.

The heat exchanger may further comprise a deflecting body for deflecting the exhaust gas and / or the fluid into or out of a sub-channel of the flow channel from or into a further sub-channel of the flow channel. This deflecting body may be the deflecting body described above. The deflecting body may be, in particular, a closing cover or a bottom part. A third aspect of the invention relates to a heat exchanger for exhaust heat utilization, comprising a heat exchanger body, a formed in the heat exchanger body flow channel for guiding an exhaust gas and for heat recovery from the exhaust gas and a vortex generating means for forming a vortex of the exhaust gas in the flow channel, wherein the flow channel has a cross-sectional profile which is at least partially adapted to a peripheral shape of the vortex to be formed. The cross-sectional profile can be particularly preferably adapted to the entire peripheral shape. If the cross-sectional profile is adapted to the entire peripheral shape, then a wire can be formed, which occupies the entire cross-sectional area of the flow channel. Thus, it can be achieved that a cross-flow occurs in an inner region of the flow channel, whereby hot flow layers reach a heat-transferring wall, so that a larger amount of heat can be transferred to a fluid to be heated. Preferably, the fluid to be heated flows in a further flow channel, which is arranged on a side of the heat exchanger body facing away from the flow channel. Furthermore, dead spaces without cross flows are advantageously avoided. The transverse flow increases the temperature gradient between the flow channel and the further flow channel. The heat exchanger expediently has a substantially cylindrical basic shape, but it may also have a conical basic shape. The heat exchanger body may also have a prismatic basic shape. Cylindrical, conical and prismatic shapes have in common that they can be advantageously produced by extrusion, so that extrusion extrusions are formed by extrusion. Such extruded profiles are also referred to as Extrusi- onskörper. Each of these extruded profiles has at least one outer and inner circumferential surface, which run parallel to a central axis and which are bounded by two base surfaces. The bases preferably correspond to the cross-sectional profile. If the heat exchanger body is produced as an extruded profile, it may additionally be provided that the extruded profile is a twisted extrusion body. That is, in the longitudinal direction of the extrusion body is twisted about the longitudinal axis of the heat transfer body. As a result, a spiraling spiral channel is created around the longitudinal axis, whereby advantageously an additional swirl in the flow of the exhaust gas is generated and the heat transfer and thus the efficiency of the heat exchanger is further improved. It can also be provided that the heat exchanger body has different cross-sectional profiles along its longitudinal extension, wherein the base surfaces preferably have an upper cross-sectional profile and an correspond to the lower cross-sectional profile. The outer and inner lateral surface are hereinafter referred to as inside and outside, wherein the flow channel is preferably formed on the inside. In addition, the cross-sectional profile can comprise transverse walls, in particular if the heat exchanger body encompasses the function of a housing and / or has a plurality of outer and inner lateral surfaces. It can be provided that the heat exchanger body has a receiving opening for an exhaust pipe, wherein an innermost lateral surface has a cross section which is adapted to the exhaust pipe, so that the exhaust pipe can be inserted into the heat exchanger body. The heat exchanger can be further developed by the cross-sectional profile is only partially adapted to the peripheral shape of the vortex. This means that the cross-sectional profile of the first flow channel can also have openings through which a flow of the exhaust gas can take place. It can also be provided that an opening is provided between two adjacent sub-channels of the first flow channel, so that the exhaust gas can flow from one sub-channel into the adjacent second sub-channel and vice versa. Branches a flow channel, the individual parts are referred to below as sub-channels. The adaptation of the cross-sectional profile to the vortex can also be described as a vortex form of the cross-sectional profile. A useful development of the heat exchanger may be that the heat exchanger comprises a deflecting body, wherein the heat exchanger body is connected to the deflecting body. The deflecting body may be a bottom part for returning the exhaust gas from the exhaust pipe. The deflecting body can also be a cover for the heat exchanger body. If the heat exchanger body has a substantially cylindrical, conical or prismatic shape, deflecting bodies can be arranged on opposite base surfaces of the heat exchanger body at the ends in each case. In this case, the flow channel can also extend to the deflecting body or the deflecting body. The deflection body may also have an inner side and an outer side, wherein the flow channel is preferably formed on the inside of the deflection body. On its inner side, the deflecting body can have a deflection region in which an exhaust gas which flows out of an exhaust gas pipe is preferably deflected by 180 °, so that it flows into the flow channel in the heat exchanger body. The heat exchanger body and the deflecting body can be joined together by joining. In this case, the deflecting body and the heat exchanger body can be connected to one another by means of soldering, welding, gluing or pressing. It can be provided that the heat exchanger body and the deflecting body are integrally formed, that is, that the heat exchanger body and the deflecting from a workpiece are formed or exist. The heat exchanger body and the deflecting body may be made of aluminum, an aluminum alloy, iron, an iron alloy, in particular steel. Preferably, the heat exchanger body and the deflecting body are made of the same material. The deflection body is preferably a casting or a compression molding. In particular, the deflecting body can not be an extruded profile. In particular, the flow channel is subdivided into a plurality of subchannels, wherein each subchannel can be arranged in each case in one rib formed in the heat exchanger body. The heat exchanger body may be formed star-shaped, wherein the ribs point wise wise radially from a central axis of the heat exchanger body have radially outward. The ribs may have gaps in which a further flow channel is designed to guide a fluid to be heated. The flow channel and the further flow channel are also referred to below as the first flow channel and the second flow channel. The second flow channel is preferably divided into a plurality of flow channel sections. The second flow channel is formed on the corresponding opposite side of a heat transfer wall of the heat transfer body. If the first flow channel is arranged on the inside of the heat exchanger body, then the second flow channel is arranged on the outside. If the diverting body is a bottom part, then the part of the first flow duct arranged in the bottom part can advantageously have a contour in which a wave contour is pronounced, so that the flow already acquires a swirl before entering the flow duct in the heat exchanger body or at least cross flows through a medium flow area, so that the vortex formation is supported and the flow layers are better mixed. Preferably, a meander shape or a pendulum length is formed in the second flow channel by the wave contour. If two opposing wave contours are formed in two opposite walls of the channel contour of the second flow channel, advantageously two intermeshing vortices can be produced. As a result, the heat transfer is improved due to the advantageous higher achieved mixing of the exhaust gas. An exhaust gas flowing in from the exhaust pipe to the deflection body is conducted or deflected in a deflection region of the deflection body into the flow channel in the heat exchanger body. The cross-sectional profile of the flow channel in the heat exchanger body can be made identical to the cross-sectional profile in the deflecting body. In particular, the interconnected base surfaces of the heat exchanger body and of the deflection body can be identical to one another or have common partial surfaces. The vortex generator can be arranged in a deflecting body. The vortex generating means may be a protruding edge, a pin or a nail or be formed by the wave contour of the flow channel in the deflecting body. However, it can also be provided that the vortex generating means is additionally or subsequently secured in the flow channel. If the deflecting body is a cover, it can be provided that the cover has an opening for receiving an exhaust pipe. Furthermore, the end cover deflection regions, in particular on an outer side, have, which allow a backflow of the fluid to be heated from a first sub-channel into a second sub-channel. The heat exchanger may have a housing which covers the further flow channel on the outside of the heat exchanger body. Suitably, however, the heat exchanger can be developed in such a way that the housing is formed by the heat exchanger body. In this case, a jacket layer of the cross-sectional profile of the heat exchanger body forms an outer housing wall. Furthermore, the housing may be formed in the region of a deflecting body by the deflecting body itself, wherein the outer housing wall is formed by an outer wall of the deflecting body.

