DE19729497A1 - Flat tube heat exchanger for car air-conditioning plant - Google Patents

Abstract

The heat exchanger has a tube block made out of several adjacent parallel flat tubes (1a,1b,1c) with a distributing and collecting tube on each side of the block. The distributing and collecting tube has a peripheral opening into which all the flat tubes are sealingly fitted at their inlet and outlet ends. The distributing and collecting tube are located with the longitudinal axis parallel to the depth direction of the block. In the depth direction, there are several adjacent tube blocks, and the flat tubes of all the blocks are fitted to the same distributing and collecting tube extending between the front and rear block.

Description

The invention relates to a flat tube heat exchanger ger according to the preamble of claim 1. Such heat become a z. B. as evaporators and condensers Automotive air conditioning systems used

In the patent US 5,368,097 is a flat tube heat Transformer described in serpentine construction, the single-flow is designed, d. H. from only one, serpentine wound NEN tubing of a multi-chamber flat tube. Each of the two pipe ends ends in one specially directed towards him tidy, longitudinally slotted connecting pipe.

Compared to such single-flow flat tube heat exchangers ha ben multi-flow heat exchanger of the type mentioned among other things the advantage of a lower pressure drop and increased performance in a given installation space. The Patent US 3,416,600 describes such heat Transformer in serpentine design, its tube / fin block of several, parallel flow, in a block high direction of adjacent serpentine pipe strings built and bent into a U-shape. At the two free ends this U-block is a respective one parallel to Block vertical direction as a distribution or collecting pipe  Acting connecting pipe, the circumference with a row spaced apart longitudinal slots is provided. The one respective connecting pipe associated pipe string ends are around 90 ° twisted out of the tube / fin block and fluid-tight individually inserted into the connecting pipe longitudinal slots adds.

In the case of a multi-flow device disclosed in EP 0 219 974 A2 Capacitor of the type mentioned is a Pipe / rib block with several straight lines, in which thereby defi nated block vertical with the interposition of a resp towards the corrugated rib, extruded multiple cells lying next to each other mer flat tubes provided. The flat tubes are with their same-sided ends in corresponding transverse slots respective to act as a distribution or manifold end pipe inserted fluid-tight. The two connecting pipes run along the corresponding opposite side ten of the tube / fin block parallel to the block vertical longitudinal axis.

The invention is the technical problem of providing development of a heat exchanger of the type mentioned reasons that can be manufactured with relatively little effort and with high pressure stability and low internal pressure as required rem volume and high performance is feasible.

The invention solves this problem by providing it a flat tube heat exchanger with the features of the An Proverb 1. This heat exchanger is designed for multiple flows, which allows high performance, and he can with re relatively low manufacturing costs using extru dated multi-chamber flat tubes with the required pressure stability are manufactured, with little soldering or Welds are required. By the characteristic Arrangement of the distribution and manifold with parallel to Block depth direction lying longitudinal axis is at relatively ge ring space a very even distribution of the  led heat transfer fluids into the individual flat tubes strands allowed. At the same time, this special posi tionation of the two connecting pipes with the right relatively little additional effort, several in the block depth direction adjacent pipe blocks to provide what the lei performance of the heat exchanger with the same Cross dimension increases.

A further developed according to claim 2 heat exchanger several pipe blocks one behind the other, their flat pipe strands with their entry and exit sides All ends in a common manifold are inserted. This realizes a heat exchanger with ho performance and favorable connection characteristics.

According to a development of the invention according to claim 3 mün that the inlet-side or outlet-side pipe string ends of a respective pipe block either individually in separa te connection openings of the distribution or manifold or as Stack in a common connection opening.

A heat exchanger further developed according to claim 4 a distribution profile in the distribution pipe around the distribution pipe cross cut in several, circumferentially distant from each other Dete distribution rooms to divide so that the tubing strings egg nes respective pipe block with their inlet ends each lead to its own distribution room. This allows the Favorably influence the uniformity of the fluid supply.

In a further developed according to claim 5 heat exchanger is one in several, one after the other in the block depth direction subdivided distribution pipe provided, where the distribution rooms, the heat transfer fluid via an egg gene supply line is supplied. Doing the feed lines in a further embodiment of the invention according to An Proverb 6 front, d. H. axially, or circumferentially, d. H. ra open into the respective distribution room.  

In a further embodiment of the invention according to claim 7 on the entry side of the distribution profile or the feeder tion set a Venturi nozzle-like flow distribution device tion provided, which is an equal distribution of heat transmission fluids on the individual pipe strings of the respective favored pipe blocks.

