EP2150757A1 - Wärmeübertrager - Google Patents
WärmeübertragerInfo
- Publication number
- EP2150757A1 EP2150757A1 EP08749432A EP08749432A EP2150757A1 EP 2150757 A1 EP2150757 A1 EP 2150757A1 EP 08749432 A EP08749432 A EP 08749432A EP 08749432 A EP08749432 A EP 08749432A EP 2150757 A1 EP2150757 A1 EP 2150757A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- channel
- heat exchanger
- exchanger according
- inflow
- outflow
- 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
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
- F25B39/022—Evaporators with plate-like or laminated elements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
- F25B39/028—Evaporators having distributing means
-
- 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
- F28F9/0229—Double end plates; Single end plates with hollow spaces
-
- 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
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
- F28F9/0273—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple holes
-
- 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
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over end 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
- F28D2021/0085—Evaporators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2275/00—Fastening; Joining
- F28F2275/04—Fastening; Joining by brazing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2275/00—Fastening; Joining
- F28F2275/14—Fastening; Joining by using form fitting connection, e.g. with tongue and groove
Definitions
- the invention relates to a heat exchanger, in particular an evaporator, as used in particular for a heating or air conditioning system for motor vehicles, according to the preamble of claim 1.
- Evaporators are known in which the two-phase refrigerant is distributed from an inflow channel to a flow-through device, preferably tubes, in particular flat tubes. After flowing through the flat tubes, the vapor refrigerant exits the evaporator via an outflow channel.
- the uniform distribution of the liquid refrigerant in the entire length of the inflow channel presents difficulties.
- the reason for this is among other things the formation of different flow forms depending on the operating condition.
- the segregation of the two-phase refrigerant mixture which is homogeneous at the time of evaporator entry also plays a special role over the length of the inflow channel. Individual pipes are thus supplied exclusively with refrigerant vapor, whereby the evaporator performance deteriorates.
- Fig. 1 shows a heat exchanger 1, in particular an evaporator for a motor vehicle air conditioner according to the prior art and in particular the flow of the refrigerant.
- a heat exchanger has an inflow channel 2, via which the refrigerant the heat exchanger from a refrigerant circuit, not shown, is supplied via an inlet opening 18 (indicated by arrow A).
- the inflow channel 2 is elongate and bounded by two ends.
- the heat exchanger 1 has a collector 12, which consists of an injection plate 5, a distributor plate 6 and a bottom plate 7.
- the refrigerant is a flow device 8, preferably flat tubes supplied.
- thermally conductive ribs are arranged, which are of a medium, preferably air L (indicated by an arrow), flowed around.
- the tubes, as well as the holes of the bottom plate 7 are divided in the middle by a web (not shown), so that two flow regions 14 and 15 are formed, which passes through the refrigerant in the opposite direction.
- the refrigerant therefore first flows through a flow region 14, following the arrow B, and is then deflected through an intermediate chamber 13, which consists of a bottom plate 9, a deflection plate 10 and a closure plate 11, following the arrow C, and flows through a flow region 15 in the opposite direction, following the arrow D, in the collector 12.
- an intermediate chamber 13 which consists of a bottom plate 9, a deflection plate 10 and a closure plate 11, following the arrow C, and flows through a flow region 15 in the opposite direction, following the arrow D, in the collector 12.
- the flow area 15 of the inflowing air L faces.
- injection holes 16 are provided so that the refrigerant from the inflow passage 2 via openings, not shown, which correspond to the injection holes 16, can flow into the flow area 14. Furthermore, suction holes 17 are provided in the injection plate 2, so that the refrigerant from the Flow region 15 can flow into the discharge channel 3. Via the outflow channel 3, the refrigerant then passes into a refrigerant circuit, not shown (represented by arrow E).
- Such an evaporator is referred to as an evaporator with a deflection in the depth according to the invention.
- Fig. 1b shows another evaporator according to the prior art.
- Such an evaporator differs from the evaporator shown in Fig. 1a in particular by the leadership of the refrigerant in the flow device 8.
- the injection holes 16 and the suction holes 17 are arranged offset in the injection plate.
- the refrigerant therefore first flows into the inflow channel (indicated by arrow A), is distributed via the injection bores 16 subsequently to the flow device and passes the arrows B and C through the suction bores into the outflow channel and flows out following the arrow D.
- the evaporator Such an evaporator is referred to according to the invention as an evaporator with a deflection in the width.