The heat exchanger may be appropriately developed so that the peripheral shape of the vortex is an 8-ter shape or loop shape. Thus, the cross-sectional shape of the flow channel assumes an 8-th shape or a loop shape. As a result, the center of the flow channel can be traversed in a simple manner with a transverse flow, so that the middle layers reach a heat transfer directly to a channel wall of the flow channel facing the further flow channel. The 8-th shape and the loop shape are characterized by two protrusions projecting from opposite points of the channel walls of the flow channel, over which the exhaust gas flows. In this case, in a region behind the projections, two partial streams intersect, whereby a particularly good mixing of the flow layers, in particular the middle flow layers is achieved. Alternatively or additionally, the heat exchanger can be developed such that the peripheral shape of the vortex is a trapezoidal shape. This preferably has rounded corners. Such a cross-sectional profile is particularly easy to produce, with the wall thickness of the heat exchanger is advantageously constant, so that a low-loss, homogeneous heat transfer along the heat exchanger wall can be set. In particular, no thickened points occur in the channel wall which produce a heat transfer. influence negatively. It may be provided that two opposite trapezoidal shapes form the 8th shape or the loop shape.

Suitably, the heat exchanger can be developed so that the peripheral shape of the vortex is formed of juxtaposed circular or elliptical arcs with different or equal radii. For example, this creates an egg shape. As a result, it is possible to generate vortices which have a largely homogeneous cross-flow shape, that is to say a peripheral shape which has no or only very small changes in curvature along the peripheral shape, as a result of which a uniform heat transfer can be achieved. It may be desired that the peripheral shape of the vortex consists of a mixed form. In this case, for example, an outwardly curved elliptical arc having a corresponding radius may be formed on an outer inner wall of the flow channel, wherein the two side walls producing a rib shape are curvilinear walls. An inner inner wall may in turn have an outwardly inclined curvature, wherein the inner inner wall may also be formed by an exhaust pipe. If the radii are adapted to the radius of curvature of the basic shape of the heat exchanger body, then aligned ribs provide for the substantially cylindrical or conical basic shape of the heat exchanger body. It may also have only the outer inner wall has a curvature. In this case, the inner wall can be straight. In this way, a heat exchanger body can be realized with an inner prismatic and an outer cylindrical shape.