In a development of the invention according to claim 8 opens a feed pipe radially through a corresponding inlet opening into the manifold at a point where there are several consecutive pipe blocks closer to the front than is at the rearmost pipe block, d. H. closer to the pipe block, the first from the outside of the pipe in the block depth direction medium passed over the pipe block, e.g. B. air, ange is flowing.

In a development of the invention according to claim 9 is an entmi anti-shock spiral profile in a curved section a supply pipe leading to the distribution pipe is provided to if necessary, segregation of the heat passed through it carrying fluids through the curved flow guide to ver avoid.

In a development of the invention according to claim 10 are the inlet side of the distribution pipe suitable flow ver vortex means provided to the radially fed and there heat transfer fluid to be deflected in the distribution sufficiently mix the pipe entry area.

In a further developed according to claim 11 heat exchanger of the serpentine type are the distribution pipe and the collector pipe opposite tube block sides, preferably dia per se gonally opposite points. Accordingly the ends of the serpentine tubing strings are opposite them horizontal pipe block sides led out and into the assigned te distribution or manifold inserted. Alternatively, are  in a heat exchanger developed according to claim 12 of the serpentine type, the distribution pipe and the collecting pipe on the arranged the same pipe block side and the pipe ends correspondingly all out of the tube on this tube block side led out block. In a further embodiment this heat according to claim 13, the transmitters are the distribution and the sam Melrohr formed as integral parts of a connecting pipe, that by means of at least one longitudinal partition in several longitudinal channels is divided, two of which are used as ver Partial or manifold function.

A further developed according to claim 14 heat exchanger hold at least two pipe blocks, one of which is one entry-side and the other one exit-side Form a block. The distribution pipe and the collecting pipe are integral Parts of a divided by means of a transverse wall, with its longitudinal axis extending in the block depth direction end pipe. The block opposite the connecting pipe side forms a fluid deflection area over which the pipe conduit le of the exit side with those of the entry side Pipe blocks are in fluid communication. In another form tion of this heat exchanger are according to claim 15 on the outlet-side and the outlet-side tube block of resp halves of U-shaped flat tubes. The flat tube halves are opposite the arch connecting them richly twisted so that it is perpendicular to the block vertical tion while the U-bend area is parallel or pointed is at an angle to the vertical direction of the block. With enough pointed Angled course of the U-bend area can the archery adjacent flat tubes in the vertical direction of the block overlap, so that the distance between each other if necessary following, preferably by a respective corrugated fin of can reduce separate flat tubes.

A further developed according to claim 16 heat exchanger maintains a tube / rib block complex that one or preferably contains several pipe blocks, with between neighboring  beard flat tubes each tube block introduced a corrugated fin is that consistently from the front to the rear Pipe block extends. This has a favorable effect on the heat transmission performance and facilitates z. B. for the user condensate drainage when an evaporator is used.

Advantageous embodiments of the invention are in the Drawings are shown and are described below. Here show:

Fig. 1 is a schematic, side view of a shortened flat-tube evaporator in serpentine structure with a zelnem tubing connection,

Fig. 2 is a view corresponding to FIG. 1, but for a modified evaporator having equal page common tubing connector

Fig. 3 of a tubular manifold a cross sectional view used in the evaporator of Fig. 1, split longitudinally,

Fig. 4 is a longitudinal sectional view of the inlet end of an end portion of the manifold of FIG. 3 vorgese Henen Verteilprofils,

Fig. 5 is a longitudinal sectional view of a transversely divided, usable for the evaporator of FIG. 1 with separate distributor pipe, axially leading-supply lines,

Fig. 6 is a longitudinal sectional view of a further ten quergeteil, usable for the evaporator of FIG. 1 Ver partialtube with separate, radially opening out supply lines,

Fig. 7 is a side view of the evaporator of FIG. 1 usable with a single distribution pipe to the catching side inlet port,

Fig. 8 is a sectional view taken along line VIII-VIII of Fig. 7,

Fig. 9 is a fragmentary longitudinal sectional view of a Ver usable for the evaporator of FIG. 1 or 2 with a curved tube part supply pipe,

Fig. 10 is a longitudinal sectional view of the inlet side of a Be Reich for the evaporator of FIG. 1 or 2 usable tubular manifold with radial Fluidzufüh tion and verwirbelnder inclined wall,

Fig. 11 is a partial longitudinal sectional view of a usable for the evaporator of FIG. 1 tubular manifold with radial fluid supply and fluid mixing, ter perforated anchoring aperture,

