EP2430385A1 - Heizkörper für ein kraftfahrzeug mit einer brennkraftmaschine - Google Patents
Heizkörper für ein kraftfahrzeug mit einer brennkraftmaschineInfo
- Publication number
- EP2430385A1 EP2430385A1 EP10717165A EP10717165A EP2430385A1 EP 2430385 A1 EP2430385 A1 EP 2430385A1 EP 10717165 A EP10717165 A EP 10717165A EP 10717165 A EP10717165 A EP 10717165A EP 2430385 A1 EP2430385 A1 EP 2430385A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- coolant
- radiator
- box
- radiator according
- flow channels
- 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.)
- Granted
Links
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
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/0202—Header boxes having their inner space divided by partitions
- F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
- F28D2021/0091—Radiators
- F28D2021/0096—Radiators for space heating
Definitions
- the invention relates to a radiator for a motor vehicle according to the preamble of claim 1.
- Radiators that are operated in countercurrent for increased performance, d. H. in which the air to be heated is passed in countercurrent to the coolant, are known. Such a radiator was known from DE 44 31 107 C2. In the known countercurrent radiator, the coolant is deflected in one or more stages of the air outlet side in the direction of the air inlet side. This can be a higher heat transfer performance can be achieved.
- the disadvantage here is that the coolant must be distributed on the inlet side over the entire row of tubes, not all tubes are supplied evenly with coolant. As a result, a temperature stratification, i. H. occur over the width inhomogeneous temperature distribution.
- the coolant is distributed on the inlet side 20 to a number of flow channels (referred to below as channels for short) which corresponds at most to the number of channels in a row.
- the inlet cross section of the coolant in the radiator block thus amounts to a maximum of 25% of the cross section of all the flow channels ⁇ of the radiator block.
- the channels can be formed by 25 tubes, in particular flat tubes, wherein a flat tube as a two-chamber tube, d. H. can be formed with two discrete flow channels.
- the radiator then has two rows of flat tubes.
- the coolant is on the inlet side either to a single, d. H.
- the coolant is distributed on the inlet side on two rows of channels and then deflected at least once in the width in both cases arise on the inlet side a more uniform admission of the channels and an increase in performance.
- the coolant is then first or second time in the Depth deflected to be subsequently deflected again in width.
- the additional volume required by the known auxiliary heater is taken up by the radiator according to the invention.
- the latter thus does not take up more space than known radiators with electric heater. This frees the electrical system of the motor vehicle from an additional consumer.
- the heat contained in the coolant can thus be used to a greater extent for the heating of the passenger compartment of the motor vehicle.
- the smaller volumetric flows mean that the hose diameter and thus the coolant quantity can be reduced, which leads to faster heating of the coolant.
- the individual embodiments according to the invention each have a specific temperature profile at a very high heating power and thus offer the possibility of a special use in the air conditioning system of the motor vehicle. This can be used in different versions of the air conditioning on a matching radiator with an adapted temperature profile.
- FIG. 1 shows a heat exchanger designed as a radiator 1 for motor vehicles, which has two rows of flat tubes 2, 3 which are each designed as two-chamber tubes and each have two discrete flow channels 2a, 2b, 3a, 3b. Between the flat tubes 2, 3 (seen perpendicular to the plane) are not shown, designed as corrugated-pen secondary surfaces arranged, which are overflowed by air, represented by an arrow L 1 . Flat tubes and corrugated ribs form a radiator block.
- the flat tubes 2, 3 are accommodated in an upper coolant box 4 and a lower coolant box 5 at the end.
- the radiator 1 is preferably made entirely of aluminum materials, and all the items are soldered together.
- the flat tubes 2, 3 or their flow channels 2a, 2b, 3a, 3b are flowed through by a heating medium, for which purpose the coolant of the cooling circuit of the internal combustion engine of the motor vehicle is used.
- the radiator is arranged on the water side in a secondary circuit (H ⁇ izniklauf) of the cooling circuit.
- the heat contained in the coolant is thus used for the heating of the air, which is supplied to a vehicle interior of the motor vehicle, not shown.
- the invention thus relates to a so-called engine-dependent heating.
- the direction of flow L of the air is also referred to as the depth direction, ie a deflection of the coolant in or against the direction of the arrow L is referred to below as a deflection in the depth.
- a deflection of the coolant - in one or both cooling middle boxes 4, 5 - perpendicular to the plane of the drawing is referred to as a transversal width.
- longitudinal partitions 4a, 4b, 4c are provided, which allow a deflection of the coolant in the depth direction.
- a middle longitudinal partition wall 5a is arranged in the lower coolant box 5.
- the arrangement shown here of the partitions 4a, 4b, 4c, 5a is only an example, it does not apply in principle for the embodiments of the invention described below.