In a preferred embodiment of the heat exchanger is intended that the cross-sectional profile of the flow channel has at least in the heat exchanger body an inlet opening for the exhaust gas and at the inlet opening an overflow edge for vortex formation or to support the vortex formation of the incoming exhaust gas is formed. This allows the exhaust pipe to form an inner inner wall of the flow channel, so that advantageous material can be saved. The inlet opening preferably extends along a longitudinal extent of the heat exchanger body in a longitudinal section of the flow channel. Further, the exhaust gas flowing in the exhaust pipe may already give off heat to the recirculated exhaust gas, so that the temperature of the recirculated exhaust gas is increased. Due to the simultaneous vortex formation in the flow channel, the so reheated exhaust gas is supplied to the outer inner wall, so that the heat transfer performance is increased overall. As a longitudinal section is a in the section of the flow channel, which is a partial section of the longitudinal extension of the flow channel.

The aforementioned aspects of the invention are preferably suitable for a modular system for producing a heat exchanger from a plurality of components, wherein the components have a common flow channel for guiding an exhaust gas and for heat recovery from the exhaust gas, wherein arranged in the flow channel at least one flow obstacle is, so that the flow layers are mixed in the flow channel, wherein the components are selected from the group of heat exchanger body or a plurality of heat exchanger body sections, bottom part and end cover, wherein the selected components comprise at least one heat exchanger body or a plurality of heat exchanger body sections, the components after selection by Joining be joined together. Due to the fact that the components have a common flow channel with flow obstacles or at least one flow obstacle, a heat exchanger can be assembled and produced in a simple manner by providing said components whose heat transfer is increased compared to a conventional heat exchanger and adapted to the corresponding intended use. In particular, if the components are extruded parts of the same material, the modular system can be assembled in a simple manner. The joining can be a pressing, gluing, welding or soldering.

In an advantageous development, a vortex generating means for vortex formation in the flow channel is provided in the flow channel, wherein the flow channel in the heat exchanger body has a cross-sectional profile which is adapted to a peripheral shape of the vortex to be formed. The cross-sectional profile may be an 8-th shape, a loop shape, a cone shape, or the like. It can also be a form consisting of straight lines and / or elliptical and / or circular arches, for example an egg shape. In particular, features of the third aspect of the invention may be provided or formed with corresponding components in the modular system.

It can be provided in particular that the bottom part and / or the end cover are each formed as a deflecting body, wherein the deflecting body for deflecting an exhaust gas in a common flow channel of the Wärmeübertragerkör- pers and the deflecting body is provided, and wherein the flow channel in the deflecting body has a contour which is formed for vortex formation in a subsequent channel section. In particular, features of the third aspect of the invention may be provided or formed in corresponding components in the modular system.

The modular system is expediently developed such that the heat exchanger body is subdivided into a plurality of heat exchanger body sections, wherein the heat exchanger body sections are arranged in a working state with respect to a reference state about a common axis rotated to each other, so that there is a deviating from the reference state configuration of the heat exchanger body. In particular, features of the second aspect of the invention may be provided or formed in corresponding components in the modular system. Suitably, the modular system is configured such that a first heat exchanger body and a second heat exchanger body portion of the plurality of heat exchanger body sections ribs, wherein the flow channel is disposed in the first and the second heat exchanger body portion between two ribs, and wherein the at least one flow obstacle through at least partially a portion the flow channel in the first heat exchanger body portion overlapping end faces of the ribs of the second heat exchanger body portion is formed. In this way, the flow obstacles can be formed in a simple manner, in particular if the heat exchanger body or the heat exchanger body sections are extruded profiles which have the same cross-sectional profile.

Additionally or alternatively, the modular system is further developed in such a way that the heat exchanger body or the plurality of heat exchanger body sections, preferably all of the components, have a common second flow channel for guiding the fluid to be heated, which is arranged on a side of the heat exchanger body facing away from the flow channel or the plurality of heat exchanger body sections is. If the heat exchanger body or the majority of the heat exchanger body sections are an extruded profile, then both channels can be realized in a single component in a particularly simple manner. In this way, it is possible in particular to omit a housing which is otherwise to be attached to the outside, when the outer of the two flow channels is surrounded by an outer wall. is also formed in the heat exchanger body or the plurality of heat exchanger body sections.