Fig. 12 is a view corresponding to FIG. 2, but for a modified evaporator with only one, made up of identi rule serpentine pipe sections pipe / fin block,

Fig. 13 is an end view of the pipe / fin block of the evaporator of FIG. 12 in the direction of arrow XIII of FIG. 12, with the cut-away Strangendbereichen

Fig. 14 is a schematic side view of a flat-tube evaporator in serpentine structure with a built from identical serpentine pipe sections pipe / fin block and a block side integrated by a longitudinally divided connecting tube formed distributing and collecting pipe,

Fig. 15 is a detail view of the portion XV of Fig. 14,

Fig. 16 is a schematic sectional view of a tubular flat-tube heat exchanger with integrated shared by a connecting pipe formed querge distribution and collection and a U-shaped from twisted Flachroh ren formed pipe / fin block complex,

Fig. 17 is a view of the flat tube bend area of Fig. 16 in the direction of arrow XVII and

Fig. 18 is a view corresponding to FIG. 17, but successive for a modified heat exchanger with them overlapping arc portion flat tubes of the tube / fin block complex.

The evaporator of a motor vehicle air conditioning system shown in Fig. 1 consists of three identically constructed tube / fin blocks, which are arranged in a block depth direction defined thereby perpendicular to the plane of Fig. 1 one behind the other, which is why in Fig. 1 only the front ste Pipe / fin block is recognizable. Alternatively, the evaporator can also be constructed from fewer or more than three such adjacent tube / fin blocks. Each tube / fin block consists of three serpentine-shaped tube strings 1 a, 1 b, 1 c made of extruded multi-chamber flat tubes in a block vertical direction z defined thereby. Between adjacent flat tube layers of the tube / fin blocks, a corrugated fin 2 is introduced, which preferably extends continuously as a one-piece corrugated fin from the foremost to the rearmost fin / tube block, which facilitates the condensate drainage.

Each serpentine pipe string 1 a, 1 b, 1 c is led out with its two end regions 3 a, 3 b, 4 a, 4 b, 5 a, 5 b on the pipe block sides opposite in block cross direction x and, if necessary with an angle, to one of the pipe block side arranged connecting pipe 6 , 8 fed, of which one acts as a distribution pipe 6 and the other as Sam melrohr 8 . The two connecting pipes 6 , 8 run with their longitudinal axis parallel to the block depth direction and are arranged at diagonally opposite positions of the pipe / fin block, the distribution pipe 6 at the top 7 of the evaporator in the position shown in FIG is positioned. This is advantageous for the distribution of the heat transfer fluid, which in this case is the refrigerant, through the pipe strings 1 a, 1 b, 1 c. Due to the diagonally opposite positioning of the two connecting pipes 6 , 8 , the length differences of the individual serpentine pipe strings can also be kept low. As can be seen from FIG. 1, the two outer serpentine tubing 1 a, 1 c of identical shape and only rotated by 180 ° angeord net, with the advantage that only two different ones for the production of the three-fin ribs / tube blocks Serpenti nenrohrstrangformen for the middle tubing 1 b on the one hand and the outer tubing 1 a, 1 c on the other hand are needed.

The inlet-side end regions 3 a, 4 a, 5 a of the tube strings 1 a, 1 b, 1 c are, as can also be seen from FIG. 1, inserted at 90 ° to each other in the circumferential direction in the distribution tube 6 and soldered tightly therein. In the same manner, the outlet-side tube end regions 3 b, 4 b, 5 b are inserted into the collecting tube 8 in a fluid-tight manner by 90 ° in the circumferential direction to one another. For this purpose, the distribution tube 6 and the header tube 8 are hen with circumferential verses with corresponding slots as connection openings, through which the flat tube ends are inserted. In order to accommodate all nine pipe ends of all three pipe / finned blocks that are the same, the two connecting pipes 6 , 8 are each provided with three rows of slots spaced apart by 90 ° in the circumferential direction, each with three slots. The connecting tubes 6 , 8 are solder-plated or prefabricated surrounded by a solder molding, and the slots have approximately the dimensions of the flat tube cross-section, so that it is during a soldering process, in which also the Wellrip pen 2 are soldered to the flat tubes, to form a tight solder connection between the ends of the extruded flat tube strands 1 a, 1 b, 1 c on the one hand and the refrigerant medium connecting pipes 6 , 8 on the other.

