EP2232183A2 - Wärmeübertrager, insbesondere heizkörper für kraftfahrzeuge - Google Patents
Wärmeübertrager, insbesondere heizkörper für kraftfahrzeugeInfo
- Publication number
- EP2232183A2 EP2232183A2 EP08859570A EP08859570A EP2232183A2 EP 2232183 A2 EP2232183 A2 EP 2232183A2 EP 08859570 A EP08859570 A EP 08859570A EP 08859570 A EP08859570 A EP 08859570A EP 2232183 A2 EP2232183 A2 EP 2232183A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- row
- heat exchanger
- region
- coolant
- flow
- 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
- 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
- F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
-
- 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
- Heat exchangers in particular radiators for motor vehicles
- the invention relates to a heat exchanger according to the preamble of patent claim 1.
- Heat exchangers in particular radiators for motor vehicles, are flowed through on the primary side by a liquid medium, in particular coolant, and are acted upon by ambient air on the secondary side, which is supplied to the vehicle cabin.
- Known radiators have an existing of pipes and ribs block in which enters the air to be heated and exits on the back again.
- a problem with the heating of the air in the radiator block is that the air outlet temperatures on the air outlet surface are not the same everywhere, so that strands of different air temperature occur in the heated air. This is disadvantageous for a targeted heating of the interior.
- a radiator which is usually formed in a multi-row or multi-flow
- different flow patterns are known, whereby the simplest form is a parallel flow, in which all tubes are flowed through in the same direction.
- a U-shaped flow through the radiator wherein in a coolant box, a partition wall (transverse partition wall) is arranged. Since this deflection of the coolant takes place transversely to the direction of air flow, it is called a deflection "in the width.”
- coolant and Air one speaks here of a cross current.
- the coolant cools down, so that the air is heated more strongly on the inlet side radiator half than on the outlet side half, which leads to the mentioned strandiness.
- a longitudinal partition is required, which separates adjacent rows on one side.
- deflection in the depth
- this is referred to as direct current or countercurrent
- the coolant must be distributed over the full width on the inlet side - this can cause the outer tubes to flow through more slowly when the coolant enters the center, which also adversely affects the air outlet temperature.
- a radiator in which the coolant is deflected exclusively in the width, specifically in several stages, wherein a plurality of coolant flows are connected in parallel.
- the aim of this arrangement is to achieve relatively large pressure losses by turbulence of the coolant at the deflection of the water boxes.
- a radiator for motor vehicles which operates on the countercurrent principle.
- the coolant is deflected in one or more stages from the air outlet side in the direction of the air inlet side. This can be a higher heat transfer performance can be achieved.
- DE 603 06 291 T2 corresponding to EP 1 410 929 B1
- a radiator for motor vehicles with a separate control for the right and the left side of the cabin (driver side and passenger side) was known.
- the coolant is supplied via two pre-runs, deflected in width to the middle and discharged there through a common return.
- a deflection in the depth is provided, namely against the direction of air flow.
- the air flow exiting the radiator is split by a dividing wall into two partial flows, which are fed to the left and right side of the cabin.
- the liquid medium enters a first region, the inlet region, and is deflected within this air outlet side series into a second region, wherein both the first region and the second region can have partial regions.
- the coolant entering the first row of flow channels is deflected at least once in width.
- the coolant is deflected from the first to the second, ie the air inlet side row, wherein all the flow channels of the second row are flowed through in the same direction.
- the coolant is also in the second, d. H. the windward row at least once deflected. Overall, the coolant flow is thus deflected twice in width and once in depth. Due to the opposing flow of coolant in both rows of tubes, the air outlet temperature profile can be homogenized even more.
- the entry region in the first row is arranged centrally, while the second region comprises two sub-regions, which are arranged symmetrically next to the first region.
- the incoming coolant stream is thus divided after the first pass and deflected in opposite directions in the width of the heat exchanger.
- the coolant flows exiting from the two partial areas are deflected in the depth and distributed to the second row in such a way that all flow channels are flowed through in the same direction.