- a heat exchanger with at least one inflow channel and at least one outflow channel and at least one collector, which has at least two adjacent plates and with a flow device, which can be flowed through by a first medium and by a second medium, wherein the first medium is distributed from an inflow channel to the collector and to the flow-through device and can be conducted to an outflow channel, at least one further channel being provided for distributing the refrigerant, which is communicatively connected to the inflow channel by at least one opening.
- the distribution path length of the refrigerant to the flow device is shortened by the at least one further channel, and thus the possibility of phase separation of the refrigerant or an equalization of the flow device with refrigerant is minimized.
- the evaporator performance is effectively increased.
- a channel means not only a current path for the refrigerant, but also the physical delimitation of the current path, for example through a pipe.
- the extent of the heat exchanger is to be understood as the overall depth and the width of the expansion of the heat exchanger transversely to the main flow direction of the second medium.
- the collector consists of at least two sheets or plates which are positively and / or materially interconnected, for example by soldering, welding, Toxen, rivets, caulking or a combination of these types of connections.
- the at least two sheets are connected to one another by a hinge.
- the collector consists of two sheets, which are produced by a deep-drawing process.
- the thermoforming profiles have in the opposite direction chamber-like bulges, in which the refrigerant is distributed to the flow device.
- the two sheets can be produced directly in a single tool. This is possible because both collector halves have very similar or identical chamber geometries. This embodiment achieves a number of advantages over prior art three-plate collectors:
- the flow device preferably consists of pipes through which the refrigerant flows.
- the tubes may have a circular, an oval, a substantially rectangular or any other cross section.
- the tubes are designed as flat tubes.
- ribs in particular corrugated fins, are arranged between the tubes, wherein the tubes and the ribs are in particular brazed together.
- the tubes and the ribs soldered to the tubes are referred to as evaporation networks.
- an evaporator network consists of up to 50 flat tubes.
- the further channel is arranged within the inflow channel.
- the further channel is provided with at least one, preferably two or more openings, which connect the further channel communicating with the inflow channel.
- the at least one, preferably two openings are arranged in the middle of the further channel.
- the openings are preferably arranged substantially in a plane which is perpendicular to the axis of the inflow channel, wherein the at least one opening may have a circular, oval, rectangular or any other cross-section.
- the openings are arranged along the entire length of the further channel.
- the number of openings corresponds to the number of flat tubes, so that an opening in the further channel is provided for each flat tube, which is preferably in the immediate vicinity of the respective flat tube.
- the further channel is arranged concentrically or eccentrically in the inflow channel, so that an annular gap is formed between the two channels, in which the refrigerant is distributed to the flow-through device.
- two or more further channels are arranged within the inflow channel.
- the refrigerant flows in this case first into the first further channel, then into the further channels and finally into the inflow channel, from where the refrigerant is distributed to the flow device.
- a longitudinal gap is formed between the inlet channel and the further channel.
- the at least one further channel is arranged partially or wholly outside the inflow channel and communicates with it through at least one opening, which is preferably arranged in the middle of the further channel.
- the inflow channel is formed by two half-shells, which are positively and / or materially interconnected.
- the further channel is arranged within the inflow channel.
- a half-shell preferably has crenellated projections which engage in corresponding recesses of the other half-shell.
- the two half-shells are particularly pressure-resistant and stable connected to each other.
- the inflow channel is formed by a trough-shaped half-shell on which the further channel rests positively and / or materially.
- two or more further channels are arranged outside the inflow channel and connected to one another in serial communication.
- the refrigerant therefore flows first into the first further channel, then into the further channels and finally into the inflow channel, from where the refrigerant is distributed to the flow device.
- the two or more further channels can be designed, for example, as tubes or as plates, which form stacked cavities in which the refrigerant is distributed to the inlet channel and the flow-through device.
- the inflow channel which can be arranged at least one further channel, which can be arranged inside and / or outside of the inflow channel and / or the outflow channel on one side of the heat exchanger and positively and / or materially connected to each other.
- Such an embodiment is particularly suitable for evaporators with small depths.
- the channels are tubular or box-shaped and have a circular or semicircular, triangular, rectangular cross-section or a combination of these cross sections or any other cross section.
- the channels are formed from formed sheet metal, which are positively and / or cohesively connected to each other.
- any desired cross sections of the channels can be produced.
- the cross-section of the channels may be substantially semicircular and / or circular.
- At least one further channel is connected communicatingly with the outflow channel through at least one opening.