Fig. 2 shows an embodiment substantially corresponding to Fig. 1, so that for the sake of clarity the same reference numerals are used for functionally identical components. The modification in the evaporator of Fig. 2 is that the same-sided tubing ends 9 a, 10 a, 11 a, or 9 b, 10 b, 11 b of the serpentine tubing 1 a, 1 b, 1 c to a respective stack, in which they are touching or at most close to each other, leads together and are inserted as a stack in a connection opening common to them each of the correspondingly modified distribution or collecting pipe 6 a, 8 a are inserted in a fluid-tight manner. This means that the two modified connecting pipes 6 a, 8 a are each provided with a series of longitudinal slots corresponding to the number of pipe / fin blocks, the dimensions of which correspond approximately to those of the associated flat pipe stack. This design can be implemented in a very compact manner and is insensitive to any uneven distributions or segregation effects of the refrigerant supply flow.

In order to favor a uniform supply of refrigerant to the individual tube strings 1 a, 1 b, 1 c of the respective tube / fin block in the evaporator of FIG. 1, it is advantageous to insert a distribution profile 12 into the distribution tube 6 , as shown in FIG can be seen in FIGS. 3 and 4. The longitudinal distribution profile 12 , as can be seen from FIG. 3, has a star-shaped or Y-shaped cross-section, whereby three separate distribution channels 13 a, 13 b, 13 c are formed, in each of which one of the three inlet-side pipe ends 3 a, 4 a, 5 a of a respective tube / fin block opens. By a suitable angular offset of the three star arms 12 a, 12 b, 12 c of the distribution profile 12 and suitable choice of the width of each star arm, the passage cross section of the three separate distribution channels 13 a, 13 b, 13 c can be set in the desired manner, preferably in such a way that the distribution channels 13 a, 13 b, 13 c all have the same volume. In the example of FIG. 3, two closely adjacent star arms 12 a, 12 b have a smaller width d ₂ than the width d _{1 of} the third star arm 12 c, which is spaced further apart in the circumferential direction.

As seen specifically in Fig. 4, the star profile 12 at its inlet end to a tip end 12 d sharpened, the inlet side upstream in a corresponding recess 14 a of a nozzle-shaped sleeve 14 projects into it. The sleeve 14 is provided with a nozzle channel 15 such that it forms, together with the star tip 12 d of the United profile 12, a Venturi nozzle-like, ie functionally egg ner Venturi nozzle corresponding flow distribution device with which the supplied refrigerant flow is equal to the various distribution channels 13 a, 13 b, 13 c is divided.

Fig. 5 shows a further possible realization of a usable as a distribution tube 6 for the evaporator of Fig. 1 to the connecting tube 6 h. This distribution pipe 6 h is divided by means of two transverse walls 16 a, 16 b into three distribution chambers 17 a, 17 b, 17 c. The two transverse walls 16 a, 16 b are each at the level between adjacent ones of the three tube / fin blocks lying one behind the other, the respective serpentine tube strings with their inlet-side ends 3 a, 5 a in the three longitudinal slots offset by 90 ° in the circumferential direction 18 are inserted, which are introduced into the distribution tube 6 h at the level of each distribution chamber 17 a, 17 b, 17 c. The refrigerant is supplied to the distribution chambers 17 a, 17 b, 17 c each separately via their own supply lines 19 a, 19 b, 19 c, which are carried out axially through the inlet-side end of the distribution tube 6 h and have a significantly smaller diameter than the manifold 6 h. Each feed line 19 a, 19 b, 19 c opens into its associated distribution chamber 17 a, 17 b, 17 c, the feed line 19 a for the rearmost distribution chamber 17 a through both transverse walls 16 a, 16 b and the feed line 19 b for the central distribution chamber 17 b are carried out through the front transverse wall 16 b. Vorzugwei se is in a manner not shown on the inlet side of the three supply lines 19 a, 19 b, 19 c again a Venturidü senanordnung for equal distribution of the supplied refrigerant is provided.

FIG. 6 shows a variant of the distributor arrangement from FIG. 5, functionally identical parts being provided with the same reference symbols. In this variant, the refrigerant supply lines 19 a, 19 b, 19 c, preferably coming from a Venturi nozzle arrangement, are guided axially along the outside of a modified manifold 6 b, the circumference of which has a push-through opening 20 a, 20 b, 20 c each fluid-tight insertion of a respective supply line 19 a, 19 b, 19 c is hen. Each distribution chamber 17 a, 17 b, 17 c is assigned a feed line push-through opening 20 a, 20 b, 20 c approximately at half the height thereof, and the feed lines 19 a, 19 b, 19 c are bent radially into the Through openings 20 a, 20 b, 20 c inserted. The feed line through openings 20 a, 20 b, 20 c are in a row and offset in the circumferential direction by 90 ° to the mutually adjacent flat tube through-slots 18 , in which the one-sided pipe ends, as shown ends 4 a, of the various tube / fin blocks.