- This achieves a symmetrical air outlet temperature profile, i. H. Any deviations from a homogeneous temperature distribution occur symmetrically. Alternatively it can be deflected in the second row in the width.
- the entry region in the first row is arranged eccentrically, preferably in a first half, while the second region is arranged next to the first region.
- the coolant flows into the heat exchanger in the first half of the row, is deflected in width, and the entire coolant flow enters the second area. From there, in turn, the deflection in the depth and the distribution of the coolant flow to the entire second row, which can be flowed through in the same direction or in different directions.
- two, preferably symmetrically arranged inlet regions are provided, which communicate with each other via a connecting pipe. This gives two partial flows on the inlet side, which are deflected inwards in width and enter the second region. Thereafter, the diversion in the depth and the distribution of the coolant take place on all tubes of the second row.
- the width can also be deflected in the second row.
- the flow cross sections of the first and second regions are the same, i. H.
- the same flow velocities occur in the flow channels of the first and second regions, ie. H. seen across the entire width.
- the flow cross section of the second region is particularly preferably greater than that of the first region, with the result that there is a delay in the flow in the flow channels of the second region. This compensates for the cooling of the liquid medium, so that a homogeneous air outlet temperature distribution is obtained as an advantage.
- the flow cross section of the second row is adapted to the flow cross section of the second region of the first row, in such a way that the entire flow cross section of the second row is either equal to or greater than the entire flow cross section of the second region.
- an expansion of the flow cross-section due to the further cooling of the liquid medium, an expansion of the flow cross-section.
- either the same flow rate in the second row as in the second range can be achieved or a delay of the flow - with the result that more heat can be released into the air and a lower pressure drop occurs.
- an extension of the flow cross-section can be carried out with the result of a reduced flow velocity.
- the heat exchanger is designed as a radiator of a heating system for motor vehicles, d. H.
- the flow channels are designed as tubes, preferably as flat tubes or multi-chamber tubes, through which the coolant flows and between which corrugated ribs are preferably arranged as secondary surfaces.
- the flat tube sections of the second row - depending on the flow pattern - the same, a greater or lesser depth than the Flat tubes of the first row on.
- a greater cooling of the coolant and thus a higher heat transfer performance can be achieved.
- the radiator according to the invention preferably comprises headers or containers, d. h an inlet box, via which the coolant enters, an outlet box, via which the coolant exits, or a coolant inlet and outlet box or a deflection box.
- partitions in the form of longitudinal and / or transverse dividing walls are arranged in the collecting boxes, which subdivide the collecting boxes into individual chambers.
- the inlet region for the flow channels or flat tubes of the first region is preferably divided by a longitudinal dividing wall and at least one transverse dividing wall within the inlet box.
- the outlet box has a longitudinal dividing wall, so that the first and the second row are separated from one another and in the first row, a deflection in the width can take place.
- transverse and longitudinal partitions may be arranged in an H-shaped manner.
- FIG. 1 shows the flow through a heat exchanger block with a central inlet region as the first embodiment of the invention
- FIG. 2 shows the flow model according to FIG. 1 in a schematic view from above
- FIG. 1 shows the flow through a heat exchanger block with a central inlet region as the first embodiment of the invention
- FIG. 2 shows the flow model according to FIG. 1 in a schematic view from above
- FIG. 1 shows the flow through a heat exchanger block with a central inlet region as the first embodiment of the invention
- FIG. 2 shows the flow model according to FIG. 1 in a schematic view from above
- Fig. 3 shows a second embodiment of the invention with off-center entry area
- 4 shows a third embodiment of the invention with two entry areas
- a radiator with "double" deflection in the width that is, in the first and second row, Fig. 9a, the radiator according to Fig. 8 in an exploded view
- Fig. 12 as a further embodiment of the invention, a radiator with outer inflow.
- Fig. 1 shows a schematic representation of a first embodiment of the invention, namely a flow model for a double-row radiator 1, of which only tubes 2 (without ribs) of a first row 3 and a second row 4 are shown.
- a longitudinal partition wall 5 with two transverse partition walls 6, 7 in the inlet region of the tubes 2 and a further, continuous longitudinal partition 8 in the lower region of the block 1 are partially shown.