The modular system can be further developed in such a way that the heat transfer body or the majority of the heat exchanger body sections are extruded profiles. In particular, the remaining components can be castings or pressed parts, which are preferably manufactured using a method different from extrusion molding. Extruded profiles are characterized by their advantageous ease of production, in particular, a homogeneous nature of the finished component can be achieved. Furthermore, a plurality of similar heat exchanger body or heat exchanger body sections can be made with only a single die.

The heat exchangers mentioned may in particular be a further development of cylindrical or substantially pot-shaped heat exchangers with alternating direct and countercurrent regions.

The invention is based, in particular, on the following findings: By virtue of the fact that a cross-sectional profile of a flow channel is adapted to a vortex to be formed, or if the flow channel in the deflecting body has a wave contour, vortex formation is favored and mixing of the flow layers in the flow channel is achieved without too high pressure loss occurs in the flow channel. By a rotation of heat exchanger sections to each other a flow in a flow channel is advantageously imposed a twist and mix the flow layers. Characterized in that in the assembled heat exchanger, a flow channel is formed with flow obstacles, the flow layers can mix in the flow channel.

Show it:

Figure 1 is a schematic sectional view of a heat exchanger;

Figure 2 is a schematic sectional view of a heat exchanger with various examples for the design of the flow channel a third embodiment of a suitable for vortex formation contour of a heat exchanger, a schematic arrangement of flow channels of a heat exchanger designed as a cover deflecting a heat exchanger a heat exchanger body of a heat exchanger as a second embodiment of a suitable vortex formation contour of a heat exchanger Floor formed deflecting a heat exchanger a arranged in the bottom part deflection a schematic view of a heat exchanger

In the following description of the drawings, like reference characters designate like or similar components.

FIG. 1 shows in a plan view a sectional view of one half of a substantially cylindrical heat exchanger 1 with a deflecting body designed as a bottom part 10 and a housing 70. In the bottom part 10, ribs 1 1 extending radially outward around a central axis 2 of the heat exchanger 1 are formed , which are arranged offset from each other by an angle α. In the present case, the angle α is 45 °, so that in the heat exchanger a total of eight ribs 1 1 are formed. It can also be formed more or less ribs 1 1. The ribs 1 1 are presently formed of an outer wall 13 and two side walls 14 and are interconnected by an inner wall 15 designed as a connecting web. The connecting webs form a prismatic inner shell of the cylindrical base The ribs 1 1 each surround a partial channel 31 of a first flow channel 30. The housing 70 and the bottom part 10 may also be integrally formed, wherein the bottom part 10 may then have a continuous outer jacket. Not shown is an exhaust pipe, which rests on the bottom part 10, wherein from the exhaust pipe, an exhaust gas flows into a deflection region 12 of the bottom part 10. The exhaust pipe has a diameter which corresponds approximately to the inner diameter of the prismatic inner shell, so that the exhaust pipe can lean against this or be attached thereto.

The deflection region 12 extends from the central axis 2 to the outer walls 13 of the ribs 1 1. The geometry of the deflection region 12 is discussed in more detail in FIGS. 5 c and 5 d. The exhaust gas is distributed through the deflection in the ribs 1 1, which is indicated by a curved line 3. In an inlet opening 17 of the ribs 1 1 1 a flow obstacle 16 is arranged. The flow obstruction 16 is a wedge which projects into the first flow channel 30 and causes a cross flow. As a result of this transverse flow, a vortex 4 is produced in the subsequent channel section, the central axis of which runs essentially parallel to a longitudinal axis of the further channel section. The cross-sectional profile of the first flow channel 30 is trapezoidal in the ribs 1 1, wherein the outer wall 13 represents the shorter of the two parallels in the trapezoid and wherein the side walls 14 form the two non-parallel connecting lines of the trapezoid. The deflection region 12 is subdivided in front of the inlet region 17 by dividing webs 18, which are respectively arranged in front of the inner walls 15 and subdivide the exhaust gas stream into a number of exhaust gas partial streams, wherein the number of exhaust gas partial streams corresponds to the number of ribs 1 1.

Together with the housing 70 form the ribs 1 1 in intervals a further or second flow channel 40 for a fluid to be heated. The fluid may be water or a coolant, for example a water-glycol mixture. A primary function of the deflection body is the deflection of the exhaust gas and the fluid to be heated. In the present embodiment, the diverting body has a secondary function, namely a heat transfer from the hot exhaust gas to the cooler, to be heated fluid. The heat transfer takes place via the side wall 14. Here, the temperature gradient between an inner side of the side wall 14 and an outer side of the side wall 14 is crucial for the efficiency of heat transfer. The Deflection of the fluid to be heated is described in more detail in Figure 5c. The deflection takes place in the view in FIG. 1 below the ribs 11 in the elbows provided therefor, for example pipe bends, segment bends or elbows, which form a deflection region, not shown in FIG. 1, in the second flow channel 40.