- the further channel is located inside and / or outside the outflow channel and is designed in accordance with the previously described embodiments.
- the further channel is for collecting the refrigerant.
- Fig. 1a is an exploded view of a heat exchanger for illustrating the prior art
- Fig. 1b is an exploded view of a heat exchanger to illustrate the prior art
- FIG. 2 shows a first embodiment of an inflow channel of a heat exchanger according to the invention in a side view
- FIG. 3 shows an inflow channel of a heat exchanger according to the invention in a front view along the line IM-III of FIG. 2
- FIG. 5 shows a collector with two sheets in an exploded perspective view of an evaporator with a deflection in depth.
- FIG. 6 shows a collector with two sheets in an exploded perspective view of an evaporator with a deflection in the width
- 7 shows a further embodiment of a collector according to the invention for an evaporator with a deflection in the width
- Fig. 8a multi-channel flat tubes for an evaporator with a deflection in the width or a deflection in the depth;
- FIG. 8b multi-channel flat tubes for a multiblock interconnector
- FIG. 11 shows an inflow channel in a side view according to the fourth embodiment
- FIG. 12 shows an inflow channel of a heat exchanger according to the invention in a front view along the line X-X from FIG. 11;
- FIGS. 13a to 13e show various embodiments for the positioning of the openings which connect the inflow channel to the further channel in a communicating manner
- FIGS. 14a to 14f show various embodiments for the openings according to FIGS. 13a to 13e;
- FIG. 15 shows an inflow channel in a side view according to the fifth exemplary embodiment
- FIG. 16 shows an inflow channel of a heat exchanger according to the invention in a front view along the line XIV-XIV from FIG. 15;
- FIG. 16 shows an inflow channel of a heat exchanger according to the invention in a front view along the line XIV-XIV from FIG. 15;
- FIG. 17 shows an inflow channel in a side view according to the sixth exemplary embodiment
- FIG. 18 shows an inflow channel of a heat exchanger according to the invention in a front view along the line XVI-XVI from FIG. 17;
- FIG. 20 shows an inflow channel of a heat exchanger according to the invention in a front view along the line XVIII-XVIII from FIG. 19;
- Fig. 21 is a plan view of the inflow port, outflow port and another port according to the eighth embodiment of the present invention.
- Fig. 22 is a front view of the inflow channel, outflow channel and another channel taken along the line XX-XX of Fig. 21;
- FIG. 23 is a perspective view of the inflow port, outflow port and another port according to the ninth embodiment of the present invention.
- Fig. 24 is a front view of the inflow channel, outflow channel and another channel according to the tenth embodiment of the present invention.
- Fig. 25 is a partial front elevation of a heat exchanger according to the eleventh embodiment of the present invention.
- FIGS. 26 to 29 show a perspective view of the inflow channel, outflow channel and a further channel according to the twelfth, thirteenth, fourteenth and fifteenth embodiments according to the present invention
- Fig. 30 to Fig. 32 is a perspective view of the inflow channel, outflow channel and another channel according to the sixteenth, seventeenth and eighteenth embodiments of the present invention.
- 33a and 33b show a perspective view and a detailed view along the line X-X from FIG. 33a of the inflow channel, outflow channel and a further channel according to the nineteenth embodiment according to the present invention
- FIG. 34 is a detail view of the inflow channel, outflow channel and another channel according to the twentieth embodiment of the present invention.
- 35a and 35b are a perspective view and a detailed view of the inflow channel, outflow channel and another channel according to the twenty-first embodiment of the present invention.
- FIG. 36 is a detail view of the inflow port, outflow port and another port according to the twenty-second embodiment of the present invention.
- FIG. 37a and 37b are a perspective view of a collector and a front view of the collector with another channel according to the twenty-third embodiment of the present invention
- Fig. 38 is a plan view of the inflow port, outflow port and two further passages according to the twenty-fourth embodiment of the present invention
- Fig. 39 is a front view of the inflow channel, outflow channel and two further channels taken along the line XXXII-XXXII of Fig. 38; 40a to 40d different embodiments for an intermediate chamber of an evaporator with deflection in depth;
- FIG. 2 to 4 show a first embodiment of an inflow channel 3 of a heat exchanger in various views according to the present invention.
- Such a heat exchanger differs from the prior art according to FIG. 1 in particular by the configuration of the inflow channel 3.
- the inflow channel 3 is communicatively connected to a further channel 4 through two openings 19, which are arranged substantially in the center of the inflow channel.