- the tubes 2 are, as indicated by flow arrows, flows through a coolant, which is branched off from a cooling circuit, not shown, of an internal combustion engine of a motor vehicle.
- the radiator block 1 is used to heat air, which flows through the block 1 according to the arrow L and not shown ribs between the tubes 2, so-called secondary surfaces, overflowed.
- the heated air is supplied to the cabin of the motor vehicle.
- the first row 3 of the radiator block 1, also referred to below as block 1 for short, is subdivided into three regions due to the partitions 5, 6, 7, a first region 9 being contained within the partitions 5, 6, 7 and a second region 10 two partial areas 10a, 10b, on both sides of the transverse partition walls 6, 7 are arranged.
- the first region 9, also called inlet region comprises four tubes 2, while the two partial regions 10a, 10b each comprise two tubes 2.
- the coolant enters the tubes 2 via the inlet region 9 according to the arrows E and flows through them from top to bottom (the terms above and below refer to the illustration in the drawing).
- the coolant flow is divided, in each case to the outside - within the first row 3 - deflected and then enters the tubes 2 of the portions 10 a, 10 b to flow through them from bottom to top.
- the deflection of the coolant is indicated by the arrows UB, UB means deflection in width.
- the two diverted in the depth of coolant partial flows are distributed to all tubes 2 (in the illustrated embodiment 8) of the second row 4 and flow through this from top to bottom.
- the deflection of the coolant in the width corresponding to the arrows UB is through the continuous longitudinal partition wall 8 - in conjunction with a coolant box, not shown, as shown in the following Fig. 6a, 6b - allows.
- the flow pattern described above corresponds to a cross-counterflow, based on coolant and air flow.
- the first row 3 is the air outlet-side row, also referred to below as the leeward row
- the second row of tubes 4 is the air inlet-side row, also referred to below as the windward row.
- the coolant thus enters the leeward row 3 in the block 1, is first deflected in width and then in depth, with all the tubes 2 of the windward row 4 are flowed through in the same direction.
- This flow through the radiator block 1 causes a largely homogeneous Air outlet temperature, ie after the exit of the air from the first row 3.
- Fig. 2 shows a schematic representation of the radiator block 1 according to FIG. 1 in a view from above of the tubes 2, which are arranged in the two rows 3 and 4.
- the air flow direction is again indicated by an arrow L.
- the flow direction of the coolant is represented by dot symbols 11 and cross symbols 12, wherein the dot symbols 11 represent an upward flow direction (out of the drawing plane) and the cross symbols represent a coolant flow downward, ie into the drawing plane.
- the tubes 2 of the inlet region 9 are marked with a clamp a, the tubes 2 of the two partial regions 10a, 10b with clamps b1, b2 and the tubes 2 of the series 4 with a clamp c.
- the letters a, b1, b2, c stand for the respective number of tubes.
- the cross sections of the tubes 2 are formed as flat tube cross sections and each have a depth T1 in the first row 3 and a depth T2 in the second row 4.
- the entire depth of the block 1 is marked T.
- the relationship a ⁇ (b1 + b2) holds.
- b1 + b2 a
- the same flow velocity for the coolant as in the tubes 2 of the inlet region 9 results in the tubes 2 of the outer subregions 10a, 10b.
- the flow cross section for the second area but slightly enlarged, so that a delay of the coolant flow is achieved. This also contributes to a homogenization of the air outlet temperature profile.
- the preferred depth dimension T2 for the second row 4 is in the range between 0.5 T1 and T1.
- the described flow model with deflections in the width and in the depth thus offers the possibility of gradually reducing the flow velocity of the coolant by changing the flow cross sections.
- Fig. 2a shows two equivalent embodiments for the aforementioned and illustrated tubes 2, each having a flat tube cross-section. In principle, it is possible to use separate tubes 2 in different rows (two-row design) or to use a two-chamber tube 2 ', ie a tube with two chambers (single-row construction).
- Fig. 3 shows a second embodiment of the invention, wherein like reference numerals are used for like parts.