By means of the vortex 4, the exhaust gas layers flowing on the side wall 14 are mixed or exchanged with the exhaust gas layers flowing further inwardly in the flow channel 30, so that a larger temperature gradient is established on the side wall 14.

FIG. 2 also shows a plan view of a section through one half of a heat exchanger body 20, which is firmly joined together with the bottom part 10 shown in FIG. 1, the center axes of the bottom part 10 and the heat exchanger body 20 coinciding. The heat exchanger body 20 is formed as an extruded profile and made by extrusion from an extruded mold. The heat exchanger body 20 is made of an aluminum alloy, but may also be made of another thermally conductive material. In the embodiments, the heat exchanger body 20 and the bottom part 10 made of the same material. The heat exchanger body 20 has corresponding to the bottom part 10 a plurality of ribs 21 a-d, which protrude in a star shape around the central axis 2 to the outside.

For clarity, a plurality of different cross-sectional profiles of the ribs 21 a-d are shown in FIG. Each of the ribs 21 a-d is accordingly penetrated by a partial channel of the first flow channel 30. Preferably, only a single cross-sectional profile of one of the fins 21 a-d shown is used repeatedly in the heat exchanger body 20, which expediently corresponds to the cross-sectional profile of the first flow channel 30 of the fins 1 1 of the base part 10.

A first cross-sectional profile of a first rib 21 a has a loop shape. The loop shape is characterized by two different width partial vortex sections, which are separated from each other by two opposite, of side walls 24a of the rib 21 a transversely to a flow direction in the flow channel 30 projecting round projections 26a. The outer shape of the rib 21 a is trapezoidal. In the present case, an outer wall 23 a of the rib 21 a shorter than an inner wall 25 a of the rib 21 a. However, the outer wall 23a can also be longer than the inner wall 25a. The first cross Section profile is thus adapted to a vortex with a loop-shaped peripheral shape. A vortex with such a peripheral shape is in particular a double vortex.

A second cross-sectional profile of a second rib 21 b has an outwardly tapered trapezoidal shape. A third cross-sectional profile of a third rib 21 c has an inwardly tapering trapezoidal shape. The outer shapes of the ribs 21 b and 21 c are corresponding trapezoidal shapes, wherein the outer shape of the rib 21 b tapers to the outside and the outer shape of the rib 21 c tapers inwardly. The heat exchanger body 20 does not necessarily have ribs. For example, the heat exchanger body having a plurality of sub-channels, which are separated by transverse walls between two jacket walls, so that there is a shell-shell profile. In this case, it may be provided that the exhaust gas and the fluid to be heated flow alternately through the subchannels, that is, there are partial channels of the first flow channel 30 and partial channels of the second flow channel 40 alternately see between two jacket walls of the heat exchanger body 20. In particular, it is advantageous if in each case only sub-channels of the first flow channel 30 are arranged between two jacket walls and form there a first flow jacket and sub-channels of the second flow channel 40 either between a further outer jacket wall and the first flow jacket or between a further inner shell wall, the may also be formed by an exhaust pipe, and the first flow jacket are arranged. The second and the third cross-sectional profile are thus adapted to trapezoidal peripheral shapes of a vortex.

A first cross-sectional profile of a fourth rib 21 d has an 8-th shape. The 8-th shape is characterized by two equal partial vortex sections, which are separated from one another by two round projections 26d projecting transversely to a flow direction into the flow channel 30 from side walls 24d of the rib 21d. The outer shape of the rib 21 d is rectangular. An outer wall 23d of the rib 21d is as long in the 8th shape as an inner wall 25d of the rib 21d. The fourth cross-sectional profile is thus adapted to a vortex with an 8-ter-shaped peripheral shape. A vortex with such a peripheral shape is in particular a double vortex.

All of the shown ribs 21 ad have in common that the inner walls 25a-d are respectively mounted in place of an inlet opening between two inner walls connecting the ribs 21 ad. is orders. However, it can be provided that the inner walls 25a-d are part of an exhaust pipe inserted into the heat exchanger.

Exemplary embodiments of the cross-sectional profile of the flow channel 30 in the bottom part are shown in FIGS. 3a to 3c. The heat exchanger body may have an identical or similar cross-sectional profile in the ribs.

The cross-sectional profile of a rib 11 of the bottom part shown in FIG. 3 a substantially corresponds to a trapezoidal shape with rounded corners and an inlet opening 17 instead of a closed inner wall. The outer wall 13 has an outwardly curved curvature. The cross-sectional profile is thus adapted to a peripheral shape of a vortex 4 of two straight lines and a bow connecting the straight lines. The side walls 14 may readily have a curvature, whereby the cross-sectional profile is adapted to a vortex with a circumferential shape formed from juxtaposed circular or elliptical arcs with different or equal radii, for example an egg shape.