- Fig. 2, 2a show a first embodiment of the invention
- a horizontally arranged radiator 10 ie its flat tubes 12, 13, corresponding to the flat tubes 2, 3 shown in Fig. 1
- the inlet side coolant box 14 and the deflection box 15 are arranged vertically.
- the coolant box 14 is additionally shown in a plan view in Fig. 2a and has a longitudinal partition wall 14a and a transverse partition wall 14d, which limits the longitudinal partition wall 14a.
- a continuous longitudinal dividing wall 15a is arranged, which is shown partially in dashed lines.
- the flow direction of the air which flows through the radiator 10 is represented by arrows L.
- Inlet and outlet of the coolant are represented by arrows E, A.
- the coolant represented by the arrow E 1
- the flow direction of the coolant is represented in FIG. 2a by cross and point symbols, the cross symbol in the circle designating a flow direction perpendicular to the drawing plane and the dot symbol in the circle indicating a flow direction perpendicular to the plane of the drawing.
- the flow pattern of the coolant in FIG. 2 is identified by seven arrows S1 to S7, each perpendicular to one another. The coolant flows through the radiator 10 after the entry thus first according to the arrow S1, d.
- the coolant is deflected in the deflection box 5 over the entire width according to the arrow S2 and then flows through the radiator 10 over the full width in the opposite direction, ie according to the arrow S3.
- arrow S4 in the coolant box 14 a Umlenk ⁇ ng in the Depth, ie opposite to the air flow direction L.
- the following arrows S5, S6, S7 correspond to the flow arrows S1, S2, S3 in the reverse direction.
- the coolant is deflected once in the row of the flat tubes 12 in width, once in depth, and a second time in the row of the flat tube 13 in the width.
- FIG. 3a, 3b show a second embodiment of the invention for a standing arranged radiator 20, d. H. the flat tubes 22, 23 are arranged vertically.
- the radiator 20 has an upperdemiüelkas- th 24 for the lateral inlet and outlet of the coolant and a lower coolant box 25, which are each shown in Fig. 3a and Fig. 3b in a plan view with partitions and flow direction symbols.
- the upper coolant box 24 in FIG. 3 a has a continuous longitudinal dividing wall 24 a, as well as an eccentrically arranged transverse dividing wall 24 d.
- the lower coolant box 25 has a continuous longitudinal partition wall 25a and an eccentrically arranged transverse partition wall 25b.
- the partitions 24d, 25b are, as far as hidden, also shown in dashed lines.
- the flow profile of the coolant is shown in FIG. 3 by thirteen flow arrows S1 to S13. Thereafter, the coolant in the inlet and leeward pipe rows is deflected twice in width, after which, according to arrow S7, a deepening in the depth takes place in the windward outlet row. There, the coolant is also deflected twice in width according to the arrows S9 to S13.
- the coolant deposits a relatively wide path due to the total of fivefold deflection, which is advantageous, in particular, for small volume flows and low inlet temperature.
- Flg. 4, 4a, 4b show a third embodiment of the invention for a
- Flow pattern 30 The associated radiator is omitted here and in the following examples, it corresponds in principle Structure of the radiator 20 of FIG. 3. The only difference is the arrangement of the longitudinal and transverse partitions and partly the inlet and outlet of the coolant.
- the flow pattern 30 is characterized by flow arrows S1 to S11 adjoining one another, ie by a simple turn in the width in the first row of tubes, a subsequent deflection in the depth (arrow S5) and then a double deflection in the width in the second row of tubes.
- the upper coolant box 34 of the radiator not shown, is shown in Fig. 4a, the lower coolant box 35 in Fig. 4b.
- Fig. 5, ⁇ a, 5b show a fourth embodiment of the invention with a flow model 40 for the coolant, represented by arrows S1 to S12, ie from the inlet E to the outlet A of the coolant.
- the upper coolant box 44 shown in FIG. 5 a, has a non-continuous longitudinal partition wall 44 a, in whose non-continuous region a dot symbol 7 b, corresponding to the flow arrow S7 b in FIG. 5, is drawn.
- the lower coolant box 45 shown in Fig. 5b, also has a non-continuous longitudinal partition wall 45a, in the non-continuous region, a cross symbol S6a is located, which corresponds to the flow arrow S6a in Fig. 5.
- the longitudinal partitions are always in the middle, d. H. arranged between the two rows of flat tubes.
- the deflection of the coolant in the width is thus always within the flat tube row, d. H. parallel in two rows of channels.
- the longitudinal partitions are also off-center, d. H. arranged between two rows of channels - this allows the coolant to be better distributed over the entire width of the radiator.
- Figures 6, 6a, 6b show a fifth embodiment of the invention, shown as a flow model 50.