FIGS. 7 and 8 show another alternative design of the distributor side terminal portion for the evaporator of FIG. 1. In this example, an undivided dispersion tube 6 c provided in the slots in addition to the three rows of three longitudinal 18 for insertion of the various eintrittsseiti gene pipe ends 3 a, 4 a, 5 a, a single inlet opening 21 is introduced circumferentially. The inlet opening 21 is in a slot opposite the adjacent flat tube push-through 18 offset by 90 ° in the circumferential area and advantageously closer to the foremost tube / fin block 22 a, that is to say the one from the outside of the tube via the tube / fin blocks 22 a behind one another , 22 b, 22 c, medium directed away in the block depth, e.g. B. air to be cooled, is first flowed to as the rearmost tube / fin block 22 c. Thus, the medium passed for cooling over the evaporator first comes into thermal contact with the refrigerant at the foremost tube / fin block 22 a, which only covers a very short distance in the distribution tube 6 c before it enters the associated serpentine tube strands 3 a, 4 a, 5 a arrives, and is therefore relatively cold. As can be seen particularly from FIG. 8, a supply pipe 23 is inserted in a fluid-tight manner into the inlet opening 21 of the distribution pipe 6 c, via which the refrigerant is fed radially into the distribution pipe 6 c. From there it gets into the three pipe ends 3 a, 4 a, 5 a of the respective pipe / fin block, with FIG. 8 being modified compared to FIG. 1 to the extent that here the middle end 4 a of the three ends of the pipe ends 3 a , 4 a, 5 a and not one of the two laterally opening ends 3 a, 5 a opens directly from the tube / fin block straight into the distribution tube 6 c.

Fig. 9 shows a further possible distributor-side connection pipe design for the evaporator of Fig. 1 or that of Fig. 2, which is why the connection pipe used here 6 d per pipe / finned block again with several longitudinal slots offset around the circumference for individual implementation of the different pipe string ends or with a wide longitudinal slot for the joint implementation of the entry side pipe string ends is provided in a stack. From Fig. 9 also the presence of a respective, by going over all at the same height flat tube layers 25 a, 25 b of the successive tube / fin blocks he stretching corrugated fin 24 between device in each block adjacent vertical tube layers clearly. To achieve egg ner compact design opens a for the distribution tube 6 d before seen feed tube 26 of substantially the same diameter with a sharp arc 26 a axially into the distribution tube 6 d. In order to avoid refrigerant segregation due to this strong flow deflection, which could otherwise lead to drying out of certain refrigerant pipe strings, is in the supply pipe 26 , which connects the manifold 6 d with the expansion valve of the air conditioning system, not shown, a coil body 27 , z. B. a Ru-helix. This spiral body 27 also fulfills the feed pipe 26 in the region of curvature 26 a and in this way prevents refrigerant segregation.

Fig. 10 shows another realization of a demixing inhibiting device when strong refrigerant deflection is required. In this example, a feed pipe 28 opens via a corresponding circumferential inlet opening 29 radially into the inlet end region of a z. B. for the United steamer of FIGS . 1 and 2 usable distribution tube 6 e. The required right-angled flow deflection is caused in an anti-segregation manner by an inclined wall 30 in the front end region of the distribution tube 6 e of the inlet opening 29 , on which the inflowing refrigerant hits at an angle of approximately 45 °, whereby it is swirled and mixed sufficiently to the individual Strands of pipe arrives.

Fig. 11 shows a further modified, suitable for the evaporator of Fig. 1 manifold 6 f, to which the refrigerant can be fed through a supply pipe 31 radially at the entry-side end face through a circumferential inlet opening 32 . A refrigerant segregation caused by the required right-angled refrigerant deflection is encountered in this distributor-side connection arrangement by a perforated baffle in the form of a transverse wall 34 provided with a central aperture 33, the transverse wall 34 between the inlet opening 32 and the foremost row of flat tube through-slots 18 in the distribution tube 6 f is introduced. Since the refrigerant has to pass through the central diaphragm opening 33 , it is sufficiently mixed again even if it has previously been separated.