At an edge of the inlet opening 17 an inwardly curved flow obstruction 16 is formed as a vortex generating means. The rounded surface of the flow restrictor 16 allows the flow of the surface to follow without stall. At the same time the flow is imposed on a transverse flow, which forms the desired vortex shape in the cross-sectional profile in combination with the cross-sectional profile. In other words, the cross-sectional profile is adapted to the vortex to be formed. FIG. 3b shows a contour in the form of a pendulum track for aiding eddy formation in the cross-sectional profile. The side walls 14 have a wave form, with wave crests 19 of one side wall 14 facing the wave crests 19 of the other side wall 14. This forces the flow to cross over. After a few intersections, two opposing vortices 4a, b are formed by the building up of the flows in the cross-sectional profile at the end of the vortex path. The cross-sectional profile of the pendulum is to illustrate how the contour has an influence on the subsequent flow, once again shown by dashed lines in Figure 2. The contour is not adapted in Figure 2 to the subsequent channel section. An adaptation of the contour to the subsequent channel section in the heat exchanger body 20 is readily possible. Figure 3c shows a contour in a meandering shape, wherein the two side walls 14a, b are formed identical to each other in many parts and their respective opposing tangents in these parts are aligned parallel to each other, so that the wave crests 19a of the first side wall 14a with respect to the troughs 19b the second side wall 14b are located. In this way, a speed component running transversely to the flow direction can be imposed on a very wide flow cross-section so that a very wide vortex in the cross-sectional profile adjusts at one end of the subsection of the flow channel 30 in the rib 11. In addition, a plurality of sub-sections, each with a meander-shaped contour can be arranged side by side, although the outside of the side walls 14a, b are formed with a corresponding waveform.

If the cross-sectional profile in FIG. 3 a - c is a cross-sectional profile of the heat exchanger body, then the inlet opening 17 can extend at least partially along the longitudinal extension, that is to say preferably parallel to the central axis. This is particularly advantageous if between the exhaust pipe and the heat exchanger body, a gap is provided, through which the exhaust gas can flow back, in which case the exhaust gas through the inlet port 17 allows an exhaust gas exchange or an afterflow of the exhaust gas, whereby the vortex formation can be supported. It can also be provided that the inlet opening 17 tapers along the longitudinal extent of the heat exchanger. This may in particular be the case when the heat exchanger body is a conical body. FIG. 4 shows a schematic arrangement of the inner first flow channel 30 and outer second flow channel 40 of a heat exchanger 1. An inner circle represents an exhaust pipe 80, which is inserted into the heat exchanger body 20 and forms an inner wall 81 for the arranged around the exhaust pipe sub-channels 31 of the first flow channel 30. In each case, two sub-channels 31 of the flow channel 30 emit heat to a second sub-channel 41 of the second flow channel 40. The outer circle represents a housing 70.

FIGS. 5a to 5c show a side view of a heat exchanger 1, comprising a closure cover 50 shown in FIG. 5a, a heat exchanger body 20 shown in FIG. 5b, and a bottom part 10 shown in FIG. 5c. It is the History of the second flow channel 40 exposed. The bottom part 10, the heat exchanger body 20 and the end cover 50 are essentially rotational bodies which have a common central axis 2. The deflection bodies 10, 50 and heat exchanger body portions 20 'shown in FIGS. 5 a to 5 c are an example of a modular system for producing a heat exchanger 1. It is also possible for only one heat exchanger body section 20 'to be designed as a heat exchanger body 20. Each of the heat exchanger body sections 20 'shown in FIG. 5b is an extruded profile, the cross sections of the heat exchanger bodies 20' being identical. The same die is used in the manufacture of the heat exchanger body sections 20 '.

The deflecting body designed as end cap 50 shown in FIG. 5a has two deflecting regions 52 ', which diverts a fluid to be heated, which flows from a flow channel section of the second flow channel 40 of the heat exchanger body 20 into the deflecting region 52'. The fluid to be heated is deflected by 180 °. The deflection regions 52 'are elbows and can be designed as elbows, segment elbows or elbows. On the side of the end cover 50, an outlet pipe 60 is arranged, from which flows in heated by the heat exchanger 1 fluid.

The end cover 50 has an exhaust pipe receiving opening 55 for receiving an exhaust pipe.