- the block 1 again has two rows 3, 4 of flat tubes 2, the first row 3 being subdivided into a first area 13, the entry area, and a second area 14.
- the inlet region 13 is divided by a longitudinal partition wall 15 and a transverse partition wall 16.
- the coolant enters according to the arrows E in the tubes 2 of the inlet region 13, is then according to the arrows UB in the width, d. H. deflected within the row 3 and then flows through the tubes 2 of the second region 14 from bottom to top.
- the coolant is deflected in the depth, corresponding to the arrows UT and distributed to all tubes 2 of the second row 4, which are all flowed through in the same direction from top to bottom. Thereafter, the coolant exits the block 1. Even with this flow pattern results in a homogeneous air outlet temperature profile.
- Fig. 4 shows a third embodiment of the invention, wherein in turn identical reference numerals are used for the same parts.
- a first region 17 with two outer subregions 17a, 17b and a middle second region 18 are provided here.
- the partial areas 17a, 17b are each divided by longitudinal dividing walls 19a, 19b and by transverse dividing walls 20a, 20b, between which a connecting tube 21 is arranged.
- the coolant enters according to the arrows E - partly via the connecting pipe 21 - in the tubes 2 of the portions 17a, 17b, flows through them from top to bottom, then, according to the arrows UB, deflected in width and flows through the middle tubes.
- the second area 18 is then deflected in the depth and distributed to all the tubes 2 of the second row 4, which are then flowed through from top to bottom in the same direction.
- This stream pattern ensures a largely homogeneous air outlet temperature profile.
- the radiator 22 comprises a radiator block 23, also called a block for short, a lower header or coolant box 24 and an upper header or coolant box 25.
- the lower header 24 has an inlet nozzle 24a and the upper coolant box, also called outlet box, has a Outlet nozzle 25a on.
- the block 23 comprises - as shown and explained in the embodiment of FIG. 1 and FIG.
- the arrow I symbolizes the incoming coolant flow in the first region
- the arrows IIa, IIb symbolize the diverted in width partial streams
- the arrow III symbolizes the coolant flow in the second, ie the windward tube row.
- the arrows UB, UT show the deflection of the coolant flow I in the width and the deflection of the partial flow IIb in depth.
- the direction of flow of the air is shown by an arrow L, that is, one looks at the air outlet side of the radiator block 23.
- the installation position of the radiator 22 with the above-arranged coolant outlet 25a is selected because of the better ventilation of the radiator 22.
- Fig. 5b shows the radiator 22 in an exploded view, ie the lower inlet box 24, the upper outlet box 25 and the block 23 are shown separately.
- the interior of the inlet box 24, in particular the inlet region 26 divided off by a longitudinal and two transverse partition walls 26a, 26b, 26c, can be seen.
- the coolant inlet stream is shown in block 23 by three arrows pointing upwards.
- the deflection in the width is carried out according to the arrows UB (here, a non-visible longitudinal partition wall is arranged in the upperdemit- telkasten 25).
- the diversion kung in depth takes place in the lower coolant box 24 according to the arrows UT.
- the flow in the windward row is indicated by five arrows pointing upwards.
- FIG. 6a and FIG. 6b again show the heating element 22 according to FIGS. 5a, 5b in an exploded view, namely in FIG. 6a with a view of the air outlet side 23a and in FIG. 6b with a view of the air inlet side 23b.
- the flow direction of the air is represented by arrows L.
- the same reference numerals are used for the same parts. From this representation, the different flow on the lee side 23a and on the windward side 23b of the radiator block 23 becomes clear. In the former case, a coolant flow takes place in opposite directions, in the second case in the same direction.
- FIG. 6 b shows a longitudinal dividing wall 27 which corresponds to the longitudinal dividing wall 8 in the exemplary embodiments according to FIGS. 1 to 4.
- Fig. 7a shows a view from above of the radiator block 23 according to Fig. 5a to Fig. 6b.
- the block 23 has two rows 28, 29 of two-chamber tubes 30, 31.
- the flow direction of the coolant is again represented by dot and cross symbols.
- the air flow direction is indicated by an arrow L.