- the refrigerant thus flows through the further channel 4, represented by the arrow F, into the heat exchanger 1 and is distributed through the two openings 19 (indicated by arrows F) into an annular gap 20 which extends between the inlet channel 3 and the further channel 4 formed. From this annular gap, the refrigerant flows through the openings 21 into the tubes, which form the flow-through device 8.
- the two openings 19, which connect the further channel communicating with the inflow channel, are substantially at opposite ends Side of the other channel and aligned in a direction that is perpendicular to the evaporator level.
- the two openings 19 are rotated by 90 ° clockwise relative to the embodiment shown in FIGS. 2 to 4.
- the inflow and the further channel are formed as a tube, wherein the further channel is inserted into the inflow channel.
- the ratio between the inner diameter of the further channel and the diameter of the opening 19, which is preferably designed as a bore, is between 1.25 and 5, preferably between 1.25 and 2.5.
- the ratio between the inner diameter of the further channel and the hydraulic diameter of the annular gap is between 1 and 20, preferably between 1 and 6.
- the collector 12 may in this case consist of three plates, namely an injection plate, a distributor plate and a bottom plate, as shown in FIGS. 1 and 2.
- the collector of two sheets 50 and 70 which are produced in particular by a forming process, preferably by a deep-drawing process, be composed.
- FIGS. 5 and 6 show such collectors for an evaporator with a deflection in the depth (FIG. 5) or in the width (FIG. 6).
- Such a collector consists of two sheets, an upper 50 and a lower plate 70, which are positively and / or materially connected to each other.
- the support of the inflow channel and / or of the outflow channel and / or of the at least one further channel takes place in a trough-shaped depression 51 of the upper metal sheet 50, the secure positioning of the individual channels being ensured by positioning lugs 52 or individual bore passages.
- the upper plate 50 and the lower plate 70 each have chamber bulges 60 in the opposite direction.
- the chambers form the cavities for distributing the refrigerant from the injection bores 16 to the flow-through device 8.
- the middle distributor plate can be dispensed with.
- this throughflow device consists of multi-channel flat tubes 80.
- Each chamber receives in each case one or more flat tubes, preferably two flat tubes (see FIG. 5) into which the refrigerant is redistributed.
- the heat exchanger is either single row or double row. This means that either a flat tube (see FIG. 6) or two flat tubes (see FIG. 5) are arranged in the overall depth.
- the inclusion of the flat tubes in the collector takes place, for example, by a torn passage on the collector side to the outside or inwards or by a punching.
- Fig. 7 shows a further embodiment of a collector according to the invention for an evaporator with a deflection in the width.
- the execution of the bottom plate 700 takes place as a wave profile, wherein the recording of the flat tubes is located in the troughs.
- a simple U-shaped end plate 500 a closed collector is formed, this is no further end cover necessary.
- the cavities for distributing the refrigerant from the injection orifices 16 to the individual flat tubes 8 are generated by the corrugation profile, as well as the chamber partitions between the individual flat tubes.
- the bottom plate 700 can also be formed as a flat plate and the end plate 500 as a corrugated profile ,
- a continuous elevation or a wall transverse to the valley valleys is introduced into the corrugated profile in order to produce a parting plane in the depth direction.
- FIGS. 9 to 11 show three further exemplary embodiments of an inflow channel according to the present invention in a side view.
- Fig. 12 shows a front view of the fourth embodiment of FIG. 11.
- the two openings 19 are spaced from the center of the inflow channel.
- the further channel 4 as seen in the flow direction, is closed after the openings 19 by a partition wall 22 in order to counteract a negative effect of the repressurization of the refrigerant. genzu note.
- the further channel is positioned concentrically or eccentrically in the inflow channel (see FIGS. 11 and 12).
- the further channel is connected by two or more openings, which are arranged substantially in a plane which is perpendicular to the axis of the inflow, with the inflow channel.
- two openings are preferably arranged diametrically.
- the further channel communicates with the inflow channel communicating through an opening.
- Figs. 15 and 16 the fifth embodiment is shown in a side and front view.
- the further channel 4 is inserted in the inlet channel 2 and has a recess 23, so that there is a longitudinal gap 24, in which the refrigerant is distributed through the openings 21 to the tubes.
- the course of the at least one opening 19 is formed substantially perpendicular or obliquely to the inflow channel.