FIG. 5b shows a heat exchanger body 20 in an assembled state. The heat exchanger body 20 is subdivided into three heat exchanger body sections 20 ', wherein the individual heat exchanger body sections 20' are shown spaced apart for the sake of clarity. The heat exchanger body sections 20 'are mutually rotated by an angle. As a result, the sections of the first flow channel and the second flow channel 40 are also arranged offset from one another. As a result, the projections projecting into the flow channels 40 influence the direction of the flow, so that the flow is conducted in a spiral around the heat exchanger body 20. For an assembly of the heat exchanger body 20, the heat exchanger body sections 20 'are joined together by joining. In the present case, the upper heat exchanger body sections about the central axis 2 are arranged to each other by a respective angle of rotation to each of their lower neighbors. The twist angle is 10 °. The heat exchanger body 20 has an inner wall 25 for abutment of the exhaust pipe to be pushed into the heat exchanger body 1.

In Figure 5c designed as a bottom part 10 deflecting body is shown. On the outer side, the bottom part 10, just like the end cover, has deflection regions 12 'of the second flow channel 40.

Dashed lines show a bottom contour 121 of the inner deflection region 12 of the bottom part 10. The deflection region 12 has a thickening about the central axis, which ensures the uniform deflection of the exhaust gas flow from the exhaust pipe. The thickening initially has an annular region tangential to the exhaust gas flow, so that the exhaust gas flow can follow the contour of the deflection region 12 in the first flow channel without turning into turbulence. Outwardly, the bottom contour initially sloping from the central axis 2, then to rise again and thus to form an arc which has a curvature of 180 ° in total. The partial webs 18 shown in FIG. 1 may follow the bottom contour 121 in their shape, wherein it may be provided that the outer radius of the partial webs 18 is smaller than the radius of the inner side 25 of the heat exchanger body 20 shown in FIG. 5b, so that the exhaust pipe is at the edges the partial webs 18 can rest. An inlet tube 61 is arranged laterally on the bottom part 10, from which fluid flows through the heat exchanger 1 into the second flow channel 40.

It can be provided that the outlet pipe 60 and the inlet pipe 61 are both arranged in a deflecting body. In particular, the outlet tube 60 and the inlet tube 61 may both be formed in or on the bottom part 10 or the end cover 50. Also conceivable is an arrangement of the tubes on a housing or on or in one of the heat exchanger body sections 20 '.

FIG. 5 d shows a further exemplary embodiment of the bottom part 10 in a sectional view, wherein an annular body 90 is arranged in the middle of the deflection region 12. The ring body can serve on the one hand the support of an exhaust pipe and on the other hand have passage openings 91 for the exhaust gas. The ring body 90 is supported on a bottom surface with a bottom contour 121. FIG. 6 shows a perspective exterior view of a heat exchanger 1 with an exhaust pipe receiving opening 55, wherein a meandering flow path 5 of the fluid to be heated in the second flow channel is indicated on the outside of the housing 80. Since the recirculated exhaust gas flows in the view in Figure 6 after flowing out of the exhaust pipe and a deflection in the deflector 10 by 180 ° upward, the fluid to be heated flows after flowing through an attached to the bottom part 10 inlet pipe 61 initially in DC with the exhaust gas. After the first deflection 6 in the end cap 50, the fluid to be heated flows countercurrently to the exhaust gas. After the second deflection, the fluid to be heated flows again in direct current. This flow is continued accordingly.

The aforementioned components 10, 20, 20 ', 50 of the heat exchanger 1 are suitable for a modular system for producing a heat exchanger, wherein the heat exchanger 1 preferably has a flow channel 30 in which a vortex 4 is formed, wherein in the flow channel 30th a vortex generating means is provided. The components comprise in particular the bottom part 10, the heat exchanger body 20 or the heat exchanger body sections 20 'and the end cover 50. The features of the invention disclosed in the above description, in the drawings and in the claims can be used individually or in any combination for the realization of the Invention essential.

LIST OF REFERENCE NUMBERS

1 heat exchanger

2 central axis

3 curved line

4 whirls

5 flow pattern of the fluids to be heated 6 deflection

10 bottom part

rib

12 deflection in the first flow channel 121 bottom contour

12 'deflection in the second flow channel

13 outer wall

14 sidewall

15 inner wall

16 flow obstacle, overflow edge

17 inlet area

18 dividing bridges

19 wave crests

19a wave crests

19b wave troughs

20 heat exchanger body

20a heat exchanger body sections

21 a first rib

21 b second rib

21 c third rib

21 d fourth rib

23a, d outer walls

24a, d sidewalls

25a-d interior walls

26a, d round projections

30 First flow channel Partial channel of the first flow channel

Second flow channel

Partial channel of the second flow channel

End cover

Deflection in the second flow channel

Inner wall, exhaust pipe receiving opening

outlet pipe

inlet pipe

casing

exhaust pipe

inner wall

ring body

Passage openings

Claims

claims

1 . Heat exchanger for exhaust heat utilization, comprising a heat exchanger body (20), a deflecting body (10, 50) for deflecting an exhaust gas in a common flow channel (30, 40) of the heat exchanger body (20) and the deflecting body (10, 50),

- Wherein the flow channel (30) in the deflecting body (10, 50) has a contour which is formed for vortex formation in a subsequent channel section.