- Fig. 7b shows a view of the radiator block 23 from below with first row of tubes 28 and second row of tubes 29 and with the inlet region 26 (first area) and partitions 26a, 26b, 26c.
- the number of tubes in the individual areas, ie in the first and second area and in the second row 29 are represented by the dimension arrows a, b1, b2, c.
- the number of tubes shown in the drawing or the dimensional ratios correspond to a preferred embodiment.
- fifteen tubes 30 are provided in the first region a, and nine tubes in the second regions b1, b2, respectively.
- Fig. 7c shows the tubes 30, 31 of the first row 28 and the second row 29 in an enlarged view, wherein the depth dimensions T1 for the tubes 30 and T2 apply to the tubes 31 and T for the entire block depth.
- the width of the tubes is indicated by B.
- the graphical representation is to scale for a preferred embodiment, i. H.
- the depth dimension T2 of the second row 29 is smaller than the depth dimension T1 of the first row 28.
- the number of tubes 30, 31 in both rows 28, 29 is - as the figures 7a, 7b show - the same.
- the entire flow cross section of the tubes 31 in the second row 29 is dimensioned such that, after the deflection in the depth, a further delay of the coolant flow results. Thus one reaches on the air inlet side an increased temperature difference and thus a performance gain.
- the depth measure T2 is selected in a range of 0.5 T1 to 1, T1.
- the radiator according to the invention or its flat tubes have the following dimensions:
- the tube width B is in a range of 0.5 to 4.0 mm, preferably in a range of 0.8 to 2.5 mm.
- the material thickness (tube wall thickness) s of the flat tubes is in a preferred range of 0.10 to 0.50 mm.
- the depth T of the block is in a range of 10 to 100 mm, preferably in a range of 20 to 70 mm.
- stepwise expansion of the flow cross section in each case after the deflection in the width and / or the deflection in depth, results in connection with the delay of the coolant flow and a lower pressure drop on the coolant side, which reduces the power requirement for the coolant pump ,
- Fig. 8 shows a further embodiment of the invention in the form of a double-row radiator 32 in which the coolant is deflected in width both in the first and in the second row of tubes.
- the entry of the coolant into the radiator 32 is indicated by an arrow E and the output enters the coolant from the radiator 32 is indicated by an arrow A.
- the direction of flow of the air through the radiator 32 is indicated by two arrows L, ie air and coolant are guided in cross-counterflow to each other.
- the radiator 32 has a first, leeward pipe row 33 and a second windward pipe row 34 and an upper coolant box 35 and a lower coolant box 36, in which open the (not provided with reference numbers) pipe ends.
- the coolant first enters an inlet region, represented by arrows I, into the first row of tubes 33, is deflected outwards in the lower coolant box 36, corresponding to the arrows UB in width, enters the two outer sections, flows through them down to the top, according to the arrows IIa, IIb, and is in the upper coolant box 35 in the depth, corresponding to the arrows UT, deflected.
- windward pipe row 34 there is a flow from top to bottom - which is not shown here - a new deflection in the width, a flow from bottom to top and finally marked by the arrow A outlet of the coolant.
- the regions I, IIa, IIb in the front and in the rear row 33, 34 are respectively flowed through in opposite directions.
- Fig. 9a shows the heating element 32 of Fig. 8 in an exploded view, wherein the same reference numerals are used for the same parts.
- the flow of the coolant is represented by arrows in the tubes and the coolant boxes 35, 36.
- the two rows of tubes 33, 34 have a plurality of flat tubes 37, between which are not provided with reference numbers corrugated fins are arranged.
- the ends of the flat tubes 37 are connected to tube sheets 38, 39, preferably by soldering.
- the tube plates 38, 39 are connected to the coolant boxes 35, 36, preferably by soldering.
- a longitudinal partition wall 40 is arranged, which separates the first and the second row of tubes 33, 34, so that in the lower coolant box 36 each for the first and second row of tubes 33, 34 can be made a deflection in width, as by the Arrows UB1, UB2, each can take place in the opposite direction.