FIGS. 12 and 13 show a vaporizer similar to FIG. 2, which is in contrast modified such that it includes only egg NEN pipe / fin block and these, e 1 is constructed of only two d ne beneinanderliegenden serpentine pipe sections 1. In addition, the distribution pipe 6 a and the manifold 8 a are no longer positioned at diametrically opposite locations on the pipe / fin block, but instead are shifted somewhat towards the center of the pipe block. The corrugated fins 2 correspond in depth to the width of the extruded multi-chamber flat tubes used. The particular advantage of this evaporator is that only a single type of identically designed serpentine tubing is required to build its tube / fin block, which keeps the manufacturing costs low. In addition, the performance of the evaporator with regard to the achievable uniform temperature distribution due to its symmetrical structure shown in FIG. 12 is positively influenced.

Fig. 14 shows a similar to the above-described flat tube evaporator in a serpentine design, in which, however, if it is mounted in the position shown on the vehicle, the straight pipe sections run vertically instead of horizontally. The evaporator consists like that of FIGS. 12 and 13 from a single tube / finned block with two adjacent serpentine tube strings 1 f, 1 g, which are designed identically, which again simplifies the manufacturing effort here. In the evaporator of FIG. 14, both the inlet-side end regions 37 a, 38 a and the outlet-side end regions 37 b, 38 b are guided out of the same on the same side of the tube / fin block and inserted into a common connecting pipe 39 , which is a distribution pipe 39 a and a manifold 39 b as integrated components, as can be seen more clearly in the detailed view of FIG. 15. For this purpose, there is a longitudinal dividing wall 40 in the round connecting pipe 39 , which divides the connecting pipe cross-section into the distribution pipe channel 39 a and the collecting pipe channel 39 b. If necessary, the connecting pipe cross section can be divided into more than two longitudinal channels by means of a plurality of partitions or dividers, in which case the distribution pipe channel is then spaced apart from the collecting pipe channel via a heat-insulating separation channel. In this way, the supplied refrigerant can be thermally decoupled from the removed refrigerant.

The two inlet-side strand end regions 37 a, 38 a lead out of the distribution pipe channel 39 a directly as adjacent flat pipe layers into the pipe / fin block in the central area of the same. From there, the serpentine pipe strings 1 f, 1 g run in the direction of flow on both sides outward to corresponding, opposite block end sides 41 , 42 , from where they bend with their outlet-side end regions 37 b, 38 b to halfway up the pipe / fin block arranged connecting pipe 39 are returned and thereby open into the manifold duct 39 b.

The manufacture of this evaporator preferably in turn includes a soldering process, for which purpose solder molded parts are used if necessary. Alternatively, the extruded flat tube strands can be provided with solder and flux, the solder being applied by the so-called Hydrogalve, CD, Sil-Flux or similar processes. The evaporator of FIG. 14 in turn has a symmetrical structure with the advantages described for the evaporator of FIGS. 12 and 13. In addition, he has the advantage that the adjacent Serpenti nenrohrstränge 1 f, 1 g with their inlet-side Rohrendbe rich 37 a, 38 a are adjacent. Since these are at the same temperature level in operation, there are no problems with regard to undesired heat transfer between a colder inlet-side end region of a pipe string and a warmer outlet-side end region of an adjacent pipe string.

FIG. 16 shows an exemplary embodiment of a heat exchanger which is constructed from a plurality of flat tubes 43 lying next to one another in the block vertical direction, of which one can be seen in plan view in FIG. 16. The U-shaped bent flat tubes 43 form an inlet-side half of the tube 43 a and an exit-side tube half 43 b, c are in fluid communication with each other through an arc range 43rd On both sides Benach discloses the arc region are c 43, both the inlet side tube half 43 a and the outlet-side pipe half 43 b by approximately 90 ° relative to the arch portion 43 c is twisted so that the entry-side and exit-side flat tube half 43 a, 43 b in the block depth direction one behind the other to lie and are oriented with their flat tube plane perpendicular to the block. The arch region is oriented parallel to the vertical direction of the block, as can also be seen from the view in FIG. 17. As can be seen there, in this construction of the tube / fin block, the height h _{1 of} successive flat tubes corresponds to the height of the arch region 43 c and thus the width of the extruded multi-chamber flat tubes 43 . In the spaces between successive U-shaped flat tubes 43 , a corrugated fin 44 is introduced, which extends continuously over both an outlet-side tube half 43 a and the outlet side tube half 43 b.