2. Heat exchanger according to claim 1, wherein the contour is formed as a wave contour, wherein the contour in particular has a meander or a pendulum.

3. heat exchanger for exhaust heat utilization, comprising a heat exchanger body (20), - wherein the heat exchanger body (20) is subdivided into a plurality of heat exchanger body sections (20 ') which can form a flow channel in a corresponding state relative to a reference state

- Wherein the heat exchanger body sections (20 ') in a working state relative to the reference state about a common axis (2) to each other rotated are arranged, so that there is a deviating from the reference state configuration of the heat exchanger body (20).

4. Heat exchanger according to claim 3, wherein by the rotation of the plurality of heat exchanger body sections (20 ') flow obstacles in the flow channel

(30, 40) are formed.

5. Heat exchanger according to claim 4, wherein the flow obstacles are formed as a vortex generating means.

6. Heat exchanger according to one of claims 3 to 5, wherein the flow channel (30, 40) is formed by the rotation in a spiral shape.

7. Heat exchanger according to one of claims 3 to 6, further comprising a deflecting body (10, 50) for deflecting the exhaust gas and / or the fluid into or out of a partial channel of the flow channel (30, 40) from one or another Partial channel of the flow channel (30, 40).

8. Heat exchanger for exhaust heat utilization, comprising a heat exchanger body (20), in the heat exchanger body (20) formed flow channel (30) for guiding an exhaust gas and for heat recovery from the exhaust gas, a vortex generating means (12, 16) for forming a vortex of the exhaust gas in the flow channel (30),

- Wherein the flow channel (30) has a cross-sectional profile which is at least partially adapted to a peripheral shape of the vortex (4) to be formed.

9. Heat exchanger according to claim 8, wherein the peripheral shape of the vortex (4) is an 8-ter shape or loop shape.

10. Heat exchanger according to claim 8 or 9, wherein the peripheral shape of the vortex (4) is a trapezoidal shape.

1 1. Heat exchanger according to claim 8, wherein the peripheral shape of the vortex (4) is formed of juxtaposed circular or elliptical arcs with different or equal radii.

12. Heat exchanger according to one of claims 8 to 1 1, wherein the cross-sectional profile of the flow channel (30) at least in the heat exchanger body (20) has an inlet opening (17) for the exhaust gas and at the inlet opening (17) has an overflow edge (16). is formed for vortex formation or to support the vortex formation of the incoming exhaust gas.

13. Modular system for producing a heat exchanger (1) from a plurality of components,

- Wherein the components have a common flow channel (30) for guiding an exhaust gas and for heat recovery from the exhaust gas,

wherein at least one flow obstruction is arranged in the flow channel, so that the flow layers are mixed in the flow channel,

- wherein the components are selected from the group heat exchanger body (20, 20 ') or a plurality of heat exchanger body sections (20'), bottom part (10) and end cover (50),

wherein the selected components comprise at least one heat exchanger body (20, 20 ') or a plurality of heat exchanger body sections (20'),

- In which the components are connected to each other after selection by joining.

14. Modular system according to claim 13, wherein in the flow channel (30) a vortex generating means for vortex formation is provided in the flow channel, and wherein the flow channel (30) in the heat exchanger body (20) has a cross-sectional profile which is adapted to a peripheral shape of the vortex (4) to be formed.

15. Modular system according to claim 13 or 14, wherein the bottom part (10) and / or the end cover (50) each as a deflecting body (10, 50) are formed, wherein the deflecting body (10, 50) for deflecting an exhaust gas in a common Flow channel (30, 40) of the heat exchanger body (20) and the deflecting body (10, 50) is provided, and wherein the flow channel (30) in the deflecting body (10, 50) has a contour which is formed for vortex formation in a subsequent channel section ,

16. Modular system according to one of claims 13 to 15, wherein the heat exchanger body (20) in the plurality of heat exchanger body sections (20 ') is divided, wherein the heat exchanger body sections (20') in a working state relative to a reference state about a common axis (2) to each other are arranged, so that there is a deviating from the reference state configuration of the heat exchanger body (20).

17. Modular system according to one of claims 14 to 16, wherein the Wärmeübert- gerkörper (20, 20 ') or the plurality of Wärmeübertragerkörperabschnitte (20'), preferably all of the components, a common second flow channel for guiding the fluid to be heated, the on a side facing away from the flow channel (30) side of the heat exchanger body (20, 20 ') or the plurality of heat exchanger body sections (20') is arranged.

18. Modular system according to one of claims 14 to 17, wherein the heat exchanger body (20) or the plurality of heat exchanger body sections (20 ') are extruded profiles.