- the upperdeffenkas- th 35 are two extending over both rows of tubes transverse partitions 41, 42 and arranged between the transverse partition walls 41, 42 extending longitudinal partition wall 43. Due to this arrangement of the partitions 40, 41, 42, 43 results in the flow pattern of the coolant shown by the arrows.
- the coolant flows in the first and second rows 33, 34 respectively in the opposite direction, as well as in the lower coolant box 36.
- the first row 33 a deflection in the width from inside to outside
- the second row 34 a deflection in width from the outside to the inside.
- Fig. 9b shows the radiator 32 in a section in which the two rows of tubes 33, 34, the two coolant boxes 35, 36, the entry of the coolant by an arrow E, the exit of the coolant by an arrow A and the flow direction of the air through an arrow L are shown.
- the countercurrent principle is clearly visible here.
- FIG. 10a shows a plan view (view from above) of the two rows of tubes 33, 34, here called R1, R2.
- the two transverse partitions 41, 42 in conjunction with the longitudinal partition wall 43 in the form of an H.
- the flow direction of the coolant through the flat tubes 37 is represented by dot and cross symbols.
- the number of tubes in the individual sections of the rows of tubes R1, R2 is represented by the sections a, b1, b2, c.
- the sum of the tubes b1 and b2 is greater than the number of tubes a, ie (b1 + b2)> a.
- the section a has fifteen tubes and the sections b1 and b2 each have nine tubes, resulting in an increase of the flow cross section around three tube cross sections. This results in a reduction of the flow velocity in sections b1 and b2.
- Fig. 10b shows a bottom view of the tube ends of the rows of tubes R1 and R2, between which the longitudinal partition wall 40 is arranged.
- the entire width of the rows of tubes R1, R2 is indicated by c - this area is not divided by transverse walls, so that in both rows R1, R2 a deflection in the width can be made.
- 10c shows an enlarged section of the two rows of tubes R1, R2, each with five flat tubes 37a, 37b, the depth of which (in the direction of air flow) is defined by T1 and T2 respectively.
- the total depth of the two rows of tubes (the block) is indicated by T.
- the depth T2 of the flat tubes 37b can be greater than the depth T1 of the flat tubes 37a are selected - this with the same tube width B and the same number of tubes.
- the tube width B is in a range of 0.5 to 4.0 mm, preferably 0.8 to 2.5 mm.
- the material thickness of the flat tubes 37a, 37b is in the range of 0.10 to 0.50 mm.
- the overall depth T (mesh or block depth) is 10 to 100 mm, preferably 25 to 70 mm.
- two rows of flat tubes 37a, 37b, which are designed as two-chamber tubes, are shown. However, it is also possible to use multi-chamber pipes or else a single-row construction with a continuous flat tube which has a partition (sipe) approximately in the central area.
- FIG. 11 shows a further exemplary embodiment of the invention with a heating body 44, which corresponds to the flow pattern of the exemplary embodiment according to FIGS. 10a, 10b.
- a constructive variant provides for a lateral inflow of the coolant via an inflow pipe 45, via which the coolant is supplied from the outside into the central inflow region 46.
- an outflow pipe (not shown) can be provided for the outflow region located downstream of the inflow region 46 in the plane of the drawing. be provided.
- Such a laterally arranged coolant connection may be advantageous due to the installation situation in the vehicle.
- FIG. 12 shows a further exemplary embodiment of the invention with a heating body 47 which has outflow regions 48, 49 arranged outside (partial regions) which communicate with each other via a connecting tube 50.
- the coolant entering via the inlet connection 51 is thus distributed to both inflow chambers 48, 49.