- Figure 6a. 6b show the upper coolant box 54 and the lower coolant box 55 of the heater, not shown.
- the coolant box 54 has a central, non-continuous longitudinal partition wall 54a and an off-center, continuous longitudinal partition wall 54b between the channels 52a, 52b of the flat tubes 52.
- the lower coolant box 55 has a centrally arranged, continuous longitudinal partition wall 55a.
- the coolant is distributed over the entire width of the coolant box 54 after the entry according to arrow E, but only in the row of the channels 52a.
- the lower coolant box 55 is then a deflection in depth, represented by two arrows T1 in Fig.
- FIG. 7a, 7b show a sixth embodiment of the invention, shown as Strömungsmod ⁇ ll 60.
- This embodiment corresponds essentially to the embodiment of FIG. 6 with the differences that the inlet and outlet of the coolant to a coolant box, namely the upper coolant box 64 are arranged and that takes place in the exit-side row of tubes only a simple deflection in width.
- the twofold deflections T1, T2 are thus in agreement with each other in the depth.
- 8a, 8b show a seventh embodiment of the invention in the form of a flow model 70, wherein the inlet E and the outlet A of the coolant takes place on opposite sides (narrow sides) of the upper coolant box 74.
- a first deflection takes place in the depth in the lower coolant box 75 as a result of the non-continuous partition wall 75 b.
- this deflection is shown as arrow T1.
- a second deflection in the depth takes place in the upper coolant box 74 due to the non-continuous longitudinal partition wall 74a, which is shown in FIG. 8 by the arrow T2.
- the deflections in the depths T1, T2 thus take place - as can be seen on the flow model 70 - on diagonally opposite regions of the radiator.
- FIG. 9a, 9b show an eighth embodiment of the invention in the form of a flow model 80, wherein the coolant inlet E and the coolant outlet A are respectively frontally, d. H. on the eliminate and windward longitudinal side of the upper coolant box 84, shown in Fig. 9a, takes place.
- a non-continuous, centrally arranged longitudinal partition wall 84a is provided here, which has cross-sections for deflection at depth on both sides-this is illustrated by the arrows T2 in FIG. The first deflection in the depth takes place in the lower coolant box 85 - represented in FIG. 9 by the arrows T 1.
- the coolant stream is therefore divided as a result of the non-continuous partition wall 84 a, ie. H. in the same part streams, which are simply deflected in each case on the outlet-side tube row and merged again in the central region of the outlet A.
- This flow mode 80 is distinguished by a particularly homogeneous temperature distribution across the width as a result of the symmetrical flow guidance.
- FIG. 10a, 10b show a ninth embodiment of the invention in the form of a flow model 90, wherein the coolant inlet E and the coolant outlet A in each case take place centrally on the longitudinal sides of the upper coolant box 94.
- the upper coolant box 94 has two eccentric continuous longitudinal web walls 94b, 94c.
- the lower coolant tank 95 shown in FIG. 1Ob 1 has a doubly interrupted, arranged off-center longitudinal partition wall 95c and a likewise arranged off-center, endseittg on non-continuous longitudinal partition wall 95b. In this respect, it comes in the lower coolant tank 95 to a first two-sided deflection in depth, shown in Fig. 10 by the two arrows T1.
- the incoming coolant flow is thus divided by the outer deflections in depth, then each deflected simply in width, reunited in the middle and then divided again and deflected in depth - this is shown schematically in Fig. 10 by the two arrows T2
- the coolant streams be in the last, luv computer located channel row in the upper coolant box 95 in the area of the outlet A merged again.
- the advantages are a homogeneous temperature distribution in the width as well as long flow paths, which allow a high heat emission of the coolant to the air.
- FIG. 11a shows the upper coolant box 104, which has two off-center continuous partition walls 104b, 104c.
- 11b shows the lower coolant box 105, which has two off-center, non-continuous partitions 105b, 105c.
- the coolant is first distributed over the entire width of a channel row after entry and then deflected in the depth - represented by the arrow T1 in Fig. 11 -.
- the exit of the coolant takes place - analogous to the entrance - over the entire width of a channel row.
- FIG. 12a shows the upper coolant box 114 with coolant inlet according to arrow E.
- FIG. 12b shows the lower coolant box 115 with coolant outlet according to arrow A.
- a twofold deflection takes place in the width, followed by a deflection in the depth, represented by the arrow T1 in FIG 12, then a further deflection in depth according to arrow T2 in Fig. 12.
- the exit ofmémitte is via the luv soup ⁇ channel row.
- FIGS. 13a, 13b show the upper coolant box 124 with coolant inlet E and coolant outlet A and the lower coolant box 125.