- the further channel 4 has a D-shaped cross-section, so that a different shape of the cross-section of the longitudinal gap 24 results.
- Figs. 17 to 20 show the sixth and seventh embodiments in a side and front view.
- the further channel 4 is arranged outside of the inflow channel 2, wherein the inflow channel is inserted into the further channel. This insertion takes place either from the inside (FIG. 17) or from the outside, in which the inflow channel is inserted into a recess 25 of the further channel (FIG. 19).
- the eighth embodiment is shown schematically in a plan and front view.
- the inflow channel, the outflow channel and the further channel are designed as round tubes and connected to one another in a material-locking manner, wherein the further channel is arranged outside the inflow channel.
- FIG. 23 shows the ninth exemplary embodiment and a development of the heat exchanger according to FIGS. 21 and 22.
- the inflow channel, the outflow channel and the further channel are in the form of triangular tubes.
- the at least one opening which communicates the further channel with the inflow channel is preferably arranged in the middle or at any other points of the further channel and the inflow channel.
- this embodiment results in an installation space optimization which is particularly suitable for evaporators with small overall depths, wherein the construction depth according to the invention is the expansion of the evaporator along and the width of the expansion of the evaporator transverse to the main flow direction of the air to understand.
- the tenth embodiment is shown in a front view.
- the inflow channel, the outflow channel and the further channel are formed by deformed metal sheets which are connected to one another in a positive and / or cohesive manner.
- the cross sections of the inlet and outlet channels are substantially semicircular and the cross section of the further channel is substantially circular.
- any other shape of the cross section is possible. By this configuration is a particularly favorable manufacturing process of the various channels possible.
- FIG. 25 shows the eleventh exemplary embodiment of a section of a heat exchanger according to the invention in a front view.
- the collector 12 consists of three plates.
- the first further channel 4a which is formed as a tube, rests on the plate-shaped second further channel 4b and is connected to it in a communicating manner.
- the refrigerant flows from the first further channel 4a into the second further channel 4b and into the inflow channel 2. From there, the refrigerant is distributed to the collector 12 and the flow-through device 8.
- FIGS. 26 to 29 show four further exemplary embodiments according to the present invention.
- the further channel 4 is positioned on the upper plate 50 of the collector 12 in such a way that, together with the specially shaped upper plate 50, an inflow channel 2 is formed.
- the further channel 4 is deformed in such a way and positioned on the upper plate 50 of the collector 12, that together with the upper plate an inflow channel 2 is formed.
- the inflow channel is formed by a flat tube, which is arranged between the further channel and the collector.
- the further channel 4 and the inflow channel 2 are formed by a tube, which is produced in particular by an extrusion method.
- FIGS. 30 to 32 show three further exemplary embodiments of a heat exchanger according to the present invention.
- the inflow channel 2 is generated by a plate 25 in the collector 12.
- the inflow channel is produced by a continuous plate 25 which is punched out on the suction side.
- the inflow channel is produced by means of a continuous metal sheet, wherein the outflow channel 4 rests on this sheet and is positively and / or materially connected thereto.
- the inflow channel 2 is formed by a trough-shaped half-shell.
- the trough-shaped shell has an impression 27 (FIG. 33b), on which the further channel 4 rests positively and / or materially.
- the other channel has a round shape, but alternatively, other shapes are conceivable. For example, can be achieved by an oval shape of the further channel 4, a larger volume of the inflow channel 2.
- the trough-shaped shell may also be flat.
- Fig. 34 shows an embodiment similar to that in Figs. 33a and 33b.
- the inflow channel is formed by an impression 27 in the further channel 4.
- the inflow channel 2 is formed by an upper 2a and a lower 2b half shell, the further channel 4 inside of the inflow channel 2 is arranged.
- the opening 19, which connects the inflow channel 2 to the further channel 4 in a communicating manner, is arranged in such a way that a vertical flow is created between inflow channel and further channel.
- two openings 19 are arranged such that a horizontal flow of the first medium is formed between inflow channel and further channel.
- the two half shells 2a and 2b are in particular positively and / or materially connected to each other, for example, clipped together.
- a half-shell has crenellated projections 28, which engage in corresponding recesses of the other half-shell (FIG. 41).
- Fig. 37a shows a collector 12 according to the prior art, wherein the further channel 4 is disposed within the collector 12.
- the opening 19, which connects the further channel 4 communicating with the collector 12 is arranged according to FIG. 37b in an upper region of the further channel.