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- 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)
- Air-Conditioning For Vehicles (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102007059672 | 2007-12-10 | ||
DE102008017485 | 2008-04-03 | ||
PCT/EP2008/009271 WO2009074196A2 (de) | 2007-12-10 | 2008-11-04 | Wärmeübertrager, insbesondere heizkörper für kraftfahrzeuge |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2232183A2 true EP2232183A2 (de) | 2010-09-29 |
EP2232183B1 EP2232183B1 (de) | 2018-09-12 |
Family
ID=40637243
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP08859570.7A Not-in-force EP2232183B1 (de) | 2007-12-10 | 2008-11-04 | Wärmeübertrager, insbesondere heizkörper für kraftfahrzeuge |
Country Status (5)
Country | Link |
---|---|
US (1) | US8695689B2 (de) |
EP (1) | EP2232183B1 (de) |
CN (1) | CN101889186A (de) |
DE (1) | DE102008055624A1 (de) |
WO (1) | WO2009074196A2 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2430385B1 (de) * | 2009-05-11 | 2016-07-13 | MAHLE Behr GmbH & Co. KG | Heizkörper für ein kraftfahrzeug mit einer brennkraftmaschine |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102009021796A1 (de) * | 2009-05-18 | 2010-11-25 | Behr Gmbh & Co. Kg | Verschaltung zweier Heizkörper zu einem Hochleistungskörper |
DE102010043000A1 (de) | 2010-10-27 | 2012-05-03 | Behr Gmbh & Co. Kg | Kraftfahrzeugklimaanlage |
CN102278899A (zh) * | 2011-05-30 | 2011-12-14 | 广州迪森家用锅炉制造有限公司 | 用于燃气采暖热水炉的翅管式主换热器及其制造方法 |
US9664450B2 (en) | 2013-04-24 | 2017-05-30 | Dana Canada Corporation | Fin support structures for charge air coolers |
CN103673233B (zh) * | 2013-12-24 | 2017-05-17 | 上海三意自动化控制工程有限公司 | 一种新风热回收装置 |
JP2015157507A (ja) * | 2014-02-21 | 2015-09-03 | 株式会社ケーヒン・サーマル・テクノロジー | 車両用空調装置 |
JP6547695B2 (ja) * | 2016-06-21 | 2019-07-24 | 株式会社デンソー | 冷凍サイクル装置 |
US10746037B2 (en) | 2016-11-30 | 2020-08-18 | Rolls-Royce Corporation | Turbine shroud assembly with tandem seals |
DE102021118138A1 (de) | 2021-07-14 | 2022-05-19 | Audi Aktiengesellschaft | Kühlmittelkühler für ein Kraftfahrzeug sowie entsprechendes Kraftfahrzeug |
DE102022207924A1 (de) | 2022-08-01 | 2024-02-01 | Mahle International Gmbh | Wärmeübertrager |
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US1993095A (en) | 1932-04-19 | 1935-03-05 | Albert S Heinrich | Radiator |
FR1265756A (fr) * | 1960-08-24 | 1961-06-30 | Daimler Benz Ag | échangeur de chaleur, notamment destiné à chauffer l'air de la cabine réservée aux passagers de véhicules automobiles |
DE3813339C2 (de) | 1988-04-21 | 1997-07-24 | Gea Happel Klimatechnik | Wärmetauscher für Kraftfahrzeuge und Verfahren zu seiner Herstellung |
US5186248A (en) * | 1992-03-23 | 1993-02-16 | General Motors Corporation | Extruded tank condenser with integral manifold |
US5205347A (en) * | 1992-03-31 | 1993-04-27 | Modine Manufacturing Co. | High efficiency evaporator |
DE4239739A1 (de) * | 1992-11-26 | 1994-06-01 | Behr Gmbh & Co | Heizkörper für ein Kraftfahrzeug |
DE4309360C2 (de) | 1993-03-23 | 1995-06-22 | Thermal Waerme Kaelte Klima | Heizungswärmetauscher für Kraftfahrzeuge |
JPH0763492A (ja) * | 1993-08-30 | 1995-03-10 | Sanden Corp | 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 |