- the coolant inlet E takes place initially in the leeward row of flat tubes a simple deflection in the width, then a deflection in the depth - according to arrow T1 in Fig. 13 - then a distribution of the coolant to a channel row and a second deflection in depth, according to arrow T2 in Fig. 13.
- the outlet A of Coolant takes place from the windward channel row.
- Flg. 14, 14a, 14b show a thirteenth embodiment of the invention, shown as flow model 130.
- Figs. 14a, 14b show the upper one
- Coolant box 134 with coolant inlet E and coolant outlet A and the lower coolant box 135.
- the coolant is simply deflected in width after entering the leeward flat tube row, then in depth, according to arrow T1 in Fig. 14, deflected and on a channel row distributed in full width. Subsequently, a second deflection takes place in the depth corresponding to the two arrows T2 in Fig. 14 and the outlet of the coolant from the windward channel row.
- FIG. 15a shows the upper coolant box 144 with coolant inlet E and coolant outlet A
- FIG. 15b shows the lower coolant box 145.
- the coolant is distributed after entry over the entire width of the leeward channel row, then deflected outwardly in the lower collection box 145 in depth, according to the arrow T1 in Fig. 15, and distributed over the remaining three rows of channels. Subsequently, a twofold Umtenkung in width over three rows of channels, which are traversed parallel to each other.
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)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009020711A DE102009020711A1 (de) | 2009-05-11 | 2009-05-11 | Heizkörper für ein Kraftfahrzeug mit einer Brennkraftmaschine |
PCT/EP2010/056208 WO2010130635A1 (de) | 2009-05-11 | 2010-05-06 | Heizkörper für ein kraftfahrzeug mit einer brennkraftmaschine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2430385A1 true EP2430385A1 (de) | 2012-03-21 |
EP2430385B1 EP2430385B1 (de) | 2016-07-13 |
Family
ID=42542801
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10717165.4A Not-in-force EP2430385B1 (de) | 2009-05-11 | 2010-05-06 | Heizkörper für ein kraftfahrzeug mit einer brennkraftmaschine |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP2430385B1 (de) |
DE (1) | DE102009020711A1 (de) |
WO (1) | WO2010130635A1 (de) |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3030036B2 (ja) * | 1989-08-23 | 2000-04-10 | 昭和アルミニウム株式会社 | 複式熱交換器 |
DE4431107C2 (de) * | 1994-09-01 | 2000-11-09 | Johann Himmelsbach | Wärmetauscheranordnung zur Beheizung der Kabine von Kraftfahrzeugen mit der Abwärme des Antriebsmotors |
DE19833845A1 (de) * | 1998-07-28 | 2000-02-03 | Behr Gmbh & Co | Wärmeübertrager-Rohrblock und dafür verwendbares Mehrkammer-Flachrohr |
DE10143092A1 (de) * | 2001-09-03 | 2003-03-20 | Att Automotivethermotech Gmbh | Gegenstromwärmetauscher mit thermischer Schichtung zur Kabinenbeheizung von Kraftfahrzeugen |
JP2004077079A (ja) * | 2002-08-21 | 2004-03-11 | Showa Denko Kk | 熱交換器、その製造方法、熱交換器用ヘッダータンクのチューブ接続構造及び冷凍システム |
DE10247609B4 (de) | 2002-10-11 | 2022-04-28 | Johann Himmelsbach | Heizungsvorrichtung für Kraftfahrzeuge mit einem Kabinenheizkreislauf |
JP4413047B2 (ja) * | 2004-03-17 | 2010-02-10 | 株式会社日本クライメイトシステムズ | 熱交換器 |
DE102005048227A1 (de) | 2005-10-07 | 2007-04-12 | Behr Gmbh & Co. Kg | Heizkörper, Kühlkreislauf, Klimagerät für eine Kraftfahrzeug-Klimaanlage sowie Klimaanlage für ein Kraftfahrzeug |
DE102008055624A1 (de) * | 2007-12-10 | 2009-06-18 | Behr Gmbh & Co. Kg | Wärmeträger, insbesondere Heizkörper für Kraftfahrzeuge |
-
2009
- 2009-05-11 DE DE102009020711A patent/DE102009020711A1/de not_active Withdrawn
-
2010
- 2010-05-06 EP EP10717165.4A patent/EP2430385B1/de not_active Not-in-force
- 2010-05-06 WO PCT/EP2010/056208 patent/WO2010130635A1/de active Application Filing
Non-Patent Citations (1)
Title |
---|
See references of WO2010130635A1 * |
Also Published As
Publication number | Publication date |
---|---|
DE102009020711A1 (de) | 2010-11-18 |
EP2430385B1 (de) | 2016-07-13 |
WO2010130635A1 (de) | 2010-11-18 |
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