The adjacent ends of each U-shaped flat tube 43 open into a connecting tube 45 , which contains a distribution tube 46 and a collecting tube 47 integrated. For this purpose, the connecting tube 45 is cross-divided by means of a transverse wall 48 at the level between the two halves 43 a, 43 b of the flat tubes 43 in the distribution tube channel 46 on the one hand and the collecting tube channel 47 on the other. Both the distribution tube 46 and the collecting tube 47 have one or more peripheral slot openings, in which the ends of the inlet-side flat tube halves 43 a or the outlet-side flat tube halves 43 b are inserted individually or as a combined stack.

The evaporator constructed in this way thus consists of a tube / fin block complex which contains a front tube block from the side-by-side, inlet-side flat tube halves 43 a and a rear tube block from the side-by-side outlet side flat tube halves 43 b, with matching on one side of the tube - / Ribs block complexes the cross-divided, the distribution channel 46 and the collecting channel 47 containing connection pipe 45 is arranged. As indicated by the flow arrows, the Kältemit tel is axially introduced into the evaporator tube 46 in this evaporator and from there evenly the various one entry-side flat tube halves 43 a are supplied. In this it flows to the flat tube bend region 43 c, where it is deflected by 180 ° into the outlet-side flat tube halves 43 b in order to flow back to the connecting tube 45 , in the collecting tube channel 47 of which it collects coming from the various outlet side flat tube halves 43 b and is axially discharged becomes.

An alternative evaporator with a similar flow guide tion of the refrigerant can be realized in that instead of the two flat tube halves 43 a, 43 b of the U-shaped flat tubes 43 of FIG. 16, two rectilinear flat tubes are used and as a deflection area instead of the Bogenbe area 43 c of FIG. 16, a deflection channel arranged on the corresponding side of the tube / fin block complex is provided, into which the flat tubes open on this block side. The refrigerant is then pressed over the flat tubes on the inlet side into the deflection channel and fed from there into the flat tubes on the outlet side.

Fig. 18 shows a variant of the U-shaped flat tubes 43 of Fig. 16. The U-shaped flat tubes 43 are bent and twisted at this Varian te in the deflection area so that their arc area 43 c no longer runs parallel to the vertical direction, but is inclined by an acute angle α. Due to this oblique course of the bend area 43 c, the flat tubes 43 which follow one another in the tube block complex can be arranged with overlapping, ie partially intermeshing bend areas 43 c, as illustrated in FIG. 18 for two adjacent flat tubes 43 . The flat tubes 43 can therefore follow one another at a distance h ₂ that is smaller than the width of the flat tubes 43 and thus the distance h ₁ in the example of FIGS. 16 and 17. Correspondingly, corrugated fins 44 a are used for the variant of FIG. 18 used with the same reduced height.

It is understood that those shown and others, by those skilled in the art Realizable embodiments of the invention not only as Evaporators in automotive air conditioning systems, but also for other types of heat exchangers, e.g. B. for capacitors, and for applications outside the automotive field can be placed.

Claims (16)

1. Flat tube heat exchanger, in particular evaporator for a motor vehicle air conditioning system, with

• - At least one tube block from several, in a block vertical direction (z) side by side, parallel flowable flat tube strands ( 1 a, 1 b, 1 c) and
• - One each side of the pipe block arranged distribution and manifold ( 6 , 8 ) with at least one circumferential opening Publ ( 18 ), in which all flat tubing strings with their one exit and exit ends ( 3 a, 4 a, 5 a; 3rd b, 4 b, 5 b) are inserted in a fluid-tight manner,
  characterized in that
• - The distribution and the collecting pipe ( 6 , 8 ) are arranged with the longitudinal axis lying parallel to the depth direction of the block.

2. Flat tube heat exchanger according to claim 1, further characterized in that

• - Several pipe blocks lying next to each other in the block depth direction are provided and
• - The flat tube strands ( 1 a, 1 b, 1 c) of all tube blocks with their ren entry and exit ends ( 3 a, 4 a, 5 a; 3 b, 4 b, 5 b) in the same, between the foremost and the rearmost pipe block extending distribution or collecting pipe ( 6 , 8 ) are inserted.