US5622219A (en) * | 1994-10-24 | 1997-04-22 | Modine Manufacturing Company | High efficiency, small volume evaporator for a refrigerant |
JPH09280755A (ja) | 1996-04-18 | 1997-10-31 | Sanden Corp | 多管式熱交換器 |
US5941303A (en) * | 1997-11-04 | 1999-08-24 | Thermal Components | Extruded manifold with multiple passages and cross-counterflow heat exchanger incorporating same |
DE19800487A1 (de) | 1998-01-09 | 1999-07-15 | Vasco Nv | Röhrenheizkörper mit innerem Rohr |
FR2780152B1 (fr) * | 1998-06-23 | 2001-03-30 | Valeo Climatisation | Echangeur de chaleur pour vehicule automobile, et son procede de fabrication |
FR2803378B1 (fr) * | 1999-12-29 | 2004-03-19 | Valeo Climatisation | Echangeur de chaleur a tubes a plusieurs canaux, en particulier pour vehicule automobile |
JP2003063239A (ja) * | 2001-08-29 | 2003-03-05 | Denso Corp | 車両用空調装置 |
DE10143092A1 (de) * | 2001-09-03 | 2003-03-20 | Att Automotivethermotech Gmbh | Gegenstromwärmetauscher mit thermischer Schichtung zur Kabinenbeheizung von Kraftfahrzeugen |
KR20050037407A (ko) | 2001-10-17 | 2005-04-21 | 쇼와 덴코 가부시키가이샤 | 증발기 및 이를 구비한 냉동 사이클이 제공된 차량 |
DE10247609B4 (de) | 2002-10-11 | 2022-04-28 | Johann Himmelsbach | Heizungsvorrichtung für Kraftfahrzeuge mit einem Kabinenheizkreislauf |
JP3982379B2 (ja) | 2002-10-15 | 2007-09-26 | 株式会社デンソー | 熱交換器 |
DE10257767A1 (de) * | 2002-12-10 | 2004-06-24 | Behr Gmbh & Co. Kg | Wärmeübertrager |
US7222501B2 (en) * | 2002-12-31 | 2007-05-29 | Modine Korea, Llc | Evaporator |
DE10312780A1 (de) * | 2003-03-21 | 2004-11-25 | Behr Gmbh & Co. Kg | Wärmetauscher |
DE102004005621A1 (de) | 2004-02-04 | 2005-08-25 | Behr Gmbh & Co. Kg | Vorrichtung zum Austausch von Wärme und Verfahren zur Herstellung einer derartigen Vorrichtung |
US7080683B2 (en) * | 2004-06-14 | 2006-07-25 | Delphi Technologies, Inc. | Flat tube evaporator with enhanced refrigerant flow passages |
DE102005048227A1 (de) | 2005-10-07 | 2007-04-12 | Behr Gmbh & Co. Kg | Heizkörper, Kühlkreislauf, Klimagerät für eine Kraftfahrzeug-Klimaanlage sowie Klimaanlage für ein Kraftfahrzeug |
US20080023182A1 (en) * | 2006-07-25 | 2008-01-31 | Henry Earl Beamer | Dual mode heat exchanger assembly |
FR2914407B1 (fr) * | 2007-03-30 | 2009-12-11 | Valeo Systemes Thermiques | Evaporateur perfectionne pour circuit de refroidissement de vehicule automobile |
-
2008
- 2008-11-03 DE DE102008055624A patent/DE102008055624A1/de not_active Withdrawn
- 2008-11-04 WO PCT/EP2008/009271 patent/WO2009074196A2/de active Application Filing
- 2008-11-04 EP EP08859570.7A patent/EP2232183B1/de not_active Not-in-force
- 2008-11-04 CN CN2008801207115A patent/CN101889186A/zh active Pending
-
2010
- 2010-06-08 US US12/796,012 patent/US8695689B2/en not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
See references of WO2009074196A2 * |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2430385B1 (de) * | 2009-05-11 | 2016-07-13 | MAHLE Behr GmbH & Co. KG | Heizkörper für ein kraftfahrzeug mit einer brennkraftmaschine |
Also Published As
Publication number | Publication date |
---|---|
WO2009074196A3 (de) | 2009-08-27 |
DE102008055624A1 (de) | 2009-06-18 |
US8695689B2 (en) | 2014-04-15 |
CN101889186A (zh) | 2010-11-17 |
WO2009074196A2 (de) | 2009-06-18 |
EP2232183B1 (de) | 2018-09-12 |
US20110036546A1 (en) | 2011-02-17 |
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