- one or more openings may also be arranged at another location, for example, such that, similar to the exemplary embodiment according to FIG. 36, a horizontal flow of the first medium is created between the further channel 4 and the collector 12.
- FIGs. 38 and 39 another embodiment is shown schematically in a plan and front view.
- two further channels 4a and 4b are arranged outside of the inflow channel 2.
- F indicated) into the first further channel flows into two separation stages into four equal-sized refrigerant mass flows, which each have a quarter of the original evaporator width on the flat tubes, for example, four
- the refrigerant is distributed to up to 50 flat tubes.
- FIGS. 40a to 40d Four exemplary embodiments for the intermediate chamber 13 of an evaporator with a deflection in the depth are shown in FIGS. 40a to 40d.
- Fig. 40a shows an embodiment in which no re-mixing of the refrigerant takes place in the intermediate chamber.
- a remixing in the intermediate chamber may be desired to compensate for any previous unequal distributions in the injection into the flow device.
- FIGS. 40b to 40d which enable a remixing of the refrigerant.
- the invention is particularly suitable for the uniform distribution of the vapor-liquid refrigerant mixture to the flow device of dual-flow evaporators.
- the refrigerant undergoes only a deflection in the flow device. This deflection can be done in the depth or in the width of the evaporator.
- such an evaporator is particularly suitable for the refrigerant R134a or R744.
- such an evaporator is also suitable for other refrigerants, for example the "Global Alternative Refrigerants (GARs)" known in the art.
- GARs Global Alternative Refrigerants
- the invention has been explained with reference to a heat exchanger in which the refrigerant flows parallel to the inlet channel in the heat exchanger.
- the refrigerant flows perpendicular to the inflow in and / or out of the heat exchanger.
- the inlet and / or outlet openings are in this case in the middle of the inflow and / or outflow or spaced from the center.
- Further alternative embodiments are within the meaning of the present invention, wherein in particular the design of the collector can be used with two or three sheets or plates for all embodiments.
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 (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102007024089 | 2007-05-22 | ||
DE102007054481 | 2007-11-13 | ||
PCT/EP2008/003784 WO2008141744A1 (de) | 2007-05-22 | 2008-05-09 | Wärmeübertrager |
Publications (2)
Publication Number | Publication Date |
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EP2150757A1 true EP2150757A1 (de) | 2010-02-10 |
EP2150757B1 EP2150757B1 (de) | 2018-10-24 |
Family
ID=39672033
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EP08749432.4A Active EP2150757B1 (de) | 2007-05-22 | 2008-05-09 | Wärmeübertrager |
Country Status (6)
Country | Link |
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US (1) | US9759492B2 (de) |
EP (1) | EP2150757B1 (de) |
CN (1) | CN101680689B (de) |
BR (1) | BRPI0811928A2 (de) |
DE (1) | DE102008023055A1 (de) |
WO (1) | WO2008141744A1 (de) |
Cited By (1)
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CN102853572A (zh) * | 2012-10-11 | 2013-01-02 | 江苏辉煌太阳能股份有限公司 | 套管式热传导介质等流程太阳能集热器流道 |
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2008
- 2008-05-09 DE DE102008023055A patent/DE102008023055A1/de not_active Withdrawn
- 2008-05-09 EP EP08749432.4A patent/EP2150757B1/de active Active
- 2008-05-09 WO PCT/EP2008/003784 patent/WO2008141744A1/de active Application Filing
- 2008-05-09 CN CN2008800167638A patent/CN101680689B/zh not_active Expired - Fee Related
- 2008-05-09 BR BRPI0811928-7A2A patent/BRPI0811928A2/pt not_active IP Right Cessation
-
2009
- 2009-11-16 US US12/619,566 patent/US9759492B2/en not_active Expired - Fee Related
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CN102853572A (zh) * | 2012-10-11 | 2013-01-02 | 江苏辉煌太阳能股份有限公司 | 套管式热传导介质等流程太阳能集热器流道 |
Also Published As
Publication number | Publication date |
---|---|
CN101680689B (zh) | 2012-11-14 |
EP2150757B1 (de) | 2018-10-24 |
US9759492B2 (en) | 2017-09-12 |
CN101680689A (zh) | 2010-03-24 |
US20100116474A1 (en) | 2010-05-13 |
BRPI0811928A2 (pt) | 2014-11-25 |
DE102008023055A1 (de) | 2008-11-27 |
WO2008141744A1 (de) | 2008-11-27 |
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