3. Flat tube heat exchanger according to claim 1 or 2, further characterized in that the inlet-side or from the outlet-side ends of the flat tube strands ( 1 a, 1 b, 1 c) of a respective tube block individually in separate, circumferentially spaced openings in the distribution or collecting tube ( 6 , 8 ) or merged into a stack in a common opening of the distribution or collecting tube ( 6 a, 8 a) are added. 4. Flat tube heat exchanger according to claim 3, further characterized in that a distribution profile ( 12 ) is provided in the distribution tube 6 , which divides the distribution tube cross-section into a plurality of circumferentially spaced distribution spaces ( 13 a, 13 b, 13 c) such that the flat tube strands of a respective tube block with their inlet ends ( 3 a, 4 a, 5 a) each open into their own distribution room. 5. Flat tube heat exchanger according to claim 2 or 3, further characterized in that the distribution tube ( 6 h) by means of egg ner or more transverse partition walls ( 16 a, 16 b) in one of the number of tube blocks corresponding number of distribution spaces ( 17 a, 17 b, 17 c) is subdivided, into each of which an associated supply line ( 19 a, 19 b, 19 c) and the inlet ends ( 3 a, 4 a, 5 a) of the flat tube strands of an associated tube block open. 6. Flat tube heat exchanger according to claim 5, further characterized in that the supply lines ( 19 a, 19 b, 19 c) with a frontal opening in the respective distribution space ( 17 a, 17 b, 17 c) inside the distribution tube ( 6 h ) or under the circumferential confluence in the respective distribution space on the outer circumference of the distribution pipe ( 6 a). 7. Flat tube heat exchanger according to one of claims 4 to 6, further characterized in that on the inlet side of the distribution profile ( 12 ) or the supply line set ( 19 a, 19 b, 19 c) a venturi-type flow distribution device ( 14 ) is provided. 8. Flat tube heat exchanger according to claim 2 or 3, further characterized in that the distribution tube has a circumferentially introduced inlet opening ( 21 ) into which a feed pipe ( 23 ) opens and which is closer to the front most tube block ( 22 a) than to the rearmost pipe block ( 22 c) is arranged. 9. Flat tube heat exchanger according to one of claims 1 to 8, further characterized in that one to the distribution tube ( 6 d) leading supply tube ( 26 ) has a curved portion ( 26 a), in which an anti-segregation spiral profile ( 27 ) is inserted. 10. Flat tube heat exchanger according to claim 8 or 9, further characterized in that the supply pipe inlet opening ( 32 ) is arranged adjacent to the inlet-side end of the distribution pipe ( 6 f) and in the distribution pipe swirling means in the form of an inclined wall opposite the supply pipe inlet opening ( 30 ) and / or a perforated blen denquer wall ( 34 ) are provided between the supply tube inlet opening and the foremost flat tube strand connection opening ( 18 ) of the distribution tube. 11. Flat tube heat exchanger according to one of claims 1 to 10, further characterized in that the distribution tube ( 6 a) and the manifold ( 8 a) are arranged on opposite Rohrblocksei th and the tube block from several identical serpentine pipe strings ( 1 d, 1 e) is constructed, the respective end regions of which are led out on these opposite tube block sides and inserted into the distribution or collecting tube there. 12. Flat tube heat exchanger according to one of claims 1 to 10, further characterized in that the distribution tube ( 39 a) and the header tube ( 39 b) are arranged on the same tube block side and the tube block from several identical serpentine-shaped tube strings ( 1 f, 1 g) is constructed, the respective end regions ( 37 a, 38 a, 37 b, 38 b) are led out on this tube block side and inserted into the distribution or collecting tube there. 13. Flat tube heat exchanger according to claim 12, further characterized in that the distribution tube ( 39 a) and the Sam melrohr ( 39 b) are integral parts of a by means of at least one longitudinal partition ( 40 ) in several longitudinal channels un divided connecting tube ( 39 ) . 14. Flat tube heat exchanger according to claim 2 or 3, further characterized in that at least one inlet-side and one outlet-side tube block are provided, which are arranged side by side in the block depth direction, where in the distribution tube ( 46 ) and the header tube ( 47 ) integral parts of a means a transverse wall ( 48 ) subdivided to the connecting pipe ( 45 ) and the pipe block side facing away from the connecting pipe forms a fluid deflection area ( 43 c) via which the pipe channels ( 43 b) of the outlet-side pipe block to the pipe channels ( 43 a) of the inlet-side pipe block are connected . 15. Flat tube heat exchanger according to claim 14, further characterized in that the inlet-side and the outlet-side tube block of respective halves ( 43 a, 43 b) U-shaped flat tubes ( 43 ) are formed, the two halves of each flat tube relative to the Fluidumlenkbe rich forming U-bend area ( 43 c) are twisted such that they are perpendicular to the block vertical direction, while the U-bend area is parallel or at an acute angle (α) to the block vertical direction. 16. Flat tube heat exchanger according to one of claims 1 to 15, further characterized in that a corrugated fin ( 24 ) is arranged between two adjacent flat tubes ( 25 a, 25 b) in the block vertical direction, which is continuous in the block depth direction from the foremost to extends to the rearmost pipe block.